EP0400385B1 - Presse à refouler volante - Google Patents

Presse à refouler volante Download PDF

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Publication number
EP0400385B1
EP0400385B1 EP90109029A EP90109029A EP0400385B1 EP 0400385 B1 EP0400385 B1 EP 0400385B1 EP 90109029 A EP90109029 A EP 90109029A EP 90109029 A EP90109029 A EP 90109029A EP 0400385 B1 EP0400385 B1 EP 0400385B1
Authority
EP
European Patent Office
Prior art keywords
slab
drive
tool
crank
press
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
EP90109029A
Other languages
German (de)
English (en)
Other versions
EP0400385A2 (fr
EP0400385A3 (fr
Inventor
Wolfgang Dr. Rohde
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.)
SMS Siemag AG
Original Assignee
SMS Schloemann Siemag AG
Schloemann Siemag 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 SMS Schloemann Siemag AG, Schloemann Siemag AG filed Critical SMS Schloemann Siemag AG
Publication of EP0400385A2 publication Critical patent/EP0400385A2/fr
Publication of EP0400385A3 publication Critical patent/EP0400385A3/fr
Application granted granted Critical
Publication of EP0400385B1 publication Critical patent/EP0400385B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B15/00—Arrangements for performing additional metal-working operations specially combined with or arranged in, or specially adapted for use in connection with, metal-rolling mills
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B15/00—Arrangements for performing additional metal-working operations specially combined with or arranged in, or specially adapted for use in connection with, metal-rolling mills
    • B21B15/0035—Forging or pressing devices as units
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J1/00—Preparing metal stock or similar ancillary operations prior, during or post forging, e.g. heating or cooling
    • B21J1/04—Shaping in the rough solely by forging or pressing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J7/00—Hammers; Forging machines with hammers or die jaws acting by impact
    • B21J7/02—Special design or construction
    • B21J7/14—Forging machines working with several hammers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J7/00—Hammers; Forging machines with hammers or die jaws acting by impact
    • B21J7/02—Special design or construction
    • B21J7/18—Forging machines working with die jaws, e.g. pivoted, movable laterally of the forging or pressing direction, e.g. for swaging

Definitions

  • the invention relates to an upsetting press for reducing the slab width in hot wide strip roughing lines, with tool carriers arranged on both sides of the slab edge and receiving the mutually facing pressing tools.
  • a compression press of the type mentioned at the outset is known, for example, from European Patent 0 112 516 and comprises a pair of pressing tools which are arranged on both broad sides of a slab feed line in such a way that their pressing surfaces point towards one another for pressing a slab. At least one of these pressing surfaces is substantially parallel to the slab feed direction; the other press surface is a surface inclined to the slab feed direction.
  • a vibration unit vibrates the pressing tool with the parallel and inclined surface.
  • This known upsetting press further comprises a width control unit for controlling the position of the pressing tool in the slab width direction and a control which detects that the front end of the slab is arranged between the parallel surfaces of the pressing tools and which then actuates the width control device and, after carrying out a predetermined pressing, the vibration unit .
  • a swaging press for reducing the width and thickness of slabs of various widths supplied from a continuous caster is known from German Offenlegungsschrift 25 31 591.
  • the upsetting press With the upsetting press, the slab is repeatedly processed with pressure tools moving against one another, the tool being able to freely follow the advance of the slab and the tools being actuated in such a way that they perform a relatively slow operation and a relatively fast idle run.
  • the upsetting press has at least one pair of edge processing tools, which act normally on the edges of the slab, and means for quickly moving the tools back and forth.
  • the tools for reducing the thickness of the advanced slabs are held in a frame that can be freely pivoted about a crank axis.
  • the crankshaft is driven by a pair of elliptical gears, which are set so that they reduce the angular velocity of the eccentric shafts in question during the operation of the tools and increase them when they are empty.
  • the edge tools for reducing the width of the slab are connected to the crank mechanism by means of interposed hydraulic units so that the edge tools can follow the movement of the slab while working on the slab without the feed movement of the slab being impaired thereby.
  • This known upsetting press is also technically too complex and therefore too expensive.
  • An adaptation to the feed speed of the rolling stock is only possible by changing the gear with the elliptical gears according to the feed speed of the slab.
  • the selected crank radius necessarily results in a certain relationship between the number of strokes and the feed speed of the press tool, which cannot be changed at constant speed of the main drive shaft.
  • An adjustment to the feed speed of the rolling stock is only possible as a result possible that the main drive is driven within a 360 ° rotation at different rotational speeds, the rotational speed in the engagement area must be selected so that the required synchronization between the feed speed of the press tool and the feed speed of the slab occurs.
  • vibrating jaws In the upsetting presses for slabs non-generic stretch forging machines for "rolling out” block, rod or tubular starting workpieces, vibrating jaws are known which are driven by specially designed crank or eccentric drives in such a way that they are in contact with each other during the effective part of their approach Roll on the workpiece, deform it while moving the workpiece to the output side of the machine and then open and swing back to its starting position, lifting off the workpiece.
  • the swing jaws are connected to their crank or eccentric pins via a handlebar to form a four-bar linkage.
  • a stretch forging machine is known from DE-B-1 171 245, which is furthermore characterized by a third link, which is fixedly mounted on the outlet side of the oscillating jaw. This is intended to improve the rolling motion of the vibrating jaws on the workpiece. Accordingly, the shape of the workpiece is designed so that it corresponds sectionally to a roller with a large roller diameter.
  • the vibrating jaws are arranged on two links and a third link rod, the position and operation of which are controlled and the rolling surfaces of the vibrating jaw are designed so that the thickness of the workpiece is in is greatly reduced in a first rolling phase and the material which has just been reduced is smoothed on the surface in a second rolling phase.
  • the tools are generally convex with a first oblique rolling surface at the workpiece inlet and a second oblique rolling surface at the workpiece outlet. Between the first rolling surfaces of the vibrating jaw, the material is reduced in a manner similar to hot rolling in roll stands due to the rolling of the vibrating jaws on the material.
  • U.S. Patent 3,583,192 describes a machine for stretch forging ductile material.
  • the swing jaws are suspended from a handlebar system.
  • the handlebars are not parallel and do not have to be the same length.
  • the handlebars are driven by a crank or eccentric drive.
  • crank angles of the eccentrics are different from one another and arranged in such a way that the eccentric of the handlebar rod, which is connected to the oscillating jaw on the entry side of the machine, runs between 135 ° and 180 ° to that eccentric of the handlebar rod that is on the exit side of the machine with the oscillating jaw is connected, the eccentrics rotating in the same direction of rotation. With the predetermined angular difference of the rotating eccentric rollers, the oscillating jaw should be rolled on the rolling stock.
  • a third handlebar with eccentric drive means that the transport of the material begins at the moment when the oscillating jaws touch the material.
  • the type of stretch-forging machine with its four vibrating jaws comprising the workpiece therefore requires a completely different kinematic movement than the genus of the upsetting presses, which must meet the technological requirements of the desired rolling of the vibrating jaws on the workpiece to be formed.
  • the measures implemented for the kinematics of the vibrating jaws in stretch forging machines cannot be used in the genus of the slab upsetting presses, inter alia for technological reasons.
  • the upsetting press of the type mentioned above is characterized in particular by the fact that the upsetting press, to form a reduction drive, each pressing tool with the associated tool holder can be moved essentially in the direction of the reduction with the aid of a handlebar system actuated by two crank drives, the crank mechanism being on is arranged in a crankcase, the handlebar system consists of two parallel lengths articulated on the tool carrier and each parallel link on the crankcase is assigned a crank mechanism with the same crank radius and crank angle, and that at least one feed drive acting essentially in the direction of the slab feed can be attacked and that between the crankcase and the feed drive there is a fixed connection in the sense of a constructive unit.
  • the feed drive can be synchronized with the reduction drive in accordance with the feed movement of the slab.
  • the handlebar system ensures that the movement of the press tool runs exactly in the normal to the direction of movement of the slab.
  • Pressure tappets can also be used instead of the parallel link.
  • the feed drive is designed as a crank drive or as a toggle lever drive and is synchronized with the main drive for normal movement, i.e. with the reduction drive for the pressing tools.
  • the crank radius of the crank mechanism for example, must be made variable using a sliding block construction.
  • the design of the feed drive as a hydraulic cylinder is particularly advantageous.
  • the movement of the hydraulic cylinder can be controlled in the form of a path / time function so that the synchronization of the pressing tool with the slab to be pressed laterally is ensured for any feed size.
  • the pressing tool is guided by a guide roller which rolls on a guide track which is fixedly arranged in the machine frame.
  • the contour of the guideway is designed such that the normal movement inevitably produces a tangential movement of the order of magnitude, which brings about the required synchronization.
  • the inclination of the guideway can be changed so that with sufficient approximation, the synchronization of the feed speed of the pressing tool with the feed speed of the slab to be pressed occurs even for different sizes.
  • the angular position of the handlebar system is designed in such a way that the tangential force component of the crank mechanism points against the direction of the feed speed of the feed drive during pressing, so that the power of the feed drive becomes part of the forming capacity when reducing the slab width.
  • FIG. 1 shows the horizontal section through a flying working upsetting press 1 designed according to the invention for reducing the width of slabs 2 in a hot wide strip roughing mill, the slabs being fed almost continuously from a slab casting system upstream of the upsetting press but not shown in detail.
  • Driver rollers 3, 4 are arranged in front of the upset press 1 and behind the upset press.
  • the slab 2 passes through the slab crushing stand in the direction of movement provided with number 5.
  • the upsetting press has stands 6.
  • a crankcase 9 is adjustably guided. The crankcase is adjusted with the aid of a mechanical adjustment 31.
  • a hydraulically acting piston / cylinder construction can also be used as the adjusting device, which is supported on the stand 7, 8 in each case.
  • Pressing tools 7 are arranged on both sides of the slab 2, one pressing surface 10 of which runs approximately parallel to the direction of movement 5 of the slab and the other pressing surface 11 of which points somewhat obliquely and against the direction of the slab movement.
  • the pressing tool 7 has a reduction drive 12 acting in the normal direction, ie perpendicular to the slab 2, and a feed drive 13 acting in the tangential direction, that is to say parallel to the slab 2.
  • the reduction drive 12 is formed in that each tool carrier 8 with an associated crankcase 9 with the aid of a of at least one crank mechanism (eccentric 14) actuated steering system (pressure tappet 18) essentially in the direction of reduction is movably connected, the crank mechanism 15 being arranged in the crankcase 9.
  • the feed drive 13 which acts essentially in the direction of the slab feed, engages on the tool carrier 8.
  • Crankcase 9 and the fulcrum 29 of the feed drive 13 are connected to form a structural unit with the aid of the connecting support 30.
  • the link system 16 consists of two parallel rods 17 and 18 articulated on the tool carrier 8 and each of these parallel rods is on the crankcase 9 each a crank mechanism 15 with crankshafts 19, 20 is assigned, the crank radius of which is identical to one another and to which the parallel links are articulated at the same crank angle.
  • the parallel links are articulated on the tool carrier at the same distance from each other.
  • the tangential movement of the press tool is brought about by the feed drive 13, which according to FIG. 2 consists of a crank drive 21.
  • a toggle lever mechanism can be provided with the same advantage.
  • the use of a crank drive for the steering system moving the pressing tool 7 in the normal direction and the use of a crank drive for the feed drive moving the pressing tool in the tangential direction enables, for example, synchronization of the reduction drive and the feed drive in accordance with the feed movement of the slab.
  • the pressing tool 7 can, in rapid succession, adjust the slab's feed speed (without relative movement to the slab) in the normal direction, then push it forward, then move back at a distance from the slab, finally attach it normally to the slab edge and press it again in the normal direction without relative movement to the slab.
  • the feed drive 13 is formed according to FIG. 3 from a piston-cylinder unit 22 whose piston 22 'on the tool carrier 8 and whose cylinder 22 ⁇ is connected to the crankcase 9 or to the connection 30 of the upsetting press.
  • This piston-cylinder unit 22 can be controlled in the form of a path / time function so that the movement synchronization of the pressing tool and slab is ensured for any feed size.
  • the tax or Control technology corresponds to the state of the art and is therefore not explained in detail.
  • FIG. 4 shows the feed drive 13 for the press tool 7 or for the tool carrier 8 with a guide roller 23 arranged on the press tool and running on a guide track 24.
  • the guide track or the guide body 25 forming the guide track is fastened in a suitable manner to the stand 6 by means of a swivel joint 26.
  • the inclination of the guideway can be adjusted in that the guide body can be pivoted in the swivel joint by certain angular amounts.
  • an adjusting mechanism acting on the guide body 25 and on the crankcase is provided, which can consist of an adjusting screw 27 articulated on the guide body 25 and an adjusting nut 28.
  • One with a hydraulic medium can also be used as the adjustment mechanism controllable piston-cylinder unit are provided.
  • the inclination of the guide path of the guide body can be adjusted depending on the selected feed speed of the slab so that the feed speed of the press tool and the feed speed of the slab are equal, so that relative movements between the slab and the press tool during the lateral compression of the Slabs are excluded.
  • the pressing tool 7 can be a highly resilient wear part that can be detachably connected to the tool carrier 8 and provided with pressing surfaces 10, 11.
  • the crank mechanism 15 on the crankcase 9 can be connected on the drive side to a conventional spur gear.
  • the flying upsetting press according to the invention for reducing the slab width can at the same time be connected to conventional devices for reducing the slab thickness.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Forging (AREA)
  • Metal Rolling (AREA)
  • Press Drives And Press Lines (AREA)
  • Straightening Metal Sheet-Like Bodies (AREA)
  • Pharmaceuticals Containing Other Organic And Inorganic Compounds (AREA)

Claims (8)

  1. Presse refouleuse (1) pour la réduction en largeur des brames dans un train ébaucheur à chaud pour des bandes larges, comprenant des porte-outils (8) qui reçoivent des outils de presse (7) agencés des deux côtés au bord des brames et dirigés les uns vers les autres,
    caractérisée en ce que dans ladite presse refouleuse, afin de réaliser un entraînement à réduction (12), chaque outil de presse (7) est susceptible d'être déplacé avec le porte-outil associé (8) sensiblement dans la direction de réduction à l'aide d'un système à bras (16) actionné par deux transmissions à manivelle (15), la transmission à manivelle (15) étant agencée sur un boîtier (9) de manivelle, le système à bras (16) étant composé de deux bras parallèles (17, 18) de même longueur et articulés sur le porte-outil (8), et à chaque bras parallèle (17, 18) est associée une transmission à manivelle (15) respective sur le boîtier de manivelle (9) qui présentent l'une par rapport à l'autre le même rayon de manivelle et le même angle de manivelle, et en ce qu'au moins un entraînement d'avance (13), agissant sensiblement dans la direction de l'avance des brames, est capable d'attaquer le porte-outil (8), et en ce qu'il existe entre le boîtier de manivelle (9) et l'entraînement d'avance (13) une liaison solidaire (30) dans le sens d'une unité de construction.
  2. Presse refouleuse selon la revendication 1, caractérisée en ce que l'entraînement d'avance (13) peut être synchronisé avec l'entraînement de réduction (12) selon la mesure du déplacement d'avance des brames (2).
  3. Presse refouleuse selon l'une ou l'autre des revendications 1 et 2, caractérisée en ce que l'entraînement d'avance (13) est réalisé sous la forme d'un entraînement à manivelle (21), le cas échéant avec un rayon de manivelle variable.
  4. Presse refouleuse selon l'une ou l'autre des revendications 1 et 2, caractérisée en ce que l'entraînement (13) est réalisé sous la forme d'une unité hydraulique à piston-et-cylindre (22).
  5. Presse refouleuse selon la revendication 4, caractérisée en ce que l'unité hydraulique à piston-et-cylindre (22) est déplaçable suivant une fonction course/temps qui permet, en fonction de l'amplitude d'avance désirée, la synchronisation de l'outil de presse (7) avec la brame (2) déplacée pratiquement en continu.
  6. Presse refouleuse selon l'une ou l'autre des revendications 1 et 2, caractérisée en ce que l'entraînement d'avance (13) est réalisé sous la forme d'un rouleau de guidage (23), lequel est en liaison avec une voie de guidage (24).
  7. Presse refouleuse selon la revendication 6, caractérisée en ce que la pente de la voie de guidage (24) est susceptible d'être réglée en fonction de l'amplitude d'avance choisie, de telle manière que la vitesse d'avance de l'outil de presse (7) peut être synchronisée avec la brame (2) qui se déplace pratiquement en continu.
  8. Presse refouleuse selon l'une au moins des revendications précédentes, caractérisée en ce que la position angulaire du système à bras (16) est agencée de telle manière que la composante de force tangentielle de l'entraînement à manivelle (15) pendant la compression est dirigée à l'opposé de la direction de la vitesse d'avance de l'entraînement d'avance (13).
EP90109029A 1989-05-29 1990-05-14 Presse à refouler volante Expired - Lifetime EP0400385B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3917398 1989-05-29
DE3917398A DE3917398A1 (de) 1989-05-29 1989-05-29 Fliegende stauchpresse

Publications (3)

Publication Number Publication Date
EP0400385A2 EP0400385A2 (fr) 1990-12-05
EP0400385A3 EP0400385A3 (fr) 1991-03-13
EP0400385B1 true EP0400385B1 (fr) 1994-07-27

Family

ID=6381577

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90109029A Expired - Lifetime EP0400385B1 (fr) 1989-05-29 1990-05-14 Presse à refouler volante

Country Status (10)

Country Link
US (1) US5077999A (fr)
EP (1) EP0400385B1 (fr)
JP (1) JP2749955B2 (fr)
KR (1) KR0163424B1 (fr)
CN (1) CN1022808C (fr)
AT (1) ATE109036T1 (fr)
DE (2) DE3917398A1 (fr)
ES (1) ES2057256T3 (fr)
LT (1) LTIP1789A (fr)
RU (1) RU1793973C (fr)

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4025390A1 (de) * 1990-08-10 1992-02-13 Schloemann Siemag Ag Stauchpresse zur breitenreduktion von walzgut
DE4029429A1 (de) * 1990-09-17 1992-03-19 Schloemann Siemag Ag Vorrichtung zum wechseln der presswerkzeuge einer stauchpresse
DE4035001A1 (de) * 1990-11-03 1992-05-07 Schloemann Siemag Ag Stauchpresse zur reduktion der breite von brammen in warmbreitband-vorstrassen
DE4035002A1 (de) * 1990-11-03 1992-05-07 Schloemann Siemag Ag Brammen-stauchpresse fuer warmbreitband-walzwerke
DE4035000A1 (de) * 1990-11-03 1992-05-07 Schloemann Siemag Ag Vorrichtung zum verspannen und ausbalancieren von presswerkzeugtraeger und kurbelgehaeuse einer stauchpresse
DE4106490A1 (de) * 1991-03-01 1992-09-03 Schloemann Siemag Ag Verfahren zum betreiben einer stauchpresse
DE4138441C2 (de) * 1991-11-22 2003-06-12 Sms Demag Ag Preßwerkzeug für eine Stauchpresse zur Reduzierung der Brammenbreite in Warmbreitband-Vorstraßen
DE4238154A1 (de) * 1992-11-12 1994-05-19 Schloemann Siemag Ag Hydraulischer Vorschubantrieb für fliegende Stauchpressen
ATE376894T1 (de) * 1997-09-16 2007-11-15 Ihi Corp Plattenpressvorrichtung und verfahren
JP3991127B2 (ja) 1997-09-16 2007-10-17 株式会社Ｉｈｉ 板厚圧下方法及び装置
US7137283B2 (en) 1997-10-14 2006-11-21 Ishikawajima-Harima Heavy Industries Co., Ltd. Plate reduction press apparatus and methods
US6601429B2 (en) 2000-04-12 2003-08-05 Sms Demag Aktiengesellschaft Upsetting tool for forming continuous cast slab in slab upsetting presses
CN101530891A (zh) * 2009-04-03 2009-09-16 中山市胜龙锻压机械有限公司 多轴式肘杆锻压机
EP2478978A1 (fr) 2011-01-21 2012-07-25 Siemens VAI Metals Technologies GmbH Presse à refouler et procédé de refoulement
CN111745112A (zh) * 2020-06-16 2020-10-09 安徽博斯特科技有限公司 一种双辊双支承推杆齿轮直联机构和曲柄压力机

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Publication number Priority date Publication date Assignee Title
DE1171245B (de) * 1956-07-13 1964-05-27 Kocks Gmbh Friedrich Streckschmiedemaschine
US3114276A (en) * 1956-07-31 1963-12-17 Kocks Gmbh Friedrich Device for drawing billet and bar stock
US3333452A (en) * 1965-03-03 1967-08-01 Sendzimir Inc T Reduction of thick flat articles
US3583192A (en) * 1969-02-17 1971-06-08 Kocks Gmbh Friedrich Stretch-forging apparatus and method
DE2030607C3 (de) * 1970-06-22 1979-01-18 Bindernagel, Ali, 5638 Wermelskirchen Vorrichtung zum Streckschmieden
FR2316014A1 (fr) * 1974-04-11 1977-01-28 Tadeusz Sendzimir Procede et appareil pour modifier la section transversale d'une brame
SU858996A1 (ru) * 1979-01-17 1981-08-30 Днепропетровский Ордена Трудового Красного Знамени Металлургический Институт Устройство дл деформировани профилей переменного сечени
DE3376530D1 (en) * 1982-12-01 1988-06-16 Hitachi Ltd Press apparatus for reducing slab width
JPS61222651A (ja) * 1985-03-27 1986-10-03 Ishikawajima Harima Heavy Ind Co Ltd 鍛造プレス装置
JPH0671606B2 (ja) * 1985-10-03 1994-09-14 石川島播磨重工業株式会社 スラブ幅圧下連続鍛造機の圧下機構
JPS62124044A (ja) * 1985-11-22 1987-06-05 Kawasaki Steel Corp 熱間スラブの幅圧下プレス方法及び装置

Also Published As

Publication number Publication date
DE59006558D1 (de) 1994-09-01
CN1047636A (zh) 1990-12-12
US5077999A (en) 1992-01-07
EP0400385A2 (fr) 1990-12-05
JP2749955B2 (ja) 1998-05-13
EP0400385A3 (fr) 1991-03-13
ES2057256T3 (es) 1994-10-16
CN1022808C (zh) 1993-11-24
KR900017759A (ko) 1990-12-19
ATE109036T1 (de) 1994-08-15
LTIP1789A (en) 1995-08-25
RU1793973C (ru) 1993-02-07
DE3917398A1 (de) 1990-12-06
JPH0313221A (ja) 1991-01-22
KR0163424B1 (ko) 1999-01-15

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