EP0516649A1 - Appareil de pliage. - Google Patents

Appareil de pliage.

Info

Publication number
EP0516649A1
EP0516649A1 EP19910903422 EP91903422A EP0516649A1 EP 0516649 A1 EP0516649 A1 EP 0516649A1 EP 19910903422 EP19910903422 EP 19910903422 EP 91903422 A EP91903422 A EP 91903422A EP 0516649 A1 EP0516649 A1 EP 0516649A1
Authority
EP
European Patent Office
Prior art keywords
cams
cover
cam
control
cylinder
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.)
Granted
Application number
EP19910903422
Other languages
German (de)
English (en)
Other versions
EP0516649B1 (fr
Inventor
Emil Fischer
Rudolf Staeb
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.)
Koenig and Bauer AG
Original Assignee
Albert Frankenthal 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 Albert Frankenthal AG filed Critical Albert Frankenthal AG
Publication of EP0516649A1 publication Critical patent/EP0516649A1/fr
Application granted granted Critical
Publication of EP0516649B1 publication Critical patent/EP0516649B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H45/00—Folding thin material
    • B65H45/12—Folding articles or webs with application of pressure to define or form crease lines
    • B65H45/16—Rotary folders
    • B65H45/162—Rotary folders with folding jaw cylinders
    • B65H45/168—Rotary folders with folding jaw cylinders having changeable mode of operation

Definitions

  • the invention relates to a control for folding knives and / or grippers of a collecting cylinder in a folding apparatus of a web-fed rotary printing press according to the preamble of claim 1.
  • the cover device contains a drivable cover plate with fixed cover cams.
  • the cover plate must run not only in the case of collective production, but also in the non-collective production that is common in practice.
  • the number of consecutive collection operations is very limited. Experience has shown that a limit is reached in two successive collection processes. More than two collection processes are practically not possible.
  • the printing press width and with it the forme cylinder diameter increase, so that there are more etchings (sides) on the circumference than before, for example eight etchings on the circumference.
  • the invention has for its object to provide a control for folding knives and / or grippers of a collecting cylinder carrying seven gripper systems and seven folding knife systems with which "partial collecting" is possible.
  • the advantages he achievable with the invention are, in particular, that the number of successive collecting operations and thus the number of possible types of production can be increased with simple and inexpensive means.
  • the following productions are advantageous
  • Partially collecting is understood to mean that, in a production position of the folding apparatus, both non-collected products and collected products are continuously produced, for. B. C; A + B for 6U forme cylinders and A; B + C + D for 8U forme cylinders.
  • Another advantage is that you have practically a kind of variable cover plate and can therefore perform more than two collecting operations.
  • the covering cams can be adjustable by means of an adjusting disk which is coaxial with the cam carrier and which can be driven together with the cam carrier and is adjustable in the circumferential direction relative to the latter.
  • These measures enable simple adjustment of the cover cams by turning the adjusting disk, which enables automatic presetting.
  • the cam carrier and the associated, uniformly drivable adjusting disk can expediently be connected to one another in terms of drive by means of a differential gear which can be adjusted by means of an auxiliary drive device which can be passivated during ongoing production. After the setting has been made, the differential gear practically functions as a rigid transmission element.
  • a further advantageous measure can consist in that the fold knives and the holding elements are assigned Neten cam carrier or adjusting discs are each rotatably connected to each other, preferably releasably braced. These measures enable the two cam carriers or the two adjusting disks to be driven together, which can simplify the construction and at the same time ensures high accuracy.
  • the control cams assigned to the folding knives or holding elements are advantageously axially offset from one another with such a distance that the two assigned covering devices can be placed in between.
  • control cam assigned to the holding elements can preferably be adjusted in the circumferential direction by means of an auxiliary drive device that can be passivated during production. This enables adaptation to the respective production in such a way that shorter formats are released earlier than longer ones.
  • a further advantageous measure to simplify the pressure cam arrangement and the adjusting disks can consist in the fact that the cover device can be driven at different speeds in the case of collective production depending on the number of desired collecting processes.
  • the drive device assigned to the covering devices can have an intermediate shaft which is parallel to the cylinder and through which the cam carrier rect and the adjusting disks can be driven with the interposition of the adjustable differential gear and which, in turn, can be coupled in register by means of a coupling part which is displaceably arranged on it, each with an opposing, freely rotatable drive wheel of different diameter mounted on it, with different limits of a double wheel which can be driven by a cylinder part comb.
  • FIG. 1 shows a longitudinal section through the drive and control device of a collecting cylinder of a folder according to the invention
  • FIG. 2 to 8 views of a variable cover plate according to the invention, provided with cover cams that can be extended and retracted, with a different cam position for different types of production.
  • the collecting cylinder 1 shown in FIG. 1 of a variable folding apparatus as it is usually arranged downstream of a rotary rotogravure printing press, consists of two armatures in the form of a laterally mounted folding blade part 2 and one on top of it, which are star-shaped and uniformly drivable in cross section gelager ⁇ tem gripper part 3.
  • the folding blade part 2 is provided with folding blades 5 which can be actuated by an actuating device 4.
  • the gripper part 3 is provided with gripper bars 8 which can be actuated by an actuating device 6 and are provided with grippers 7.
  • On the bearing pins 9 and 10 of the folding knife partly 2 or gripper parts 3 are attached drive wheels 11 of the same diameter, which can be coupled to achieve a uniform drive with simultaneous adjustment by a lock-up gear, not shown here.
  • control cams 12 and 13 which are provided coaxially to the cylinder axis and are provided in the area of the cylinder end face, are provided
  • Actuators 4 and 6 are scanned.
  • the actuating devices 4 and 6 each contain two feeler rollers 14, 15 arranged side by side on a common axis, of which one feeler roller 14 runs on the respectively associated control cam 12 or 13 and the other feeler roller 15 on one of the control curve 12 or 13 neighboring cover device for lateral covering of the control cam-side control depression 16 runs, by means of which actuation of the folding knife 5 or gripper 7 is effected.
  • the control cams 12 and 13 are seated in the form of an arcuate circumferential contour.
  • control sinks 16 are released with every revolution of the collecting cylinder 1 (non-collecting) or with every nth rotation of the collecting cylinder 1 (collecting) and are otherwise covered laterally.
  • the cover devices are provided with cover cams 17.1-17.7 arranged parallel to the respectively associated control cam 12 or 13.
  • the width of the feeler rollers 14 and 15 corresponds to the width of the tax curves 12, 13 or the cover cam 17.
  • the control cams 12, 13 are at a standstill with respect to the driven collecting cylinder 1.
  • the control cam 12 provided for controlling the folding knives 5 is fixed to a bush 18 which comprises the outer bearing journal 9 and is fastened to the housing.
  • the control cam 13 assigned to the grippers 7 is fixed to a radially outer bush 19 which is rotatably mounted in the machine frame and to which an adjustment pocket 20 is fastened, by means of which control cam 13 can be adjusted in the circumferential direction to adjust the opening time of the gripper 7.
  • the adjustment pocket 20 can be by means of an auxiliary drive device in the form of a
  • Format setting provided auxiliary motor, etc. can be driven or simply operated by hand.
  • the adjustment pocket 20 is secured against twisting during production.
  • the covering cams 17 on ironing devices assigned to the control cams 12 and 13 are driven with respect to the constant control cams 12, 13 during production.
  • a drive sprocket 21 is flanged to the outer drive wheel 11, from which the drive of the two control cams 12 and 13, respectively, associated covering devices is derived.
  • the two cover devices each comprise, as shown schematically in FIG. 2 for the cover devices assigned to the control cam 12 associated with the folding knives, a cam carrier 22 arranged coaxially to the control cam 12, 13 in question, on which the cover cams 17.1-17 are adjustably accommodated in the radial direction.
  • the Circumferential contour 23 of the covering cams 17.1-17.8 corresponds to a circular section with a radius corresponding to the radius of the control depression 16, which is formed outside by a circumferential recess 16, 13, 13.
  • the circumferential contour 23 of the covering cams 17.1-17.8 can be brought from a radially outer active position, which overlaps with the circular arc-shaped contour of the associated control cam 12, 13, into a passive position located radially inside the control depression by adjusting the covering cams 17.1-17.8.
  • the cover cams 17.1-17.8 cover the side of the SenKe 16 as it passes, so that the feeler roller 14 running on the control cam 12 or 13 in question passes over the control depression 16 by the adjacent one on a cover cam 17.1-17.8 running feeler roller 15 is prevented from falling into the control depression 16 and triggering a folding process, as indicated at 15a.
  • the actuating device which is assigned to the folding knife 5 passing through the folding nip in FIG.
  • an adjusting disk 24 which is arranged coaxially with the cam carrier 22 and is axially aligned with the cover cams, is provided, which is provided with fixed control cams 25 and circumferential recesses 26 therebetween.
  • the cover cams 17.1-17.8 are each fastened to a pivot arm 27 pivotally mounted on the cam support 22 with an axially parallel pivot axis and provided with a radially inwardly projecting button 28 which is held in contact with the circumferential contour of the associated adjusting disk 24 by the action of a pressure spring 29.
  • the pressure spring 29 is received in a recess 30 of the associated cover cam 17.1-17.8 and is supported on the one hand at the inner end of the cam-side recess 30 and on the other hand on a pin 31 protruding into the recess 30 and fastened on the cam carrier 22.
  • the adjusting disk 24 and the cam carrier 22 carrying the covering cams 17.1-17.8 are driven uniformly after adjustment of the adjusting disk 24 during operation, so that the covering cams 17.1-17.8 maintain their position caused by the adjusting disk 24 during operation.
  • the drive speed of the entire covering device formed by cam carrier 22 and adjusting disc 24 is selected depending on the respective type of production so that the covering cams 17.1-17.8 issued in each case pass through the control depression 16 such that only the desired number of folding operations is carried out.
  • the two cam carriers 22 and the two adjusting disks 24 of the respectively assigned covering devices can be firmly connected to one another in order to simplify the drive device required for the drive. Accordingly, as can also be seen from FIG. 1, the two control cams 12 and 13 are spaced further apart from one another in the axial direction in such a way that the two cover devices, the are arranged with adjacent cam carriers 22, find space. The back-to-back cam carriers 22 are firmly clamped together by clamping devices.
  • the adjusting disks 24 which reach under the respectively assigned control cam 12 or 13 and cover cams 17.1-17.8 are screwed together with the interposition of a spacer 32, the thickness of which corresponds to the total thickness of the cam carriers clamped together.
  • two bushes 33, 34 are provided in the area between the bushings 18, 19 carrying the control cams 12, 13, the radially inner bush 33 being the cam bearers 22 lying directly against one another and the radially outer sleeve 34 carry the adjusting disks 24 connected to one another with the interposition of the spacer 32.
  • one of the adjusting disks 24 and one of the cam carriers 22 extends with its radially inner edge to the respectively assigned bushing 33 and 34 and is screwed to it.
  • the respective other adjusting disk 24 and the other cam carrier 22 can end further out.
  • the spacer 32 engages with its spacer jaws through this associated window of the cam carrier 22 fastened to the bush 34.
  • the other cam carrier 22 comprises the spacer 32.
  • the bushes 33, 34 carrying the adjusting disks 24 or the cam carriers 22 are rotatably mounted and are provided with flanged drive sprockets 35, 36 of the same diameter at their ends remote from the cylinder are accommodated in a chamber 37 delimited by the housing parts receiving the control cam bushings 18, 19 and accessible from the gearbox 38.
  • the drive sprockets 35, 36 mesh with associated intermediate wheels 39, 40 of the same diameter, which are mounted on the frame side.
  • the intermediate wheel 40 located in the drive train assigned to the cam carriers 22 meshes with a pinion 42 which is wedged onto an intermediate shaft 41 arranged parallel to the cylinder axis outside the collecting cylinder.
  • the intermediate wheel 39 belonging to the drive train of the adjusting disks 24 meshes with an egg Gear ring 43 of a double wheel mounted on the intermediate shaft 41, the two gear rings 43, 44 of which have the same diameter as the pinion 42.
  • This meshes with the input wheel 45 of a differential gear 46 arranged parallel to the axis next to the intermediate shaft 41, the output gear 47 of which meshes with the second ring gear 44 of the double wheel rotatably mounted on the intermediate shaft 41.
  • the differential gear 45 allows the output wheel 47 to be adjusted with respect to the input wheel 45 having the same diameter by means of an auxiliary drive device 48.
  • the auxiliary drive device 48 is passivated, so that the differential gear 45 functions like a rigid double wheel.
  • the adjusting disks 24 can be brought into the desired rotational position by actuating the auxiliary drive device 48.
  • the intermediate shaft 41 mounted in the gearbox 38 is in turn provided with different gear teeth by the drive sprocket 21 flanged to the outer drive wheel 11. speeds can be driven.
  • a double wheel mounted on a pin fastened on the frame is provided with two ring gears 49, 50 of different diameters, which in turn mesh with drive wheels 51, 52 of different diameters freely rotatably mounted on the intermediate shaft 41.
  • These can alternatively be coupled to the intermediate shaft 41 by means of a coupling part 53 which is slidably wedged onto the intermediate shaft 41 and arranged between them.
  • the drive wheels 51, 52 are provided in the region of their mutually facing end faces with two axially projecting coupling claws 54, into which the coupling part 53 can be latched with corresponding recesses 55, so that there is a clear, register-accurate coupling.
  • the coupling part 53 can be displaced from the left engagement position shown in FIG. 1 into a right engagement position by means of a shift lever 56 engaging in a circumferential groove. By corresponding actuation of the shift lever 56, two different speeds of the covering devices can thus be brought about.
  • the cam carrier 22 is provided with eight adjustable cover cams 17.1-17.8 » the circumferential contour 23 of which each has a degree of about 10-20 °.
  • the eight cover cams 17 are divided into two groups of four offset cams 17.1, 17.2, 17.3, 17.4 in the first group and 17.5, 17.6, 17.7, 17.8 in the second group, each offset by 180 ° from one another.
  • Two cover cams 17.1 - 17.5; 17.2 - 17.6; 17.3 - 17.7 and 17.4 - 17.8 are diametrically opposed.
  • the adjusting disk 24 is provided with six fixed circumferential cams 25.1 to 25.6, which are arranged in two groups of three circumferential cams 25.6, 25.1, 25.2; Distribute 25.3, 25.4, 25.5.
  • the circumferential cams 25.1 to 25.6 of the adjusting disk 24 have different circumferential lengths.
  • the distance between two cover cams is in each case determined from half the circumferential contour length to half the circumferential contour length Measure with the cover cams 17.1 - 17.8 in the extended state.
  • This distribution of the covering cams 17.1 - 17.8 and the circumferential cams 25.1 - 25.6 with the circumferential recesses 26 between the circumferential cams 25.1 - 25.6 each allow the adjustment disk 24 together with the different drive speeds in the present seventh collecting cylinder 1 to produce any desired type of production No collecting when using 40-, 6ü- or 8ü-form cylinders (A + B; A + B + C; A + B + C + D); Two compartments with 4 or 8U form cylinders (AB; AB + CD); Triple collection when using 6U form cylinders (ABC); Quadruple collection when using 8-cylinder (ABCD); Partial collection when using 6ü form cylinders (AB + C); Partial - collecting when using 8ü form cylinders (A + BCD).
  • the setting of the adjusting disk 24 on which FIG. 2 is based on the cam carrier 22 and thus on the covering cams 17.1-17.8 corresponds to the production type non-collecting with either 4-cylinder, 6-cylinder or 8-cylinder cylinders, resulting in a single-layer product.
  • the adjusting disc 24 is adjusted so that none of the covering cams 17.1-17.8 is issued, ie each row of folding knives 5 performs a folding process, each row of grippers 7 opens during the folding process. Because each of the seven rows of folding knives 5 or rows of grippers 7 finds a released control sink 16 with each collecting cylinder revolution and carries out a folding process. The same naturally also applies to the gripper rows 7. None of the cover cams 17.1 - 17.8 has been issued.
  • the Drive speed, ie the speed of the Nockentr ger 22 and the adjusting disks 24 is 7/8 the speed of the collecting cylinder, which carries seven folding blades and rows of grippers.
  • the setting of the adjusting disk 24 on which FIG. 3 is based corresponds to the type of production double collecting when using 4U or 8ü form cylinders.
  • the result is a two-layer product.
  • the switching cams 17.1 and 17.4 or 17.5 and 17.8 have been issued, the switching cams 17.2 and 17.3 or 17.6 and 17.7 have been retracted.
  • the drive speed of the cam carrier 22 and the adjusting disk 24 is 7/8 of the speed of the collecting cylinder 1. With every second collecting cylinder revolution, the control roller of each row of folding knives 5 or row of grippers 7 finds a free control depression 16 and carries out a folding process or the row of grippers opens 7.
  • the setting of the adjusting disk 24 on which FIG. 4 is based corresponds to the production type triple collecting when using 6U forme cylinders.
  • the result is a three-layer product.
  • the first and third switch cams 17.1 and 17.3 or 17.5 and 17.7 have been issued, switch cams 17.2 and 17.4 or 17.6 and 17.8 have been retracted.
  • the drive speed of the cam carrier 22 and adjusting disk 24 is 7/6 the speed of the collecting cylinder 1.
  • the control roller of each row of folding blades 5 or row of grippers 7 finds a free control depression 16 and carries out a folding process or the row of grippers 7 opens .
  • the control roller of each row of folding knives 5 or row of grippers 7 finds a free control depression 16 and carries out a folding process or row of grippers 7 opens.
  • the setting of the adjusting disk 24 on which FIG. 6 is based corresponds to the production type partial collection when using 6U forme cylinders, i. H. six benefits (e.g. A, B, C, A, B, C) around its scope.
  • the result is a single-layer plus a two-layer product.
  • the switching cams 17.2 and 17.6 are on, the switching cams 17.1, 17.3, 17.4, 17.5, 17.7 and 17.8 are retracted.
  • the drive speed of the Nockentr ger 22 and the adjusting disc 24 is 7/6 the speed of the collecting cylinder 1.
  • Each field on the collecting cylinder 1 is controlled so that after one revolution the row of folding knives 5 or row of grippers 7 finds the control roller of a control sink 16 and then then must run twice until it finds a free tax sink 16 again.
  • the setting of the adjusting disk 24 on which FIG. 7 is based corresponds to the production type partial collection when using 8U forme cylinders, ie eight Benefits (e.g. A, B, C, D, A, B, C, D).
  • the result is a single-layer plus a three-layer product.
  • the S chaltnocken 17.2 and 17.4, 17.6 and 17.8 are issued, the operating cams 17.1 and 17.3 or 17.5 and 17.7 are retracted.
  • the drive speed of the cam carrier 22 and adjusting disk 24 is 7/8 the speed of the collecting cylinder.
  • Each field on the collecting cylinder 1 is controlled in such a way that after rotation the row of folding knives 5 or gripper 7 finds the control roller of a control depression 16 and then has to revolve three times until it finds a free control depression 16 again.
  • the structure and the mode of operation of the covering device assigned to the gripper control correspond to the covering device of the folding knife control on which the FIGS. 2 to 8 are based only with the difference that the grippers 7 holding the beginning of the sheet have already passed through the folding gap when the folding operation is carried out.
  • the activation of the folding knife 5 and the opening of the gripper 7 therefore take place essentially simultaneously.
  • these processes extend over a certain period of time, the opening of the grippers 7 should take place somewhat earlier when processing short products
  • the gripper strips 8 and the folder 5 are divided over the cylinder length, with each cylinder side being assigned its own control device.
  • the construction of these two control devices can correspond to the construction shown in FIG. 1 of the control device for the right half of the cylinder, only with the difference that the intermediate shaft 41 cannot be coupled to the cylinder drive via an associated claw coupling, but by means of a lock-up shaft 57 with the opposite intermediate shaft 41 is connected, as shown in Figure 1. This results in a common drive shaft that runs through the entire cylinder width.
  • the adjustment of the cover cams takes place by means of assigned adjusting disks 24, which is automatically preset by appropriate programming of the
  • Auxiliary drive device (48) allows. However, it would also be easily conceivable to set the cover cams 17.1-17.8 individually by hand according to appropriate instructions. Here, the cam carrier 22 would simply have to be provided with suitable clamping devices for holding the cover cams 17.1-17.8. To set the different types of production, the adjusting disc 24 is adjusted with the circumferential cams 25.1 to 25.6 so that the cover cams 17.1 to 17.8 are brought into a position in which the gripper rows and folding knife rows are activated at the right time.
  • 4ü- 6U-, 8U-form cylinder means that 4 (e.g. A, B, A, B) or 6 (e.g. A, B, C, A, B,) evenly distributed around the circumference of the form cylinder C) or 8 (e.g. A, B, C, D, A, B, C, D) equally long panels (pages) are arranged.
  • 4U, 6ü and 80 are of equal length and can vary in the permissible format range.

Landscapes

  • Folding Of Thin Sheet-Like Materials, Special Discharging Devices, And Others (AREA)

Abstract

Un appareil de pliage utilisable tant en production par assemblage qu'en production sans assemblage comprend un cylindre d'assemblage (1) pourvu de griffes (7) et de plioirs (5). Les éléments de retenue et les plioirs sont reliés à des éléments d'actionnement de préférence sous forme de rouleaux danseurs (14, 15) commandables par des courbes de commande correspondantes (12 ou 13) et dont la zone de commande, qui forme de préférence une dépression de commande (16), peut être libérée ou recouverte sélectivement par un dispositif de recouvrement pourvu d'une came de recouvrement (17) montée dans un porte-came (22) entraînable coaxial à la courbe de commande (12 ou 13). Etant donné que les cames de recouvrement (17.1 - 17.8) de chaque dispositif de recouvrement sont radialement réglables sur leur porte-came correspondant (22), on peut effectuer avec cet appareil de pliage une grande diversité de processus d'assemblage.
EP91903422A 1990-02-19 1991-02-19 Machine rotative d'impression avec appareil de pliage Expired - Lifetime EP0516649B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE4005195 1990-02-19
DE4005195 1990-02-19
DE4041613 1990-12-22
DE4041613A DE4041613A1 (de) 1990-02-19 1990-12-22 Falzapparat
PCT/DE1991/000126 WO1991012195A1 (fr) 1990-02-19 1991-02-19 Appareil de pliage

Publications (2)

Publication Number Publication Date
EP0516649A1 true EP0516649A1 (fr) 1992-12-09
EP0516649B1 EP0516649B1 (fr) 1995-05-24

Family

ID=25890305

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91903422A Expired - Lifetime EP0516649B1 (fr) 1990-02-19 1991-02-19 Machine rotative d'impression avec appareil de pliage

Country Status (5)

Country Link
US (1) US5287805A (fr)
EP (1) EP0516649B1 (fr)
JP (1) JPH0780618B2 (fr)
DE (2) DE4041613A1 (fr)
WO (1) WO1991012195A1 (fr)

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DE4408202C2 (de) * 1994-03-11 1999-02-25 Roland Man Druckmasch Falzzylinder
DE19625084C2 (de) * 1996-06-22 2000-12-14 Koenig & Bauer Ag Zylinder
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EP1754602A3 (fr) * 2003-04-23 2007-03-28 Koenig & Bauer Aktiengesellschaft Machine d'impression rotative
DE102004020305A1 (de) * 2004-04-26 2005-11-17 Koenig & Bauer Ag Falzapparat für Sammelbetrieb
DE102005017232B4 (de) * 2005-04-14 2016-04-28 Manroland Web Systems Gmbh Sammelzylinder eines Falzapparats einer Druckmaschine
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JP5210082B2 (ja) * 2007-08-03 2013-06-12 株式会社小森コーポレーション シート状物の搬送装置
EP2030931B1 (fr) * 2007-09-03 2013-06-12 Koenig & Bauer Aktiengesellschaft Appareil de pliage variable et imprimantes dotées d'un appareil de pliage
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Also Published As

Publication number Publication date
US5287805A (en) 1994-02-22
JPH0780618B2 (ja) 1995-08-30
WO1991012195A1 (fr) 1991-08-22
JPH05502849A (ja) 1993-05-20
EP0516649B1 (fr) 1995-05-24
DE4041613A1 (de) 1991-08-22
DE59105593D1 (de) 1995-06-29

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