EP0021171A1 - Système de flèche à deux bras pour grue - Google Patents

Système de flèche à deux bras pour grue Download PDF

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Publication number
EP0021171A1
EP0021171A1 EP80103130A EP80103130A EP0021171A1 EP 0021171 A1 EP0021171 A1 EP 0021171A1 EP 80103130 A EP80103130 A EP 80103130A EP 80103130 A EP80103130 A EP 80103130A EP 0021171 A1 EP0021171 A1 EP 0021171A1
Authority
EP
European Patent Office
Prior art keywords
arm
link
retaining
horizontal
tension
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
EP80103130A
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German (de)
English (en)
Other versions
EP0021171B1 (fr
Inventor
Hans Tax
Klaus Dr. Hösler
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.)
TAX, HANS
Terex Peiner GmbH
Original Assignee
Peiner Maschinen und Schraubenwerke 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 Peiner Maschinen und Schraubenwerke AG filed Critical Peiner Maschinen und Schraubenwerke AG
Publication of EP0021171A1 publication Critical patent/EP0021171A1/fr
Application granted granted Critical
Publication of EP0021171B1 publication Critical patent/EP0021171B1/fr
Expired legal-status Critical Current

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    • 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
    • B66C23/06—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 with jibs mounted for jibbing or luffing movements
    • B66C23/08—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 with jibs mounted for jibbing or luffing movements and adapted to move the loads in predetermined paths
    • B66C23/10—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 with jibs mounted for jibbing or luffing movements and adapted to move the loads in predetermined paths the paths being substantially horizontal; Level-luffing jib-cranes
    • B66C23/14—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 with jibs mounted for jibbing or luffing movements and adapted to move the loads in predetermined paths the paths being substantially horizontal; Level-luffing jib-cranes with means, e.g. pantograph arrangements, for varying jib configuration

Definitions

  • the invention relates to an adjustable crane boom system, comprising a basic link which acts as a pressure rod and is pivotally mounted about a first horizontal articulation axis on a support, a basic arm with a one which is pivotably mounted on the basic link about a second horizontal articulated axis and which is rigid at least in a first adjustment range of the system Deflection point for the deflection of a hoist rope into the suspension line having a load arm and a first retaining arm which is articulated in a third horizontal articulation axis with a tension support, which in turn is connected to the carrier about a fourth horizontal articulation axis, the articulation axes being laid such that the deflection point describes an approximately horizontal path in the first setting range.
  • Adjustable crane boom systems of this type are known for example in port cranes.
  • the deflection point for the hoist rope on the one hand be very close to the carrier, i.e. H. can be approached to the first and fourth hinge axis, but on the other hand a large radius is also possible, d. H. the deflection point can be brought into a large horizontal distance from the carrier, that is to say from the first and fourth articulation axes, and nevertheless the deviations from the horizontal path of the deflection point remain within narrow limits.
  • This requirement exists in particular in the case of cranes which are arranged so that they cannot move on the construction site, for example in the case of construction cranes.
  • the invention has for its object an adjustable crane boom system of the type mentioned To be designed in such a way that, given the size of the structural parts, the requirements for simultaneously achieving a low minimum radius, a large maximum radius and a slight deviation from the horizontal path of the deflection point can be met at the same time.
  • a second restraining arm is attached to the load arm, rotatably connected to it, which is connected in a fifth articulation axis via a coupling coupling to the tension support in or near the third articulation axis, that the first restraining arm in the
  • the stretch position between the tension support and the tension coupling can be decoupled from the connection to the tension support and that the location of the fifth articulation axis with respect to the load arm is selected such that in a second adjustment range of the system after the first support arm has been decoupled, the deflection point continues to describe an approximately horizontal path .
  • the first restraining arm can be decoupled automatically when the stretched position between the tension support and the tension coupling occurs, without any external intervention in the system being required.
  • the first support arm need not be permanently rigidly connected to the load arm. It is conceivable that the first support arm with the Load arm is articulated in or near the second hinge axis and is rotatably supported on the load arm by the second support arm in the first adjustment range of the system.
  • the second support arm is permanently connected to the load arm in a rotationally fixed manner, but this does not require that the second support arm and the load arm are connected to one another, for example by a welded or screwed connection.
  • the second support arm and the load arm can also be connected to one another in an articulated manner, for example in turn in the second articulation axis, the rotationally fixed connection between the second restraint arm and the load arm being able to be established by a permanently effective bracing, because the requirement for a rotationally fixed connection of the second Retaining arm and the load arm is already fulfilled when the second restraining arm is fixed in a rotational direction in a rotational direction.
  • a possible connection between the first restraint arm and the tension support, which causes the first restraint arm to be automatically decoupled from the tension support when the stretched position between the tension support and the tension coupling occurs, is based on an elongated hole connection between the first restraint arm and the tension support.
  • a crane boom system which fulfills the requirement for a minimal minimum radius of the deflection point and for a large maximum radius of the deflection point with little deviation from the horizontal path of the deflection point.
  • This known system also includes a pressure rod, which acts as a compression rod and is pivotally mounted about a first horizontal hinge axis on a support, a rigid, two-armed head arm with a swivel bearing on the base arm about a second horizontal hinge axis Steering point for the deflection of the hoist rope in the suspension line having a load arm and a retaining arm, which is articulated about a third horizontal articulation axis with a tension support, which in turn is connected to the carrier about a fourth horizontal articulation axis.
  • the restraining arm is permanently connected to the load arm in a rotationally fixed manner by means of anchoring.
  • a cam disk is arranged on the restraining arm, around which a traction rope serving as a tension support is placed over a more or less large angle depending on the adjustment position.
  • the shape of the cam disc means that the deflection point of the load arm describes an approximately horizontal path from a small minimum radius to a large maximum radius.
  • the solution according to the invention advantageously differs in that one can do without the very complicated manufacture of the cam disc which deviates from the circular shape.
  • the parts loa, lob, 1oc are components of a rigid support, ie the parts loa, 1ob, 1oc are unchangeable in their relative position under normal circumstances.
  • a basic control arm 12 is articulated on the support 1 0 about a first horizontal hinge axis 14.
  • the basic link 12 is pressure-resistant.
  • a two-armed head link 16 is articulated about a second horizontal hinge axis 18.
  • the head link 16 consists of a load arm 2o and a retaining arm 22.
  • the load arm 2o and the retaining arm 22 are connected to one another in a flexurally rigid manner by means of a guy system (not shown, but symbolized by the arch 24) that they are not relative in terms of enlarging the arch 24 can move towards each other.
  • the retaining arm 22 is connected in a third horizontal hinge axis 26 to a tension support 28, which is articulated about a fourth horizontal hinge axis 3o on the carrier 1o at 1oa.
  • a double-acting hydraulic piston-cylinder unit 32 is arranged, which serves for the change in inclination of the base arm 12 and thus the adjustment of the whole system.
  • the position of minimal deflection of the system is indicated in dashed lines.
  • a rope deflection point on the load arm, 2 0 which is denoted by 34 is a minimum distance a min from a dash-dotted axis 36, which symbolizes, for example, a tower axis in the case of a tower crane.
  • the deflection axis 34 on the load arm 2o is at the greatest distance amax from the axis 36 shown in broken lines.
  • the path which the deflection point 34 describes between the position of the boom system shown in broken lines and the position of the boom system shown in solid lines is drawn in with a dash-dotted line 38.
  • the path curve 38 between the two end positions of the boom system runs essentially horizontally with slight deviations from the horizontal which can be accepted. Beyond, ie to the right of that position of the deflection point 34 that it occupies on the system drawn in solid lines, the path curve 38 rises steeply, so that the "horizontal path of the deflection point 34 is no longer guaranteed within the permissible limits.
  • the course of the hoisting rope is not shown.
  • This hoisting rope runs from a winch arranged on the support 10 to the deflection point 34 and hangs freely down from this deflection point 34 in order to carry a crane hook or another load suspension device at the end of its free hanging distance.
  • the course of the hoisting rope can be chosen arbitrarily. But it is also conceivable to let the hoist rope coming from the winch run over deflection points of the boom system in such a way that when the winch is at a standstill, the height of the load hook or other load lifting device is not changed when the deflection point 34 passes through the double-dotted line between the two extreme positions, in one of which is the projection amine and the other of which is the projection a max .
  • FIGS. 2 to 4 A solution is now shown in FIGS. 2 to 4, in which the area of the horizontal path (with tolerable deviations from the horizontal) of the deflection point 34 can be expanded with a comparable size of the system parts.
  • FIG. 2 analog parts are provided with the same reference numerals as in FIG. 1, each increased by the number 100.
  • two restraining arms are articulated in the second articulation axis 118 on the basic link 112 in FIG. 2, a first restraining arm 150 and a second restraining arm 152.
  • the second restraining arm 152 is represented by a not shown but symbolized by the bow 154 Bracing is connected in a rotationally fixed manner to the load arm 12o, so that the second retaining arm 152 cannot be moved relative to the load arm 12o in the sense of enlarging the arc 154.
  • the first restraint arm 15o is connected to the second restraint arm 152 by a pull coupling 156, which extends between the third horizontal articulation axis 126 and a fifth horizontal articulation axis 164, so that in the adjustment range shown in FIG. 2, the first restraint arm 15o on the second Retaining arm 152 and thus ultimately rigidly fixed to the load arm 12o, in the sense that the arc 166 shown in broken lines cannot be enlarged in terms of angle.
  • the third horizontal hinge axis 126 is formed between the tension support 128 and the tension coupling 156.
  • An elongated hole guide 16o is arranged on the first restraining arm 15o and wraps around a joint head 162 on the third horizontal joint axis 126.
  • the second restraining arm 152 is loaded by a force K acting on the deflection point 134.
  • the joint head 126 is always in the lower end of the elongated hole 16o in FIG. 2.
  • the system spanned by the first restraining arm 15o, the second restraining arm 152, the guying 154 and the pulling coupling 156 behaves as a rigid disk; As in the embodiment according to FIG. 1, the movement of the system takes place in the first joint axis 114, the second joint axis 118, the third joint axis 126 and the fourth joint axis 13o.
  • the deflection point 134 for the hoisting rope passes through the double-dotted, approximately horizontal las tweg 138 up to the projection a maxI .
  • Fig. 3 the system is in the position which corresponds to the projection a maxI .
  • the pull coupling 156 has just entered the pull support 128 in the extended position. If the adjustment system is now further adjusted from the position according to FIG. 3 in the direction of the position according to FIG. 4, the pull coupling 156 remains in the extended position with respect to the pull support 128.
  • the system now behaves as if whether a single tension element 128 + 156 would act directly on the second retaining arm 152, which is still fixed invariably with respect to the load arm 12o via the arc 154.
  • the boom system now behaves similarly to the system shown in FIGS.
  • the first restraint arm 15o is no longer loaded.
  • the elongated hole 16o can move freely relative to the joint head 162, as is shown from the difference between FIGS. 3 and 4.
  • the fifth joint axis 164 can be positioned in relation to the other joint axes 114, 118, 126 and 130 so that the approximately horizontal connection of the curve section 138 'to the curve section 138 is ensured.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Jib Cranes (AREA)
EP80103130A 1979-06-07 1980-06-04 Système de flèche à deux bras pour grue Expired EP0021171B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2923146 1979-06-07
DE2923146A DE2923146C2 (de) 1979-06-07 1979-06-07 Doppellenker-Kranauslegersystem mit annähernd horizontalem Lastweg

Publications (2)

Publication Number Publication Date
EP0021171A1 true EP0021171A1 (fr) 1981-01-07
EP0021171B1 EP0021171B1 (fr) 1985-01-30

Family

ID=6072713

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80103130A Expired EP0021171B1 (fr) 1979-06-07 1980-06-04 Système de flèche à deux bras pour grue

Country Status (2)

Country Link
EP (1) EP0021171B1 (fr)
DE (2) DE2923146C2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2562974A1 (fr) * 1984-04-13 1985-10-18 Darmon Michel Mecanisme de guidage, machine-outil ainsi equipee, applications du mecanisme a un bras articule et a une table elevatrice, et combinaisons de deux tels mecanismes
GB2353515A (en) * 1999-07-07 2001-02-28 Liebherr Werk Ehingen Controlling the path of a crane hook
GB2353513A (en) * 1999-07-07 2001-02-28 Liebherr Werk Ehingen Crane lifting capacity optimisation

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE346502A (fr) *
FR643078A (fr) * 1926-09-11 1928-09-10 Demag Ag Grue basculante
DE602311C (de) * 1934-09-06 Demag Akt Ges Doppellenkerwippkran
DE1073179B (de) * 1960-01-14 Kampnagel Aktiengesellschaft (vorm. Nagel S. Kaemp), Hamburg Portalwippkran mit waagerechtem Lastweg
DE1207059B (de) * 1964-10-10 1965-12-16 Demag Ag Doppellenkerwippkran mit Hilfshub
DE1531159A1 (de) * 1967-12-08 1969-12-18 Biedermann Dipl Ing Herbert Doppellenkerwippausleger fuer Wippkrane,insbesondere Turmdrehkrane
US3685668A (en) * 1969-10-03 1972-08-22 Hopper Inc Convertible level luffing crane

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE236723C (fr) *
DE494848C (de) * 1930-03-31 Demag Akt Ges Wippkran mit Spitzenausleger
DE621937C (de) * 1933-01-10 1935-11-15 Demag Akt Ges Wippkran

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE346502A (fr) *
DE602311C (de) * 1934-09-06 Demag Akt Ges Doppellenkerwippkran
DE1073179B (de) * 1960-01-14 Kampnagel Aktiengesellschaft (vorm. Nagel S. Kaemp), Hamburg Portalwippkran mit waagerechtem Lastweg
FR643078A (fr) * 1926-09-11 1928-09-10 Demag Ag Grue basculante
DE1207059B (de) * 1964-10-10 1965-12-16 Demag Ag Doppellenkerwippkran mit Hilfshub
DE1531159A1 (de) * 1967-12-08 1969-12-18 Biedermann Dipl Ing Herbert Doppellenkerwippausleger fuer Wippkrane,insbesondere Turmdrehkrane
US3685668A (en) * 1969-10-03 1972-08-22 Hopper Inc Convertible level luffing crane

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2562974A1 (fr) * 1984-04-13 1985-10-18 Darmon Michel Mecanisme de guidage, machine-outil ainsi equipee, applications du mecanisme a un bras articule et a une table elevatrice, et combinaisons de deux tels mecanismes
EP0159947A1 (fr) * 1984-04-13 1985-10-30 Michel Darmon Mécanisme de guidage
US4718292A (en) * 1984-04-13 1988-01-12 Michel Darmon Mechanism for guiding an element parallel to itself
US4721006A (en) * 1984-04-13 1988-01-26 Michel Darmon Mechanism for circular guiding
GB2353515A (en) * 1999-07-07 2001-02-28 Liebherr Werk Ehingen Controlling the path of a crane hook
GB2353513A (en) * 1999-07-07 2001-02-28 Liebherr Werk Ehingen Crane lifting capacity optimisation
GB2353513B (en) * 1999-07-07 2003-09-03 Liebherr Werk Ehingen Lifting capacity optimisation when making crane movements
GB2353515B (en) * 1999-07-07 2003-09-10 Liebherr Werk Ehingen A method and an apparatus for the operation of a crane load hook

Also Published As

Publication number Publication date
DE2923146C2 (de) 1982-04-01
EP0021171B1 (fr) 1985-01-30
DE2923146A1 (de) 1980-12-18
DE3070048D1 (en) 1985-03-14

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