EP1033213A2 - Vorrichtung und Verfahren zum Erzeugen einer verdichtender Bewegung in einem Gleitfertiger zum Herstellen von Betongegenständen - Google Patents

Vorrichtung und Verfahren zum Erzeugen einer verdichtender Bewegung in einem Gleitfertiger zum Herstellen von Betongegenständen Download PDF

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Publication number
EP1033213A2
EP1033213A2 EP00660038A EP00660038A EP1033213A2 EP 1033213 A2 EP1033213 A2 EP 1033213A2 EP 00660038 A EP00660038 A EP 00660038A EP 00660038 A EP00660038 A EP 00660038A EP 1033213 A2 EP1033213 A2 EP 1033213A2
Authority
EP
European Patent Office
Prior art keywords
movement
eccentric
compacting
shaft
primary
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Withdrawn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
EP00660038A
Other languages
English (en)
French (fr)
Other versions
EP1033213A3 (de
Inventor
Paavo Ojanen
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.)
Valkeakoski X-Tec Ltd Oy
Original Assignee
Valkeakoski X-Tec Ltd Oy
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 Valkeakoski X-Tec Ltd Oy filed Critical Valkeakoski X-Tec Ltd Oy
Publication of EP1033213A2 publication Critical patent/EP1033213A2/de
Publication of EP1033213A3 publication Critical patent/EP1033213A3/de
Withdrawn legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B28—WORKING CEMENT, CLAY, OR STONE
    • B28B—SHAPING CLAY OR OTHER CERAMIC COMPOSITIONS; SHAPING SLAG; SHAPING MIXTURES CONTAINING CEMENTITIOUS MATERIAL, e.g. PLASTER
    • B28B1/00—Producing shaped prefabricated articles from the material
    • B28B1/08—Producing shaped prefabricated articles from the material by vibrating or jolting
    • B28B1/084—Producing shaped prefabricated articles from the material by vibrating or jolting the vibrating moulds or cores being moved horizontally for making strands of moulded articles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B28—WORKING CEMENT, CLAY, OR STONE
    • B28B—SHAPING CLAY OR OTHER CERAMIC COMPOSITIONS; SHAPING SLAG; SHAPING MIXTURES CONTAINING CEMENTITIOUS MATERIAL, e.g. PLASTER
    • B28B3/00—Producing shaped articles from the material by using presses; Presses specially adapted therefor
    • B28B3/20—Producing shaped articles from the material by using presses; Presses specially adapted therefor wherein the material is extruded
    • B28B3/22—Producing shaped articles from the material by using presses; Presses specially adapted therefor wherein the material is extruded by screw or worm
    • B28B3/228—Slipform casting extruder, e.g. self-propelled extruder
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/26—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks
    • B30B1/266—Drive systems for the cam, eccentric or crank axis

Definitions

  • Elongated concrete products such as hollow-core slabs are conventionally made using extruder-type casting machines or slip-form casting machines.
  • the casting machine is comprised of a conical feed hopper having one or more spiral feed augers adapted thereunder.
  • the auger is frequently followed by a core-forming trowel member which further has an extension serving as the final trowel member that supports the core cavity formed into the product.
  • the core-forming trowel member incorporates a vibrator or similar compacting arrangement for the compaction of the cast concrete into the shape determined by the casting mould and the core-forming trowel members.
  • the casting machine has an upper trowel beam acting as the upper edge of the mould and, frequently, the sides of the mould are also designed to perform as the side trowel beams.
  • trowel beams compact the concrete mix during casting and give the cast product a neat surface finish.
  • vibration can also be employed for compaction.
  • Extruder-type casting machines are designed to operate as continuous-casting machines, which are transferred forward on the mould top by the reaction forces imposed by the feed augers.
  • the compaction of cast concrete mix is accomplished, among other methods, by means of vibrating the mould surfaces that define the product being cast or, in the case of hollow-core slab production, vibrators adapted into the core-forming trowel. Instead of vibration, compaction has also been achieved by relatively slow movements of the different parts of the casting machine that work the cast concrete mix. Such compacting movement has been implemented by means of either a sideways deflected rotational movement of the core-forming trowel member that is secured to the end of the feed auger and/or cyclic deformation of said trowel member, whereby the compaction of the concrete is attained through varying the cross section of the trowel member. For trowel members of noncircular cross section, cyclically reversible rotational movement has been used for compaction.
  • the above-described compacting method is generally called working compaction or shear compaction, and one of its benefits is that the movements and displacements of aggregate particles will be large already at a low number of strokes, that is, at a low frequency of the machine component movements resulting in noiseless operation of the machine.
  • the principle of low-frequency compacting movements has been further developed in a casting machine in which the core-forming members are provided with conical or wedge-shaped surfaces, whereby concrete is compacted by means of slow movements of the core-forming members performed in the direction of the casting flow.
  • compaction is carried out using reciprocating movements with an amplitude of 5 - 50 mm and a frequency of 1 - 10 Hz, which are slow in regard to the amplitudes and frequencies used in vibrating.
  • the machine uses wedge-shaped or conical surfaces which provide flaring or tapering spaces in the direction of the casting flow, said spaces acting as compacting spaces.
  • Compaction has a great impact on the final quality of the product.
  • it is essential to make the concrete mix particulates, that is, the aggregates move relative to each other so as to allow them assume mutual positions of maximum packing density, whereby the concrete becomes compacted.
  • This goal is attained by means of pressure imposed through the mechanical machine parts and by gravitation.
  • the amplitudes and frequencies of the compacting movements may vary widely inasmuch the target is to use the most appropriate compacting method for a particular product and concrete mix being cast.
  • the compacting movement may have a frequency of 1 - 200 Hz and amplitude of 50 - 0.005 mm. Generally, the higher the frequency the lower the amplitude and vice versa.
  • the effect of the compacting movement on the concrete mix being cast may vary within wide limits and good results under different conditions may be obtained by using different amplitudes.
  • the compaction of concrete mix it is typical that large aggregates can be compacted with large-amplitude movements performed at very low frequencies and, respectively, small aggregates require high vibrating frequencies at low amplitudes for good compaction.
  • the composition of a normal concrete mix contains particles of a wide size distribution starting from entirely dust-like binder particles up to aggregates as large as 16 - 32 mm. By varying the size and type of particulate matter, as well as their amount in the mix, it is possible to fabricate products suitable for all kinds of applications.
  • compaction frequency is relatively easy, because electric motors used as drive sources for vibrating means may be controlled over a large rpm range using frequency converters, for instance.
  • compromises must be made in concrete compaction by accepting such a compaction frequency and amplitude that give an acceptably good end result.
  • compaction parameters are kept unchanged without paying attention to the concrete mix composition in regard to its different design proportions, that is, the relative proportions of its components and the aggregate size distribution of the concrete mix used or other mix properties or changes therein.
  • the compaction outcome is either poor or a very high specific compaction energy must be consumed to attain a desired compaction effect.
  • Use of high compaction power causes wear and stress in the machinery, thus necessitating a more frequent maintenance thereof and requiring the casting machine to be dimensioned already at its design stage for high stresses.
  • the compaction efficiency is controlled by altering the frequency of the compacting movement.
  • the frequency control can chiefly affect the compacting power level alone, that is, the amount of energy transferred into the concrete mix.
  • Frequency control does not pay any attention to the properties of the concrete mix nor the aggregate sizes or size distribution thereof. Consequently, current control methods cannot provide full control of the compaction process so that the properties of different concrete mixes could be utilized in an optimum manner without the need for using an unnecessarily large amount of energy in order to achieve a good compaction result.
  • the goal of the invention is achieved by means of generating the compacting movement with the help of two rotary shafts of which the primary shaft has a primary eccentric member adapted thereon and the secondary shaft has a secondary eccentric member adapted thereon.
  • the movement of the primary eccentric member is transmitted to the secondary eccentric member by means of a lever, whereby the eccentricity of both eccentric members determines the angle of the reciprocating rotation of the secondary shaft and, thus the stroke length of one or more crank levers mounted thereon.
  • the crank levers are connected to the members that are desired to perform a reciprocating movement, e.g., swinging levers moving the core-forming trowel members.
  • the assembly according to the invention is characterized by what is stated in the characterizing part of claim 1.
  • the invention provides significant benefits.
  • the invention makes it possible to optimize the compaction power and application technique for different concrete mixes.
  • the compaction process can be governed in different ways. Should the properties or component proportions of the concrete mix vary, the amplitude and frequency of the compacting movement can be readjusted quickly to optimal values for the new composition of the mix. If the aggregate components or other constituents of the concrete mix are changed, the compaction parameters can be readjusted so that no products need to be dumped, but instead, it is possible to make products of good quality immediately or almost directly after a change in mix design.
  • the invention can provide savings in production costs. Less compaction power is needed, which means lower energy costs, as well as less stress and wear on the machine. The lower compaction power level also gives less noise.
  • the invention is more cost-efficient to implement than constructions providing the compacting movement from, e.g., hydraulic cylinders. While hydraulics can be used for implementing a reciprocating variable-amplitude compacting movement, the arrangement would need a high-capacity pressure system and a complicated control system.
  • FIG. 1 therein is shown an extruder-type casting machine in which one of the compacting movements is provided by the rockingly reciprocating movement of the core-forming trowel members 3.
  • the compacting movement and the function of such an extruder is described in EPO Pat. Appl. No. 0,677,362, whose copy is annexed with this application.
  • a casting mould 2 defined by mould walls 7, said mould having thereon an infeed opening 8 for introducing concrete mix into the moulding space.
  • the infeed opening 8 is delineated by a rear wall 9 through which shafts 10 of feed augers 3 can pass.
  • core-forming trowel members 4 having a shape capable of forming core cavities of a desired cross section to the interior of hollow-core slabs to be cast. While in this type of apparatus embodiment, the compaction is particularly implemented with the help of the compacting movement of the trowel members 4, such products as pillars or solid-core slabs must be made using some other member for imposing the compacting movement inasmuch this kind of casting does not use core-forming trowel members.
  • the rocking movement of the core-forming trowel members 4 is achieved with the help of a swinging member 5.
  • the swinging member 5 is adapted to support the shaft 10 of the feed auger 3 and it is connected by two levers 6 to the framework 1 of the apparatus.
  • the typical rocking movement of the core-forming trowel members 4 can be attained under the guidance of said levers 6 as described in cited EPO Pat. Appl. No. 0,677,362.
  • To the swinging member 5 is connected a crank lever 11 which is mounted on a shaft 12 by means of an eccentric member 13.
  • the shaft 12 serves as the secondary shaft of the power transmission chain and is mounted on the framework 1 on bearings adapted to rotate in bearing blocks 15.
  • a primary shaft 14 is mounted above the secondary shaft 12 on the framework 1 in a similar manner on bearings adapted to rotate in bearing blocks 16.
  • the primary shaft 14 includes at its other end suitable means 17 for connecting the shaft to an electric motor or the like power source. While in the illustrated embodiment said means 17 are V-belt pulleys, any conventional power transmission means can be used as well for driving the shaft.
  • a primary eccentric member 18 having a crank lever 19 mounted thereon on a bearing. Also mounted on a bearing, the other end of the crank lever 19 is connected to an eccentric member 20 adapted to the end of the secondary shaft 12.
  • the primary eccentric member 18 has an eccentricity a , and in the illustrated embodiment, the eccentricity of the eccentric member 18 is made adjustable.
  • the eccentricity adjustment can be implemented as a screw adjustment, for instance, either so that the center of rotation of the eccentric member in regard to the center axis of the primary shaft is arranged adjustable by means of coaxial eccentric disks, whose mutual position can be changed, or using an adjustment flange to be described later in the text.
  • the eccentricity control may be arranged if so required to be remote-controlled or controllable from the machine control panel during operation provided that the adjustable eccentric member is complemented with a suitable actuator device.
  • the machine construction cost will be elevated by such a remote control facility, but it can be implemented in a simple manner if so desired by the machine operator.
  • the secondary eccentric member 20 has an eccentricity b and this value must be greater than the eccentricity of the primary eccentric member 18.
  • the function of the apparatus is as follows.
  • the primary shaft 14 is rotated by means of an electric motor, for instance.
  • the speed of rotation of the primary shaft 14 determines the compacting frequency, whose adjustment may be readily implemented with the help of, e.g., a frequency converter connected to supply an electric motor drive.
  • the end (first end) of the lever 19 connected to the primary eccentric 18 rotates about the center axis of the primary shaft 14 along a trajectory determined by the eccentricity a and actuates the end of the lever 19 that is connected to the secondary eccentric member 20.
  • the trajectory of the end of lever 19 connected to the secondary eccentric member 20 is determined by the eccentricities of both eccentric members, the lever length ratios between the eccentric members and the positions of the eccentric members.
  • the eccentricity b of the secondary eccentric member 20 is slightly larger than the eccentricity a of the primary eccentric member 18, whereby the end (second end) of the lever 19 connected to the secondary eccentric 20 cannot traverse over the center axis of the secondary shaft 12, but instead, is forced to move in a reciprocating manner.
  • This reciprocating movement is transmitted to levers 11, which are mounted on the secondary shaft by third eccentric members 13, whereby the levers are at their other ends connected to the swinging member 5.
  • the rotary movement of the primary shaft 14 is converted into a rockingly reciprocating movement of the swinging member 5 and, subsequently, of the core-forming trowel member 5 and the feed auger 3 connected thereto.
  • the lever mechanism 6 of the swinging member 5 controls the movement of the core-forming trowel members in the fashion described in cited EPO Pat. Appl. No. 0,677,362.
  • the angle ⁇ of reciprocating rotation of the secondary shaft 12 is determined by the eccentricity a of the primary eccentric member if the other eccentricity b is fixed and vice versa. Further, for a given setting of these variables, the amplitude of the swinging member stroke is determined by the lever ratio between the lever 11 connected to the swinging member 5 and the eccentric member 13 mounted on the secondary shaft 12 that actuates the lever. Also the position of the swinging lever 11 in regard to the secondary shaft 12 is a variable that affects the stroke length of the swinging member 5. This possibility is utilized in an exemplifying embodiment described later in the text.
  • rotation of the primary shaft 14 at a speed of 1500 r/min gives a compacting stroke frequency of 25 Hz.
  • the adjustment range of the screw or slit adjuster adapted on the primary eccentric member 18 for setting the eccentricity a thereof can be, e.g., 0 - 15 mm, combined with 20 mm eccentricity of the secondary eccentric member. Then, the lever ratio between the swinging levers 11 and the eccentric members 13 mounted on the secondary shaft 12 is determined so that when the eccentricity a of the primary eccentric member is set at its maximum value, also the desired maximum amplitude of the compacting stroke is attained.
  • the stroke amplitude control is implemented in a slightly different manner.
  • the eccentricities a, b of the primary eccentric member 18 and the secondary eccentric member 20 are made fixed, and the amplitude control is accomplished by changing the position of the secondary shaft 12 and the swinging levers 11 mounted thereon in regard to the secondary eccentric 20.
  • this apparatus embodiment is similar to that described above, except for an adjustment flange 21 mounted on the secondary eccentric member 20.
  • Fig. 6 shows the connection of the swinging levers 11 via the eccentric members 13 to the secondary shaft 12. The number of the secondary levers 11 depends on the number of feed augers 3 and core-forming trowel members 4.
  • the swinging levers 11 are adapted to move in cycles of offset phases, and when required, the movements of the feed augers 3 and their core-forming trowel members 4 can be varied in regard to each other by changing their actuator connection angle on the secondary shaft 12.
  • both the secondary eccentric member 20 and the adjustment flange 21 have rings of holes 22 and 23 made on their periphery.
  • the holes are staggered by their mutual distances so as to make the holes coincide in different angular settings when the adjustment flange 21 or, respectively, the secondary eccentric member 20 is rotated.
  • the zero angle between the adjustment flange 21 and the secondary eccentric member 20 is the angle in which the desired direction of the swinging member stroke is parallel to the line drawn via the center of rotation of the eccentric member 13 mounted on the swinging lever 11 and via the center axis of the secondary shaft 12.
  • the rotary movement of the secondary shaft causes the minimum possible movement of the swinging member 5.
  • the lever-eccentric mechanism rotates about the secondary shaft 12 always by a fixed angle ⁇ that in the illustrated construction is 49.24°.
  • the stroke amplitude of the swinging member 5 and the core-forming trowel member 4 actuated thereby is determined by the position of the swinging lever 11 mounted on the secondary shaft.
  • the rotation of the secondary shaft 12 actuates the swinging lever 11 chiefly in the lateral direction in regard to the desired longitudinal direction of compacting movement, whereby the amplitude of the compacting stroke remains small as the lever-eccentric mechanism is in its dead-center point that in the illustrated case is the top dead-center point.
  • the swinging lever 11 connected to said eccentric member moves chiefly in a direction parallel to the compacting movement thus causing a large stroke amplitude.
  • This can be utilized for stroke amplitude control so that the secondary shaft 12 with the adjustment flange 21 mounted thereon is made rotatable in regard to the secondary eccentric member 20.
  • the locking holes 22, 23 made to the secondary eccentric member 20 and the adjustment flange 21 permit the secondary shaft 12 to be locked in different positions so that a suitable position can be found in which the eccentric members mounted on said shaft convert the angle ⁇ of the reciprocating movement of the secondary shaft 12 into a desired stroke amplitude of the compacting movement.
  • the zero angle position of stroke adjustment can be selected to be, e.g., either the top or bottom dead-center point of the mechanism formed by the eccentric member 13 of the secondary shaft with the swinging lever, whereby the adjustment angle ⁇ is defined as the angular deviation of the adjustment flange 21 from said zero angle position.
  • Fig. 7 is plotted the dependence of the stroke length on the adjustment angle ⁇ for the mechanism dimensions given in Fig. 5. Obviously, these dimensions are depicted as an exemplifying case, and the adjustment ranges may vary between different machine and actuator mechanism designs.
  • eccentric members used in the above-described embodiments can be replaced by, e.g., crank mechanisms or other types of mechanisms capable of generating an equivalent actuating movement.
  • the term eccentric mechanism must be understood broadly to refer to any type of assembly suited for converting the rotary motion of at least one machine part into the forced movement of a point, such as the connection point of a cranking lever, along a predetermined trajectory.
  • the adjustment flange attached to the secondary eccentric member can be disposed with by mounting all the eccentric members actuating the swinging levers 11 with the help locking means onto the secondary shaft.
  • the invention may be used for generating compacting movements for other purposes than the actuation of core-forming trowel members alone. If the compacting movement is needed only for one compacting element such as a top trowel beam, the lever or arm actuating said element can be connected directly to the secondary eccentric member that in this case serves as both the secondary eccentric member and the actuating eccentric member of the swinging lever. If a cranking lever mechanism is used to replace the eccentric member mechanism, the primary and secondary eccentric mechanisms can be located centrally between the shafts. Obviously, a plurality of eccentric mechanisms can be mounted in parallel where substantially large compacting power levels must be used. The shafts of the assembly can be substantially shorter than those shown in the diagrams when, e.g., the compacting movement needs to be transmitted to one compacting member alone.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • Chemical & Material Sciences (AREA)
  • Ceramic Engineering (AREA)
  • On-Site Construction Work That Accompanies The Preparation And Application Of Concrete (AREA)
  • Road Paving Machines (AREA)
  • Devices For Post-Treatments, Processing, Supply, Discharge, And Other Processes (AREA)
EP00660038A 1999-03-02 2000-03-01 Vorrichtung und Verfahren zum Erzeugen einer verdichtender Bewegung in einem Gleitfertiger zum Herstellen von Betongegenständen Withdrawn EP1033213A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FI990451A FI115618B (fi) 1999-03-02 1999-03-02 Sovitelma ja menetelmä tiivistysliikkeen aikaansaamiseksi betonin valu koneessa
FI990451 1999-03-02

Publications (2)

Publication Number Publication Date
EP1033213A2 true EP1033213A2 (de) 2000-09-06
EP1033213A3 EP1033213A3 (de) 2002-11-13

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EP00660038A Withdrawn EP1033213A3 (de) 1999-03-02 2000-03-01 Vorrichtung und Verfahren zum Erzeugen einer verdichtender Bewegung in einem Gleitfertiger zum Herstellen von Betongegenständen

Country Status (3)

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EP (1) EP1033213A3 (de)
CN (1) CN1265962A (de)
FI (1) FI115618B (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1952961A3 (de) * 2007-02-05 2010-09-08 Elematic Oy Ab Verfahren und Vorrichtung zum Giessen von Betonprodukten

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102615697A (zh) * 2012-04-13 2012-08-01 河南省四达仙龙实业有限公司 一种空心水泥板成型机的振管

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1369083A (fr) * 1963-09-03 1964-08-07 May Pressenbau Gmbh Presse à levier à genouillère
US4434646A (en) * 1981-12-17 1984-03-06 Aida Engineering, Ltd. C-Frame press
US4674971A (en) * 1984-09-10 1987-06-23 Rakennusvalmiste Oy Concrete slab extruder with shear-action coring members
EP0235114A2 (de) * 1986-01-17 1987-09-02 Lohja Parma Engineering Lpe Oy Gleitfertiger für Hohldielen aus Beton
EP0541963A1 (de) * 1991-10-11 1993-05-19 Lohja Parma Engineering Lpe Oy Verfahren und Vorrichtung zum Herstellen von mit einem gesteuerten Verdichtungsgrad gepressten Gegenständen
EP0677362A1 (de) * 1994-04-07 1995-10-18 Valkeakoski X-Tec Oy Ltd. Verfahren und Vorrichtung zum Herstellen von Betongegenständen
EP0846534A1 (de) * 1996-12-04 1998-06-10 Partek Concrete Development Oy Ab Verfahren und Vorrichtung zum Giessen von Betongegenständen

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1369083A (fr) * 1963-09-03 1964-08-07 May Pressenbau Gmbh Presse à levier à genouillère
US4434646A (en) * 1981-12-17 1984-03-06 Aida Engineering, Ltd. C-Frame press
US4674971A (en) * 1984-09-10 1987-06-23 Rakennusvalmiste Oy Concrete slab extruder with shear-action coring members
EP0235114A2 (de) * 1986-01-17 1987-09-02 Lohja Parma Engineering Lpe Oy Gleitfertiger für Hohldielen aus Beton
EP0541963A1 (de) * 1991-10-11 1993-05-19 Lohja Parma Engineering Lpe Oy Verfahren und Vorrichtung zum Herstellen von mit einem gesteuerten Verdichtungsgrad gepressten Gegenständen
EP0677362A1 (de) * 1994-04-07 1995-10-18 Valkeakoski X-Tec Oy Ltd. Verfahren und Vorrichtung zum Herstellen von Betongegenständen
EP0846534A1 (de) * 1996-12-04 1998-06-10 Partek Concrete Development Oy Ab Verfahren und Vorrichtung zum Giessen von Betongegenständen

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1952961A3 (de) * 2007-02-05 2010-09-08 Elematic Oy Ab Verfahren und Vorrichtung zum Giessen von Betonprodukten

Also Published As

Publication number Publication date
CN1265962A (zh) 2000-09-13
FI115618B (fi) 2005-06-15
EP1033213A3 (de) 2002-11-13
FI990451A0 (fi) 1999-03-02
FI990451A (fi) 2000-09-03

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