EP0413189B1 - Contrôle du tambour de câble d'un treuil pour masse de frappe à chute libre suspendue au câble - Google Patents

Contrôle du tambour de câble d'un treuil pour masse de frappe à chute libre suspendue au câble Download PDF

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Publication number
EP0413189B1
EP0413189B1 EP90114618A EP90114618A EP0413189B1 EP 0413189 B1 EP0413189 B1 EP 0413189B1 EP 90114618 A EP90114618 A EP 90114618A EP 90114618 A EP90114618 A EP 90114618A EP 0413189 B1 EP0413189 B1 EP 0413189B1
Authority
EP
European Patent Office
Prior art keywords
weight
cable
torque
rope
ramming
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
EP90114618A
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German (de)
English (en)
Other versions
EP0413189A1 (fr
Inventor
Roman Pfister
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.)
Liebherr Werk Nenzing GmbH
Original Assignee
Liebherr Werk Nenzing 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 Liebherr Werk Nenzing GmbH filed Critical Liebherr Werk Nenzing GmbH
Priority to AT90114618T priority Critical patent/ATE90128T1/de
Publication of EP0413189A1 publication Critical patent/EP0413189A1/fr
Application granted granted Critical
Publication of EP0413189B1 publication Critical patent/EP0413189B1/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
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/54—Safety gear
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
    • E02D7/00—Methods or apparatus for placing sheet pile bulkheads, piles, mouldpipes, or other moulds
    • E02D7/02—Placing by driving
    • E02D7/06—Power-driven drivers
    • E02D7/08—Drop drivers with free-falling hammer

Definitions

  • the invention relates to a method for controlling the cable drum of a winch according to the preamble of claim 1.
  • a device for performing such a method is already known from DE 20 65 907 A1. It describes in particular how the pile weight maintains a preselectable, constant value throughout the pile driving.
  • Pile weights are used, for example, to compact soil or other materials and to drive piles or pile tubes, whereby the drop height can be, for example, three to 10 meters. Due to the almost unbraked free fall of the ram weight, which is only braked by the inertia of the moving masses, in particular the masses set into rotation, and friction, the rope pulled off the rope drum is accelerated to considerable speeds which, after the ram weight hits the Material to be rammed will lead to slack rope formation and possibly even to a cross lay of the rope on the winch if the rope does not hit the ram weight is braked on the pile in such a way that it remains taut.
  • the rope drum must be braked depending on the impact of the ram weight on the pile. It is known to detect the sound caused by the impact by sensors and to apply the brakes of the cable drum immediately after the sensors respond or with a predetermined time delay. Furthermore, it is known to detect the vibration waves caused by the blow in the rope by sensors, which then initiate braking immediately or with a predetermined time delay. However, both methods are deficient because neither the sound nor the wave returning in the rope can generate sufficiently precise control signals.
  • the object of the invention is therefore to provide a control of the type specified above, with which the rope pulled from the ram weight by the rope drum can be braked within a predetermined overtravel essentially without bumps while preventing the formation of slack rope and while maintaining the selected drop height in subsequent blows .
  • this object is achieved in a generic method by the features of the characterizing part of claim 1.
  • the control system makes it possible to determine the point in time of the impact of the pile weight on the pile material precisely by a To determine rope length measurement without having to provide sensors that detect sound waves or shock waves running through the rope and can be exposed to interference.
  • the time of lifting the ram weight from the pile can be determined very precisely by the increase in the tensile force in the rope to the threshold value, which is greater than the tensile force for lifting the load handler, but less than the tensile force required to lift the pile weight.
  • the threshold value is reached, the rope lifting the pile weight is taut, so that the rope length can be determined and measured precisely until the pile weight is raised to the selected lifting height.
  • the time of the ramming weight hitting the pile can be determined exactly by subtracting a length of the rope corresponding to the measured lifting height from the winch drum.
  • the winch brake engages, which brakes the rope and the load handler within the overtravel.
  • the lowering of the upper point of the lifting height which results, for example, from driving in a pile, is automatically taken into account.
  • the load suspension means is raised above the height of the overtravel with reduced traction until the full ram weight acts on the traction rope after passing through the overtravel.
  • the tensile force initially rises as the slipping clutch slips to a threshold value that indicates the position of the ram weight at the time of impact on the rammed material on the next impact.
  • This load threshold value is saved and serves as the zero point for the measurement of the rope when lifting to the selected lifting height.
  • the exact determination of the time of impact and the impact of the ram weight on the ramming material on the next stroke can reduce the wear of the ramming machine because impact loads can be largely avoided. Furthermore, the service life of the rope can be significantly extended, because the rope is also less stressed and cross-strikes are avoided by skipping grooves in the rope drum.
  • the pile driving can be made safer and more user-friendly by avoiding the formation of slack ropes and unnecessary bumps. The workflow and the overall efficiency of the pile driving can be improved.
  • the cable drum is expediently braked by the slip clutch, which is switched to a corresponding braking torque.
  • the braking time is determined precisely by the previously measured rope length corresponding to the lifting height, which was pulled off the winch drum when the ram weight hit the rammed material.
  • the slipping clutch is switched to the caster torque for lifting the load handler after braking the rope, the load handler and the angular momentum of the winch drum, as well as the masses rotating therewith.
  • this switchover means that the load handler is automatically raised until the threshold value is reached and then the ram weight is also raised by a corresponding increase in tractive force, so that the ramming work can be carried out in a very short time without dead times. If, on the other hand, it happens that the ram weight hits cavities (caverns), this slipping does not cause any noteworthy blows because the required rope length can be pulled off the winch drum while the slipping clutch slips.
  • the load-carrying means has such a large mass or that an additional mass of the size is provided which prevents the formation of slack rope during braking via the overtravel. If the load suspension device does not have a sufficiently large mass, an additional mass can be provided which keeps the rope taut in the desired manner and prevents the formation of slack rope during braking via the overtravel.
  • the mass of the load handler alone or together with an additional mass can be in the range of 200 kg.
  • the braking of the load-carrying device takes place after the rope length corresponding to the fall height has passed from the winch drum, which is reduced by a certain lead distance, which results from the masses to be braked, which are to be braked and moved.
  • This type of control can be useful if larger sound levels, for example greater than 3 to 5 meters, are selected. In this case, especially the winch drum and the parts rotating with it are accelerated to speeds which result in a considerable angular momentum (swirl).
  • a hydraulically switchable multi-plate clutch which is extremely low-wear, is expediently used as the slip clutch.
  • the required variable torques can be set quickly and reliably, because the forces or relief paths generated by hydraulic cylinders of the multi-plate clutch acted upon by a spring are essentially linear to the magnitude of the torques.
  • the cable drum is driven via a planetary gear (differential gear with planet gears), from which two outputs can be coupled to one another by the slip clutch.
  • the slip clutch can be adjusted in a simple manner to control the respective torques until it slips, and the cable drum can also be switched to freewheel in a simple manner, with an additional holding brake being provided on the drive side, which engages when the drive motor is at a standstill.
  • a plate used for soil compaction can be attached to the load suspension device by means of ropes or chains.
  • the ram weight can also consist of a cylindrical hammer, which is provided in its interior with a substantially cylindrical chamber, the length of which is greater than the overtravel, the load suspension means or the additional weight being arranged in the chamber with the through a bore is connected in the top wall of the chamber hoist rope is connected.
  • the ram weight can also be formed by the gripper of a single-rope excavator, although an upper lifting point must then also be approached, in which a fixed bell is arranged, which serves to open the gripper.
  • the lifting rope 3 runs, to which the ram weight is attached in the form of a hammer 5.
  • the hoisting rope 3 is wound onto the winch drum 4 in the usual way.
  • the percussion hammer 5 consists of a cylindrical body with an inner elongated cylindrical chamber 6.
  • a bore 8 is provided, through which the lifting cable 3 is passed.
  • the load-carrying means 9 is fastened, which consists of a cylindrical weight with a mass of, for example, 200 kg.
  • the load-carrying means 9, consisting of an additional weight, can be lowered within the cylindrical chamber 6 of the hammer 5. However, if the hoist rope is raised, the load-carrying means 9, the diameter of which is larger than the bore 8, abuts the edge of the bore with its upper side, so that the impact ram can be raised via the load-carrying means 9 and the hoist rope.
  • the blow hammer 5 is guided within a pile tube 10 so that it can be raised and lowered. To drive this pile tube 10, the hammer 5 is raised to a predetermined height and then dropped by switching the winch drum 4 to freewheel.
  • the winch drum 4 is driven by the hydraulic hoist motor 12 via a planetary planetary gear.
  • Two outputs of the planetary epicyclic gear are connected to each other by the multi-plate clutch 13.
  • the multi-plate clutch 13 is closed by a compression spring and a hydraulic piston-cylinder unit, not shown, which relieves the compression spring is used for opening.
  • the closed multi-disc brake 13 has, for example, a braking force or a torque corresponding to a pulling force of the hoisting rope of 20 t
  • the braking or pulling force of 20 t can be applied via the hydraulic piston-cylinder unit, which can be pressurized, for example, to a maximum pressure of 80 bar to almost 0 steer down.
  • a holding brake 14 also consisting of a multi-plate clutch, which engages when the hoist motor 12 is stopped.
  • the length of rope wound on the winch 4 can be determined by a sensor 15, which can be an incremental encoder, for example.
  • a proportional valve 16 is provided to control the multi-plate clutch 13.
  • the multi-plate clutch 13 can be switched to free-fall release, in which the freely falling ram weight 5 pulls the hoist rope from the winch drum 4 switched to freewheeling.
  • the hydraulic circuit shown schematically in the drawing is supplied with hydraulic oil by the hydraulic pumps 19, 20, which are driven by the diesel engine 22 via the transmission 21.
  • the hammer 5 rests with its lower abutting surface 24 on the counter abutting surface 25, which is formed by the bottom of the pile tube 10.
  • the load-carrying means 9 is located, for example, in the lower region of the chamber 6, so that the lifting rope 3 is kept taut and the slack rope is prevented.
  • the operator of the duty cycle crawler crane actuates the automatic control, for example using a push button.
  • the automatic control now places the multi-plate clutch 13 on a limited cable that is coordinated with the lifting of the load-carrying means 9.
  • the hoist pump 19 for the hoist motor 12 is set to the maximum delivery rate in the lifting direction.
  • the system pressure in the pump circuit rises and triggers the coupling process to full cable pulling force.
  • a pressure threshold value is exceeded, at which the clutch 13 is changed over from limited cable pull to maximum cable pull, the cable length measurement, which is carried out by the measuring sensor 15, is set to 0. The point of impact of the hammer 5 on the next stroke is thus precisely defined.
  • the pump 20 After reaching the preselected free fall height, the pump 20 is pivoted to 0 and the clutch is opened to the free fall state via the switching valve 17. As soon as the counter of the measuring sensor running backwards reaches the counter reading 0, the clutch 13 is closed on a reduced cable pull, so that the load-carrying means forming an additional weight is braked within the overtravel, which is approximately 0.7 m.
  • the lower end of the additional weight 9 is at the height 30.
  • the height 30 thus indicates the braking point at which the clutch 13 engages as a follower brake.
  • This retention path can be chosen freely and, depending on the free fall height, can be in a range of 50 to 90 cm.

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Paleontology (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Placing Or Removing Of Piles Or Sheet Piles, Or Accessories Thereof (AREA)
  • Unwinding Of Filamentary Materials (AREA)
  • Storage Of Web-Like Or Filamentary Materials (AREA)
  • Ropes Or Cables (AREA)
  • Lift-Guide Devices, And Elevator Ropes And Cables (AREA)
  • Braking Arrangements (AREA)
  • Control And Safety Of Cranes (AREA)

Claims (11)

  1. Procédé pour le contrôle du tambour de câble (4) d'un treuil qui est relié à un moteur (12) et dont une masse de frappe (5) en chute déroule un câble (3) reliée à celui-ci, dans lequel la masse de frappe (5) reposant sur le matériau de frappe (10) est relevée par le câble (3) de nouveau à la hauteur de chute souhaitée, la hauteur de chute souhaitée de la masse de frappe (5) étant déterminée par un dispositif de mesure (15),
    caractérisé,
    en ce que le tambour de treuil (4) est entraîné par le moteur (12), par un accouplement à glissement (13) avec un couple de rotation réglable, en ce qu'un moyen de suspension de la charge (9) est disposé à une telle hauteur au-dessus de la masse de frappe (5) ou est relié de telle façon à la masse de frappe (5) que le câble (3), en évitant une formation de câble mou avant le heurt de la masse de frappe (5) peut être freiné à l'intérieur d'une distance de ralentissement, et que le câble (3) est freiné par le tambour de treuil (4) peu avant, au moment où, un peu après que la masse de frappe (5) heurte le matériau de frappe (10) à l'intérieur de la distance de ralentissement, en ce que le couple de rotation, lors du soulèvement sur la hauteur de la distance de ralentissement, est réglé à une valeur seuil, en ce que le poids du câble (3) et du moyen de suspension de la charge (9) sont accordés de façon que celui-ci, mais non pas la masse de frappe (5), soit soulevé, qu'après avoir atteint la valeur seuil, la force de traction du câble (3) avant ou pendant le soulèvement de la masse de frappe (5) active le dispositif de mesure (15), en ce que lorsqu'on atterrit la valeur seuil, l'accouplement (13) est commuté du couple de rotation plus faible de la distance de ralentissement au couple de rotation lors du soulèvement de la masse de frappe (5) ou au couple de rotation nominal, en ce que l'accouplement (13), lors de l'enroulement d'une longueur de câble correspondant à la hauteur de chute sur le tambour de treuil (4) est commuté en course libre, et en ce que le frein de treuil (14) devient actif dès q'une longueur de câble (3) correspondant à la hauteur de chute est déroulé du tambour de treuil (4).
  2. Procédé selon la revendication 1, caractérisé en ce que, lorsqu'on atteint la valeur seuil, la force de traction de câble est augmentée de façon continue au couple de rotation nominal du tambour de treuil (4).
  3. Procédé selon la revendication 1 ou 2, caractérisé en ce que le tambour de treuil (4) est freiné par l'accouplement à glissement (13) qui est commuté à un mouvement de freinage correspondant.
  4. Procédé selon l'une des revendications 1 à 3, caractérisé en ce que l'accouplement à glissement (13), après le freinage du câble (3) du moyen de suspension de la charge (9) et de l'impulsion de rotation du tambour de treuil (4) et d'autres masses tournant conjointement est commuté au couple de rotation de ralentissement pour relever le moyen de suspension de la charge (9).
  5. Procédé selon l'une des revendications 1 à 4, caractérisé en ce que le moyen de suspension de la charge (9) possède une masse ou qu'on prévoit une masse supplémentaire de la grandeur qui permet d'empêcher un formation de câble mou pendant le freinage sur la distance de ralentissement.
  6. Procédé selon l'une des revendications 1 à 5, caractérisé en ce que le freinage du moyen de suspension de la charge (9) est effectué après le déroulement d'une longueur de câble correspondant à la hauteur de chute du tambour de treuil (4) qui est diminuée d'une distance de retard ou de réserve défini qui résulte des masses tournantes, à freiner et effectuant un mouvement translatoire.
  7. Procédé selon l'une des revendications 1 à 6, caractérisé en ce que l'accouplement à glissement (13) est un embrayage à disques maintenu hydrauliquement.
  8. Procédé selon l'une des revendications 1 à 7, caractérisé en ce que le tambour de treuil (4) est entraîné par un engrenage planétaire (engrenage différentiel), dont deux sorties peuvent être accouplées l'une à l'autre par l'accouplement à glissement (13).
  9. Procédé selon l'une des revendication 1 à 8, caractérisé en ce qu'une plaque servant au compactage du sol est accrochée au moyen de suspension de la charge (9) par des câbles ou chaînes.
  10. Procédé selon l'une des revendications 1 à 8, caractérisé en ce que la masse de frappe est constituée d'un organe de frappe cylindrique (10) qui est pourvu dans son intérieur d'une chambre essentiellement cylindrique dont la longueur est plus grande que la distance de ralentissement, en ce que le moyen de suspension de la charge (9) et le poids supplémentaire respectivement sont disposés dans la chambre et sont reliés à des câbles de levage (3) passant à travers le perçage dans la paroi de recouvrement de la chambre.
  11. Procédé selon l'une des revendications 1 à 8, caractérisé en ce que la masse de frappe est constituée par le grappin d'un excavateur mono-câble.
EP90114618A 1989-08-18 1990-07-30 Contrôle du tambour de câble d'un treuil pour masse de frappe à chute libre suspendue au câble Expired - Lifetime EP0413189B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90114618T ATE90128T1 (de) 1989-08-18 1990-07-30 Steuerung der seiltrommel einer winde fuer ein an das seil angehaengtes, frei herabfallendes rammgewicht.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3927354A DE3927354A1 (de) 1989-08-18 1989-08-18 Steuerung der seiltrommel einer winde fuer ein an das seil angehaengtes, frei herabfallendes rammgewicht
DE3927354 1989-08-18

Publications (2)

Publication Number Publication Date
EP0413189A1 EP0413189A1 (fr) 1991-02-20
EP0413189B1 true EP0413189B1 (fr) 1993-06-02

Family

ID=6387397

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90114618A Expired - Lifetime EP0413189B1 (fr) 1989-08-18 1990-07-30 Contrôle du tambour de câble d'un treuil pour masse de frappe à chute libre suspendue au câble

Country Status (7)

Country Link
EP (1) EP0413189B1 (fr)
JP (1) JPH03120196A (fr)
KR (1) KR0139796B1 (fr)
AT (1) ATE90128T1 (fr)
DE (2) DE3927354A1 (fr)
ES (1) ES2041086T3 (fr)
HK (1) HK121093A (fr)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4297784B2 (ja) * 2001-10-23 2009-07-15 サムスン エレクトロニクス カンパニー リミテッド マークアップ文書とａｖデータとが記録された情報保存媒体、その記録方法、再生方法及び再生装置
DE102007062301B4 (de) 2007-12-21 2011-09-22 Franki Grundbau Gmbh & Co.Kg Steuerung für eine Rammvorrichtung
DE102009007916A1 (de) 2009-02-06 2010-08-19 Franki Grundbau Gmbh & Co.Kg Ramme mit Wirbelstromkupplung
CN102425166A (zh) * 2011-09-09 2012-04-25 苏州力高建筑工程技术有限公司 地基施工处理的新型打桩方法及其设备
DE102015003177A1 (de) 2015-03-12 2016-09-15 Liebherr-Werk Nenzing Gmbh Verfahren zum Betrieb einer mobilen Arbeitsmaschine mit Bodendruckbegrenzung
DE102015003980A1 (de) * 2015-03-26 2016-09-29 Liebherr-Werk Nenzing Gmbh Verfahren zur Steuerung einer Baumaschine sowie Schürfkübelbagger
DE102016008819A1 (de) * 2016-07-19 2018-01-25 Liebherr-Werk Nenzing Gmbh Schlagzahloptimierung
CN107090830B (zh) * 2017-06-15 2019-06-18 汤始建华建材（山东）有限公司 施打波浪桩设备及施工方法
DE102017120490A1 (de) 2017-09-06 2019-03-07 Liebherr-Components Biberach Gmbh Freifallwinde
CN110803622B (zh) * 2019-10-12 2020-10-27 浙江中锐重工科技有限公司 一种地下连续墙液压抓斗自由落体卷扬机系统
CN110862039B (zh) * 2019-11-12 2021-02-26 湖南博邦重工有限公司 一种强夯机控制系统
CN115247422B (zh) * 2021-04-26 2023-09-15 东台市巨力机械制造有限公司 一种用于履带式伸缩打桩机的卷扬机构

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE341669B (fr) 1970-04-13 1972-01-10 Stabilator Ab
US4002211A (en) * 1974-09-19 1977-01-11 Raymond International Inc. Cable operated apparatus for forming piles
FI820489L (fi) * 1981-02-19 1982-08-20 Frankignoul Pieux Armes Foerfarande och anordning foer automatisk reglering av indrivning av ett avlaongt paolelement i jorden
DE8630852U1 (fr) * 1986-11-18 1988-01-14 Philipp Holzmann Ag, 6000 Frankfurt, De

Also Published As

Publication number Publication date
DE59001607D1 (de) 1993-07-08
DE3927354C2 (fr) 1991-08-14
DE3927354A1 (de) 1991-04-25
KR0139796B1 (ko) 1998-07-15
ES2041086T3 (es) 1993-11-01
KR910004460A (ko) 1991-03-28
JPH03120196A (ja) 1991-05-22
EP0413189A1 (fr) 1991-02-20
HK121093A (en) 1993-11-12
ATE90128T1 (de) 1993-06-15
JPH0565437B2 (fr) 1993-09-17

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