EP0988403B1 - Schwenkvorrichtung mit ausleger - Google Patents

Schwenkvorrichtung mit ausleger Download PDF

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Publication number
EP0988403B1
EP0988403B1 EP98922793A EP98922793A EP0988403B1 EP 0988403 B1 EP0988403 B1 EP 0988403B1 EP 98922793 A EP98922793 A EP 98922793A EP 98922793 A EP98922793 A EP 98922793A EP 0988403 B1 EP0988403 B1 EP 0988403B1
Authority
EP
European Patent Office
Prior art keywords
swivel
arm
linear drive
swivel arm
boom
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
EP98922793A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0988403A1 (de
Inventor
Emile Lonardi
Philippe Malivoir
Victor Kremer
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.)
Paul Wurth SA
Original Assignee
Paul Wurth SA
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 Paul Wurth SA filed Critical Paul Wurth SA
Publication of EP0988403A1 publication Critical patent/EP0988403A1/de
Application granted granted Critical
Publication of EP0988403B1 publication Critical patent/EP0988403B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • C—CHEMISTRY; METALLURGY
    • C21—METALLURGY OF IRON
    • C21B—MANUFACTURE OF IRON OR STEEL
    • C21B7/00—Blast furnaces
    • C21B7/12—Opening or sealing the tap holes

Definitions

  • the invention relates to a swivel device with boom Swiveling a work organ between a rest position and one Working position.
  • a swivel device with boom Swiveling a work organ between a rest position and one Working position.
  • Such a device is used, for example, for pivoting a tap hole cannon attached to the boom from a rest position in a working position in front of the tap hole of a blast furnace, and to then press the stuffing cannon into the tap hole.
  • a classic swivel device for a taphole cannon includes in known manner a fixed support structure and a boom that with one of its two ends is rotatably supported in this support structure. To the Hydraulic cylinders are mostly used to swing the boom.
  • the swivel range of such a swivel device should be as possible be large to keep the darning cannon as far out of the area as possible To be able to swing out the launder.
  • modern stuffing cannons work with ever higher stuffing pressures. Hence must also the swivel device, which the stuffing cannon against Press the tap hole should be designed for ever greater contact forces.
  • DE-A-2035697 is a swivel device for a Taphole cannon known to generate a master cylinder Swivel movement and a smaller auxiliary cylinder to overcome the Has dead center of the master cylinder.
  • the master cylinder is between one first lever arm at the rear end of the boom and a first fixed lever that protrudes far from the support structure of the boom, arranged.
  • the auxiliary cylinder is between the rear end of the boom and a second fixed lever arranged on the support structure.
  • the Auxiliary cylinder swivels the boom over the dead center of the master cylinder.
  • a hydraulic circuit changes the stroke direction of the double-acting Master cylinder when dead center is exceeded.
  • the first Hydraulic cylinder is the moment of force that the second hydraulic cylinder presses on the darning cannon exerts on the tap hole on the swing frame into the Initiate the supporting structure.
  • the two hydraulic cylinders approximately equally large lever arms are available, so that both hydraulic cylinders are equally strong are designed.
  • the lever arm of the, in Working position the second hydraulic cylinder for transmitting a force to the Boom is not available due to the position of the swivel frame being affected.
  • the object of the present invention is to transmit the power in the US-A-4,544,143 to improve known pivoting device.
  • Such a swivel device includes how the device from US-A-4,544,143: a boom for carrying a work organ; a support structure in which the boom with one end about a pivot axis is pivotally mounted; a first linear actuator, usually a hydraulic cylinder, for pivoting the boom between its rest position and its working position, the lifting drive using a first swivel joint is connected to the boom; a swivel arm with one end is pivotally mounted about a pivot axis in the support structure, the Lift drive by means of a second swivel joint with the free end of the Swivel arm is connected; and an actuator for pivoting the Swivel arms relative to the support structure.
  • a first linear actuator usually a hydraulic cylinder
  • the swivel arm is not - as described in US-A-4,544,143 - coaxial to the swivel axis of the boom, but at a certain distance from the same.
  • the swivel arm is eccentric to the boom stored.
  • can be Example increase the lever arm with which the linear actuator exerts its force on the Boom transfers.
  • the actuator of the swivel arm Switch largely without power when the boom is in the working position.
  • the swivel arm can be swiveled into a position in which the Lift drive, when transmitting a force to the boom, no moment of force exerts on the actuator.
  • the hydraulic cylinder of the boom When swinging the boom out of his The hydraulic cylinder of the boom is at rest in its working position and the actuator of the swivel arm either simultaneously or in succession operated.
  • the actuator of the swing arm Like the one arranged between the support structure and the swing frame Hydraulic cylinder in US-A-4,544,143 also carries the actuator of the swing arm contributes to covering the swivel range of the boom.
  • an inventive one Swivel device can be built more compact and cheaper, where neither the swivel range, nor that of the boom on the work organ transferred contact pressure must be reduced.
  • the pivot arm can be pivoted by its actuator into a working position in which the second swivel joint of the lifting drive, in the working position of the boom, is in the immediate vicinity of a plane which contains the swivel axis of the swivel arm and the center of the first swivel joint of the lifting drive.
  • the swivel arm does not have to absorb any or only a small moment of force when the lifting drive is actuated, so that the actuator does not have to exert any or only a small force in order to hold the swivel arm in its working position.
  • the actuator of the swivel arm can therefore be designed much weaker than the lifting drive of the boom.
  • the pivot arm can be pivoted by its actuator into a working position in which the second swivel joint of the lifting drive, in the working position of the boom, lies beyond a plane which contains the swivel axis of the swivel arm and the center of the first swivel joint of the lifting drive.
  • the second swivel joint of the lifting drive is swiveled beyond the position in which the swivel arm is torque-free when the lifting drive is actuated.
  • the direction of action of the moment of force exerted on the swivel arm changes.
  • the support structure advantageously has an abutment on which the swivel arm rests in the working position.
  • This abutment absorbs the moment of force that is introduced into the swivel arm when the linear actuator is actuated, so that the actuator is fully relieved.
  • the actuator can also have a built-in end stop which defines the working position of the swivel arm.
  • the swivel arm and its actuator are advantageously designed such that when swiveling the swivel arm into its working position, the distance between the swivel axis of the boom and a straight line, which is the centers connecting the two swivel joints of the linear actuator increases.
  • the lever arm increases with which the force of the linear actuator on the pivoting boom is transmitted. Because the contact pressure caused by the Swivel device is transferred to a working organ, proportional to The moment of force that the linear actuator transmits to the boom takes it The contact pressure is therefore proportional to the lever arm mentioned above.
  • very large contact forces are generated.
  • the actuator is preferably a second stroke drive, usually a hydraulic cylinder, on the one hand with a fixed point of the supporting structure and on the other hand is pivotally connected to the swivel arm.
  • This second linear actuator can be much smaller than the first linear actuator (i.e. have a much smaller diameter). This will not only enables a more compact and cheaper design of the swivel device, but also the oil consumption of the swivel device is reduced.
  • the actuator of the swivel arm may also be a rotary drive, such as an electric or hydraulic swivel motor.
  • the Swivel arm in a rest position in which the second swivel joint of the Lift drive is arranged such that in the rest position of the boom, the first stroke drive is essentially parallel to the boom.
  • the invention is particularly advantageous is applicable to the swivel device of a tap hole tamping machine.
  • FIG. 1 shows a taphole tamping machine 10 according to the invention a rest position in front of a blast furnace 12, indicated by a circular arc.
  • This tap hole tamping machine 10 consists essentially of a Swivel device 14 according to the invention and a known taphole cannon 16. The latter is not described further here.
  • the pivoting device 14 comprises a stand that has a supporting structure 18 trained for a boom 20. Instead of standing on the floor this support structure 18 can of course also be suspended.
  • the boom 20 is pivotally supported at one end in this support structure 18.
  • Figure 1 shows the position of the pivot axis of the boom 20 in the support structure 18 shown by reference numeral 22. It is usually relative to the vertical slightly inclined towards the blast furnace 12.
  • the taphole cannon 16 is pivotally suspended.
  • the position of the swivel axis the taphole cannon 16 in the boom 20 is denoted by the reference numeral 24 shown.
  • a control rod 26 is articulated with the support structure 18 and the rear end of the tap hole cannon 16 connected. It allows the alignment of the taphole cannon 16 in Determine dependence of the pivot angle of the boom 20.
  • One end of this hydraulic cylinder 28, in the embodiment shown, is concerned around its piston end 30, by means of a first swivel joint 32 front end of the boom 20 connected.
  • the boom 20 advantageously a lateral projection 34 on which the first swivel joint 32 is attached (see also Figure 2).
  • the version shown is the cylinder base, is about a second pivot joint 36 is connected to a swivel arm 38.
  • the latter is pivoted at a fixed point of the support structure 18.
  • the location of the The pivot axis of the pivot arm 38 in the support structure 18 is shown in the figures shown by reference numeral 40. It is an important feature of the present Invention that the pivot axis 40 of the pivot arm 38 in one certain distance from the pivot axis 22 of the boom 20.
  • support structure 18, boom 20, swivel arm 38 and hydraulic cylinder 28 kinematically form a four-link gear (18, 20, 38, 28) with four swivel joints (22, 32, 36, 40).
  • a second substantially smaller hydraulic cylinder 42 is articulated on the one hand a fixed point 46 on the support structure 18 and on the other hand articulated with the Swivel arm 38 connected.
  • This hydraulic cylinder 42 enables pivoting of the swivel arm 38 relative to the support structure 18, wherein in gearbox (18, 20, 38, 28), the relative position of the hydraulic cylinder 28 to the boom 20, and thus also the lever arm of the hydraulic cylinder 28 relative to the pivot axis 22 of the boom 20, changed.
  • both hydraulic cylinders 28 and 42 have their minimum length on, i.e. their piston rods are retracted. It is found that the Swivel device 14 is extremely compact in this position, and in comparison requires little space for known machines. On the other hand, are in this Position the requirements for a torque transmission from the hydraulic cylinder 28 on the boom 20 but extremely unfavorable. Indeed, the lever arm X1 for this power transmission, i.e. the distance between the swivel axis 22 of the boom 20 and the straight line 48, which are the centers of the two Swivel joints 32 and 36 of the hydraulic cylinder 28 connects, relatively small.
  • the tap hole tamping machine 10 is in its working position shown.
  • the tap hole cannon 16 should pass through the boom 20 are pressed firmly against a tap hole 51 on the blast furnace 12.
  • the second Swivel 36 of the hydraulic cylinder 28 in the immediate vicinity of one Level 48 ", which is the pivot axis 40 of the pivot arm 38 and that Center of the first pivot 32 of the lifting drive 28 contains. This will ensures that the hydraulic cylinder 42 of the swivel arm 38 ideally does not have any, or in practice to absorb only a small component of the reaction force needed when the hydraulic cylinder 28 needed on the stuffing gun 16 Contact pressure is generated and is supported on the support structure 18.
  • Such misalignment can for example, be due to the fact that the swing angle of the boom 20 can easily change from the rest position to the working position.
  • the hydraulic cylinder 42 is preferred designed such that it has a residual torque from the hydraulic cylinder 28 when Pressing the stuffing gun 16 into the swivel arm 38 is compensated for can.
  • the stroke of the Hydraulic cylinder 42 advantageously adjustable.
  • the hydraulic cylinder 42 for Example have a mechanically adjustable end stop.
  • the pivoting angle of the boom 20 can be changed too much, which can result resulting misalignment of the swivel arm 38 by a transducer are detected, and for example the stroke of the hydraulic cylinder 42 automatically be readjusted until the alignment error is eliminated, i.e. the Centers of the two pivot joints 32 and 36 of the hydraulic cylinder 28 and the The pivot axis 40 of the pivot arm 38 lie in a plane 48 ′′ Regulation is indicated schematically in Figure 6. With the reference numeral 52 an angle encoder designated, the angle between the swivel arm and hydraulic cylinder 28 detected and forwarded to a controller 54. The output signal 56 of this controller 54 is then used, for example, to control the hydraulic cylinder 42 used. For the readjustment of the hydraulic cylinder 42, the hydraulic cylinder must 28 may be temporarily relieved.
  • FIG. 7 shows a further design option for the invention Swivel device shown in working position. Comparing Figure 7 with 6, it can be seen that the second swivel joint 36 of the lifting drive 28 lies beyond the plane 48 ", which is the pivot axis 40 of the pivot arm 38 and the center of the first pivot 32 of the lifting drive 28 contains. In this position, the swivel arm 38 lies on an abutment 60 Support structure 18. Also in this version the swivel device needs the actuator 42, in the working position of the boom 20, when transmitting the Force moment by the hydraulic cylinder 28 on the boom 20 no reaction forces to record. The latter are, in fact, directly about the Rotary bearing 40, or the abutment 60 is introduced directly into the support structure 18.
  • the position of the swivel arm 38 according to FIG. 7 could also be changed an internal stroke limitation of the hydraulic cylinder 42, i.e. without additional Abutment 60 to be determined on the support structure.
  • the Hydraulic cylinder 42 when the torque is transmitted through the hydraulic cylinder 28 on the boom 20, but absorb tensile forces.
  • the two hydraulic cylinders 28, 42 their minimum length in the rest position.
  • the swinging of the boom 20 from its rest position to its working position is thus by an extension their piston rods. It remains to be noted that it is easily possible is to convert the swivel device such that the swiveling of the Outrigger 20 from its rest position into its working position by retracting the piston rods of the two hydraulic cylinders is effected.
  • the oil intake is for a predetermined swivel angle of the boom 20 of the weaker hydraulic cylinder 42 is of course much less than the oil absorption of the hydraulic cylinder 28.
  • the total oil absorption for pivoting the boom 20 from its rest position to its working position, is consequently greatly reduced by the pivoting power of the hydraulic cylinder 42. From this results that in comparison to the known pivoting devices, the hydraulic cylinder 28, with the same swivel angle and the same total oil absorption of the Swivel device, may have a larger diameter.
  • the contact pressure can accordingly the swivel device by choosing a stronger hydraulic cylinder 28 can be increased without the oil absorption of the swivel device therefore would increase significantly. It should be noted that lower oil consumption not only results in cost savings for the hydraulic system, but in most cases also lower energy consumption enables.
  • the swivel device described is particularly advantageous if a large swivel angle and a large one Contact pressure are required.

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  • Chemical & Material Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Materials Engineering (AREA)
  • Metallurgy (AREA)
  • Organic Chemistry (AREA)
  • Manipulator (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • Jib Cranes (AREA)
  • Transmission Devices (AREA)
  • Surgical Instruments (AREA)
  • Investigating Materials By The Use Of Optical Means Adapted For Particular Applications (AREA)
  • Length Measuring Devices With Unspecified Measuring Means (AREA)
  • Actuator (AREA)
EP98922793A 1997-06-12 1998-05-02 Schwenkvorrichtung mit ausleger Expired - Lifetime EP0988403B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
LU90078A LU90078B1 (de) 1997-06-12 1997-06-12 Schwenkvorrichtung mit Ausleger
LU90078 1997-06-12
PCT/EP1998/002602 WO1998056960A1 (de) 1997-06-12 1998-05-02 Schwenkvorrichtung mit ausleger

Publications (2)

Publication Number Publication Date
EP0988403A1 EP0988403A1 (de) 2000-03-29
EP0988403B1 true EP0988403B1 (de) 2001-08-29

Family

ID=19731691

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98922793A Expired - Lifetime EP0988403B1 (de) 1997-06-12 1998-05-02 Schwenkvorrichtung mit ausleger

Country Status (16)

Country Link
US (1) US6245286B1 (cs)
EP (1) EP0988403B1 (cs)
JP (1) JP4220578B2 (cs)
KR (1) KR100497150B1 (cs)
CN (1) CN1073627C (cs)
AT (1) ATE204913T1 (cs)
AU (1) AU7529998A (cs)
BR (1) BR9809543A (cs)
CZ (1) CZ289865B6 (cs)
DE (1) DE59801329D1 (cs)
LU (1) LU90078B1 (cs)
RU (1) RU2196833C2 (cs)
TW (1) TW428028B (cs)
UA (1) UA54528C2 (cs)
WO (1) WO1998056960A1 (cs)
ZA (1) ZA985067B (cs)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10315007B4 (de) * 2003-04-02 2006-02-23 Thermoselect Ag Schmelzofen und Verfahren zum Entfernen von den Schmelzeablauf verstopfenden Zapfen von Schmelzen
CN102839245A (zh) * 2012-09-04 2012-12-26 无锡市长江液压缸厂 液压泥炮的曲臂与液压缸连接结构
KR101665770B1 (ko) * 2014-10-28 2016-10-13 주식회사 포스코 슬래그 배출 도어장치
CN108034789B (zh) * 2017-12-30 2021-05-14 中钢集团邢台机械轧辊有限公司 一种槽式电弧炉出钢口的填堵设备
CN110220383B (zh) * 2019-06-12 2020-11-03 甘肃金麓银峰冶金科技有限公司 一种固定悬臂式一机两位堵眼机
CN116732266A (zh) * 2023-06-27 2023-09-12 中钢集团西安重机有限公司 一种大回转角度的开铁口机

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL162432C (nl) 1970-11-27 1980-05-16 Wurth Anciens Ets Paul Inrichting voor het stoppen van het afsteekgat van een schachtoven.
SU502030A1 (ru) * 1974-04-26 1976-02-05 Предприятие П/Я Г-4586 Пушка дл забивки летки доменных печей
DE2822605C2 (de) 1978-05-24 1987-01-15 Dango & Dienenthal Maschinenbau GmbH, 5900 Siegen Schwenkvorrichtung, insbesondere für Stichlochstopfmaschinen
US4247088A (en) * 1978-10-05 1981-01-27 Ishikawajima-Harima Jukogyo Kabushiki Kaisha Mud gun
SU857267A1 (ru) * 1979-12-04 1981-08-23 Государственный Ордена Ленина Союзный Институт По Проектированию Металлургических Заводов "Гипромез" Устройство дл открывани и закрывани чугунной летки доменной печи
LU84711A1 (fr) * 1983-03-23 1983-11-23 Wurth Paul Sa Boucheuse pour l'obturation de trous de coulee de fours a cuve
LU84764A1 (de) * 1983-04-21 1983-11-23 Wurth Paul Sa Kompakter schachtofen-stopfkanonenschwenkantrieb fuer grosse schwenkwinkel
LU87926A1 (fr) * 1991-04-26 1992-11-16 Wurth Paul Sa Procede de bouchage du trou de coulee d'un four a cuve et machine de bouchage pour la mise en oeuvre de ce procede
LU88023A1 (fr) * 1991-10-30 1993-05-17 Arbed Lance de soufflage

Also Published As

Publication number Publication date
ZA985067B (en) 1999-01-14
UA54528C2 (uk) 2003-03-17
WO1998056960A1 (de) 1998-12-17
ATE204913T1 (de) 2001-09-15
BR9809543A (pt) 2000-06-20
CN1073627C (zh) 2001-10-24
CZ9904398A3 (cs) 2000-10-11
DE59801329D1 (de) 2001-10-04
KR20010013186A (ko) 2001-02-26
CZ289865B6 (cs) 2002-04-17
TW428028B (en) 2001-04-01
AU7529998A (en) 1998-12-30
RU2196833C2 (ru) 2003-01-20
EP0988403A1 (de) 2000-03-29
KR100497150B1 (ko) 2005-06-29
US6245286B1 (en) 2001-06-12
CN1260008A (zh) 2000-07-12
HK1027598A1 (en) 2001-01-19
JP2002503291A (ja) 2002-01-29
JP4220578B2 (ja) 2009-02-04
LU90078B1 (de) 1998-12-14

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