EP0358343A1 - Grue avec détecteur de surcharge - Google Patents

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Publication number
EP0358343A1
EP0358343A1 EP89308173A EP89308173A EP0358343A1 EP 0358343 A1 EP0358343 A1 EP 0358343A1 EP 89308173 A EP89308173 A EP 89308173A EP 89308173 A EP89308173 A EP 89308173A EP 0358343 A1 EP0358343 A1 EP 0358343A1
Authority
EP
European Patent Office
Prior art keywords
load
crane
pulley
jib
rope
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP89308173A
Other languages
German (de)
English (en)
Inventor
John Allen
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.)
Rolls Royce Power Engineering PLC
Original Assignee
Northern Engineering Industries PLC
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
Priority claimed from GB888819960A external-priority patent/GB8819960D0/en
Priority claimed from GB888819959A external-priority patent/GB8819959D0/en
Application filed by Northern Engineering Industries PLC filed Critical Northern Engineering Industries PLC
Publication of EP0358343A1 publication Critical patent/EP0358343A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/88—Safety gear
    • B66C23/90—Devices for indicating or limiting lifting moment

Definitions

  • This invention relates to cranes and more particular­ly to cranes provided with means for detecting overloading of the crane.
  • the load a crane can lift is a function of the radius of the derrick or jib of the crane from the central pivot axis of the crane, which, in turn, for a given length of jib, is dependent upon the angle of the jib with the horizontal.
  • the practical permissible load at any given radius is less than the maximum load the crane could tolerate at that radius under ideal conditions before being damaged.
  • the tension in the load-handling rope or the luffing rope is monitored, for example by a load cell, and the angle of the jib to the horizontal is measured using an inclinometer. This information is then processed electronically to determine whether the load being lifted at a particular radius of the jib is within allowable safety limits.
  • a crane comprising a support structure, a jib and a winch mounted on said structure, a rope extending from said winch over first pulley means mounted on the jib, the rope terminating in load-engaging means, and load-sensing means responsive to the load on the rope, characterised by second pulley means mounted on the structure, the rope extending from the winch over the second pulley means and then over the first pulley means, the load-sensing means reacting between the second pulley means and the structure and being so arranged that, for the maximum safe load at any given operating radius of the jib, the load-sensing means experiences a substantially constant predetermined load thereon.
  • a single predetermined condition of the load-sensing means is appropriate to overloading of the crane regardless of the angle of inclination of the jib, it not therefore being necessary to measure the inclination of the jib, nor to compute multiple readings, to determine overload conditions but only to monitor a force derived from the load-sensing means.
  • the load-­sensing means comprises a load cell.
  • the load-sensing means further includes resilient means reacting between the second pulley means and the load cell, and a switch co-operating with the resilient means in such a manner that, when a load in excess of said predetermined load is applied to the resilient means, the switch is actuated.
  • the second pulley means comprises a rope accumulator, the arrangement being such that, when a load in excess of said predetermined load is applied to the load-­sensing means, the second pulley means pays out rope in a sense to reduce said load.
  • the second pulley means of the alternative embodiment comprises an elongate member one end of which is pivotally mounted to the crane support structure and on the other, free end of which is mounted one or more pulleys, the load-sensing means comprising resilient means reacting between the crane support structure and said elongate member, the arrangement being such that, when a load in excess of said predetermined load is applied to the resilient means, the elongate member is pivoted about its one end to pay out rope in a sense to reduce the load.
  • a pedestal crane of the type used on offshore platforms is indicated generally at 10 and includes a support structure consisting of a pedestal 12 mounted on the platform (not shown), a base 14 mounted on the pedestal 12 by a slewing mechanism (not shown) and a superstructure 16 incorporating a cab for the crane operators.
  • One end of a jib 18 is pivotally mounted to the base 14, the other, free end of the jib 18 carrying a first pulley system 20.
  • a luffing winch 22 and a load-handling winch 24 are also mounted on the base 14, one end of a luffing rope 26 being attached to the luffing winch 22, said rope 26 being reeved between the pulley system 20 and a pulley 28 mounted on the superstructure 16.
  • the other end of the rope 26 is anchored, for example at 30, on the super­structure 16 whereby operation of the winch 22 causes the jib 18 to luff.
  • the crane further includes a second pulley system indicated generally at 32 and comprising an elongate member 34 one end of which is pivotally mounted to the base 14 at 36 and the other, free end of which carries a pulley 38.
  • the member 34 is anchored to a load cell 40 mounted on the superstructure 16 through a coil spring 42 reacting between a point on the member 34 adjacent its free end and the load cell 40, a microswitch 44 being associated with the spring 42 as will be explained in more detail below.
  • a load-handling rope 46 is attached to the winch 24 and is reeved through the second pulley system 32 and then through the first pulley system 20, the rope terminating at its other end in a load-engaging means such as a hook 48.
  • the pulley system 20 can be any suit­able arrangement, and, for example, the pulley or pulleys through which the rope 46 is reeved may not be coaxial with the pulleys through which the rope 26 is reeved.
  • the maximum load the crane can handle is dependent upon the angle of the jib 18 to the horizontal.
  • the crane may be capable of handling a maximum load of 30 tons on the hook 48, while, with the jib substantially horizontal, this load may be reduced to about 10 tons.
  • the dimensions and configuration of the pulley system 32 - i.e. the location of the pivot point 36 and of the cell 40 and spring 42 - are selected such that, regardless of the angle of the jib 18 with the horizontal, the resultant force on the pulley system 32 and therefore on the load cell 40 for a maximum safe load on the crane is substantially constant.
  • the maximum load capable of being lifted by the jib 18 at a relatively acute angle of the jib, indicated by the lines 46P and 46W, the directions of the rope 46 to the pulley system 20 and the winch 24 respectively, is 10 tons.
  • the resultant of these forces in the lines 46P and 46W is indicated by the vector R and amounts to a force of 15 tons acting at the load cell 40.
  • the maximum load capable of being lifted with the jib 18 substant­ially vertically may be 30 tons as indicated by the lines 46P′ and 46W′.
  • the nature of the pulley system 32 is such that the resultant force, indicated by the vector R′, is again 15 tons acting at the load cell 40.
  • the crane operator can therefore easily read from the load cell output whether or not the load being lifted at the particular radius concerned - i.e. jib elevation - exceeds the permitted safe load. If the permitted safe load is exceeded, the member 38 extends the spring 42 sufficiently for the microswitch 44 to be actuated to trigger an associated audible and/or visible alarm or to deactivate the winch 24.
  • Such an arrangement utilises the tension in the rope 46 to produce a modulating signal which is fed to the load cell 40 to ensure that, regardless of the angle of the jib and without the necessity for cal­culation, overload is detected.
  • the mechanism of the crane itself is thus being used to regulate the load on the pulley system 32.
  • the pulley system 32 can function as a rope accumu­lator system.
  • the elongate member 34 is anchored to the superstructure 16 through a spring such as 42 which may or may not react against a load cell 40, the load on the spring 42 again being sub­stantially constant for the maximum safe load the crane can lift at any given operating radius of the jib 18.
  • the spring 42 is overcome and the pulley 38, together with the elongate member 34, pivots along an arcuate path 50 to the position shown in dotted lines at 38′ thereby rapidly paying out rope in a sense to reduce the force.
  • the paying out of the reserve of rope serves to protect the crane 10 against the effects of the exessive load for a short period which allows the control system (which includes overload sensors) or the operators to respond and cause the winch 24 to pay out rope.
  • the pulley 38 may be mounted on a slide mechanism, while the resiliency of the system 32 in its rope accumulator mode may be provided by pressurised pneumatic, hydraulic or hydropneumatic systems.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Jib Cranes (AREA)
  • Control And Safety Of Cranes (AREA)
EP89308173A 1988-08-23 1989-08-11 Grue avec détecteur de surcharge Withdrawn EP0358343A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
GB888819960A GB8819960D0 (en) 1988-08-23 1988-08-23 Cranes
GB8819960 1988-08-23
GB8819959 1988-08-23
GB888819959A GB8819959D0 (en) 1988-08-23 1988-08-23 Cranes

Publications (1)

Publication Number Publication Date
EP0358343A1 true EP0358343A1 (fr) 1990-03-14

Family

ID=26294311

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89308173A Withdrawn EP0358343A1 (fr) 1988-08-23 1989-08-11 Grue avec détecteur de surcharge

Country Status (2)

Country Link
EP (1) EP0358343A1 (fr)
NO (1) NO893352L (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2145568C1 (ru) * 1998-02-10 2000-02-20 Открытое акционерное общество "Тихорецкий машиностроительный завод имени В.В.Воровского" Ограничитель грузоподъемности крана (варианты)
US6145680A (en) * 1997-09-24 2000-11-14 Kci Konecranes International Plc Apparatus for reducing overload and dampening collision energy
CN104150359A (zh) * 2014-07-08 2014-11-19 湖南中联重科智能技术有限公司 起重量测量方法、设备、系统以及工程机械
CN117566588A (zh) * 2023-11-21 2024-02-20 永天机械设备制造(深圳)有限公司 龙门吊提产系统
EP4450446A1 (fr) * 2023-04-18 2024-10-23 Liebherr-MCCtec Rostock GmbH Grue

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL89303C (fr) * 1900-01-01
DE1167501B (de) * 1962-10-09 1964-04-09 Demag Ag Lastmoment- und UEberlastsicherung fuer Wippkrane
FR1574384A (fr) * 1968-07-11 1969-07-11
FR2040948A5 (fr) * 1969-04-29 1971-01-22 Schwermasch Dimitroff
FR2162997A5 (fr) * 1971-11-23 1973-07-20 Kirow Leipzig Schwermasc

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL89303C (fr) * 1900-01-01
DE1167501B (de) * 1962-10-09 1964-04-09 Demag Ag Lastmoment- und UEberlastsicherung fuer Wippkrane
FR1574384A (fr) * 1968-07-11 1969-07-11
FR2040948A5 (fr) * 1969-04-29 1971-01-22 Schwermasch Dimitroff
FR2162997A5 (fr) * 1971-11-23 1973-07-20 Kirow Leipzig Schwermasc

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6145680A (en) * 1997-09-24 2000-11-14 Kci Konecranes International Plc Apparatus for reducing overload and dampening collision energy
RU2145568C1 (ru) * 1998-02-10 2000-02-20 Открытое акционерное общество "Тихорецкий машиностроительный завод имени В.В.Воровского" Ограничитель грузоподъемности крана (варианты)
CN104150359A (zh) * 2014-07-08 2014-11-19 湖南中联重科智能技术有限公司 起重量测量方法、设备、系统以及工程机械
CN104150359B (zh) * 2014-07-08 2016-06-08 湖南中联重科智能技术有限公司 起重量测量方法、设备、系统以及工程机械
EP4450446A1 (fr) * 2023-04-18 2024-10-23 Liebherr-MCCtec Rostock GmbH Grue
CN117566588A (zh) * 2023-11-21 2024-02-20 永天机械设备制造(深圳)有限公司 龙门吊提产系统

Also Published As

Publication number Publication date
NO893352L (no) 1990-02-26
NO893352D0 (no) 1989-08-21

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