EP0605443A1 - Frictional force compensation for laundry mangles. - Google Patents
Frictional force compensation for laundry mangles.Info
- Publication number
- EP0605443A1 EP0605443A1 EP92917609A EP92917609A EP0605443A1 EP 0605443 A1 EP0605443 A1 EP 0605443A1 EP 92917609 A EP92917609 A EP 92917609A EP 92917609 A EP92917609 A EP 92917609A EP 0605443 A1 EP0605443 A1 EP 0605443A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- laundry
- roller
- trough
- ironing
- force
- 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
Links
Classifications
-
- D—TEXTILES; PAPER
- D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
- D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
- D06F67/00—Details of ironing machines provided for in groups D06F61/00, D06F63/00, or D06F65/00
- D06F67/10—Driving arrangements
Definitions
- the invention relates to a laundry ironer with at least one ironer roller, which is held by means of at least one support arm in a heatable trough in an operating position in which by means of at least one adjusting means, the ironer roller and the ironer body assume a movable position relative to one another, which together for the passage of laundry items limit an inlet and an outlet side.
- a laundry ironer is known from PCT / WO 85/03313, in which there are several ironer rollers arranged in series one behind the other.
- a somewhat parallel, preferably coaxial adjustment of the longitudinal axes of the roller and trough half cylinders can be achieved, which is to ensure smooth operation of the laundry mangle.
- a complete swiveling in and out of the mangle roller in or out of the trough is possible in order to have free access to the trough, for example for the purpose of removing stuck laundry items, cleaning and / or ventilation.
- the respective mangle roller is rotatably supported at the ends of its bearing axis in a pair of support arms which can be pivoted up and down about a fixed bearing point by means of a working cylinder.
- the within a narrow range adjustable storage in the form of the bearing point in order to ensure smooth operation of the laundry shortage, is then set such that, if possible, a coaxial operating position between the shortage roller and the associated trough is achieved; a position which is then fixed in the relevant operating position.
- the driven ironing roller due to its torque, the driven ironing roller has the tendency to move towards the trough on the inlet side of the laundry shortage, which reduces the distance between the ironing roller and trough on the inlet side, so that there are increased friction values at this point.
- the friction on the trough surface changes in an irregular and unpredictable manner, for example due to uneven heating or when items of laundry are introduced, which have different sizes, thicknesses and also coefficients of friction and are carried along by the roller surface and rubbed along the trough surface .
- the DD-PS 24 331 is a generic laundry shortage Known, in which the ironing roller and the trough assume a movable position relative to one another during operation of the laundry ironer by means of an adjusting means.
- the ironer roller is supported on both sides on a support arm, by means of which it can be swung out and on the swivel axis of which a drive wheel for the ironer roller is arranged. Defect roller and drive wheel are connected to each other via a gear engagement.
- the known trough lack provides that between the gear wheel of the roller axis, which has the same or approximately the same diameter, and the actual drive wheel an intermediate wheel is provided on the support arm, which can also be swung out. Furthermore, a spring force accumulator acting on the support arm is provided as the adjusting means. Admittedly, the known harmful iron pressure can be eliminated with this known laundry mangle. In this case, however, forces occur which press the mangle roller against the trough on the inlet side and move away from the trough on the outlet side. This leads to an increase in the frictional force and thus to an uneven and excessive ironing pressure on the inlet side with the disadvantages mentioned at the beginning.
- the ironer roller is rotatably suspended in support arms forming a rocker arm, which is attached to a ironer in such a way that it runs obliquely upwards from the roller axis to the stator suspension, wherein seen in the direction of rotation, an angle between 0 ° and 90 ° results between the rocker and a horizontal line through the center of the roller.
- This angle is selected, the greater the contact pressure of the roller on the trough, and the greater the frictional force between the mangle roller and trough.
- the trough is adjusted by means of an adjusting means in the form of a spring force chers resiliently pivoted.
- the known friction force can only partially compensate for the friction force occurring, and in particular the ironing pressure can neither be set constantly nor increasingly towards the outlet side.
- the platen roller is pivotally mounted via a pair of support arms and, in the pivoted-in state, is gripped by a bow trough designed as a half-shell, the free ends of which by means of a mechanism or can be controlled with a heating medium in such a way that they move towards each other during operation to increase the ironing pressure, the distance between the ironing roller and the trough being reduced on the inlet side and on the outlet side.
- the defective roller can be lifted out simultaneously by means of the two support arms.
- the invention has for its object to provide a laundry deficiency in which the disadvantages described are avoided. This problem is solved by a lack of laundry with the combination of features of claim 1.
- a force can be exerted on the ironing roller and / or the trough, which take up a movable position in relation to one another in operation, by means of the respective adjusting means, which counteracts the frictional force occurring during operation of the laundry shortage in such a way that a constant or is set to increasing bracket pressure towards the outlet, is a dynamic adjustment of the position of The mangle roller and trough reach each other during operation of the laundry mangle, in which the magnitude of the force compensating the frictional force increases or decreases, depending on whether the frictional force acting between the mangle roller and the trough increases or decreases.
- the distance between the platen roller and the trough on the inlet side increases and decreases on the outlet side during operation.
- the respective adjustment means acts in such a way that the ironing or plate pressure increases constantly towards the outlet side, an increased deficiency can be achieved. Due to the relatively high temperature difference between the items of laundry entered on the inlet side and the heating temperature in the ironing gap there, improved drying results can no longer be achieved even at relatively high ironing pressures. However, this improves if the temperature difference has decreased after passing through the respective trough. If a correspondingly high ironing pressure is then applied on the outlet side, significantly improved heat transfer coefficients result on average.
- the lack of performance compared to a lack of laundry with constant ironing pressure in the case of a lack of laundry designed for this purpose the entire trough surface is significantly increased, but without there being wear on the laundry items and / or the defect.
- the mangle performance can be optimized in such a way that a uniform ironing pressure is set by means of the adjusting means in the roller with trough which follows immediately in the transport direction and that the ironing pressure is reduced in the last roller with trough to the exit side.
- the ironing roller arranged last seen in the direction of transport brings out the items of laundry which have already dried, without causing unnecessary overheating on the outlet side, which would damage the items of laundry.
- two working cylinders are provided, one of which absorbs the drive-side drive torque. Due to this arrangement, with two working cylinders of the same design and with a shortened lever arm on the so-called exhaust air side of the laundry shortage, a uniform ironing pressure can be generated within the trough, which lowers the manufacturing costs of the laundry shortage according to the invention.
- Fig.l is a side view of the drive side of a laundry jacket with a friction force compensation by an obliquely acting working cylinder and with a movable roller bearing;
- FIGS. 2 and 3 show a side view of a laundry mangle with spring-supported roller storage or a modified embodiment of the goods storage
- FIG. 4 shows a side view of a laundry ironer with a resiliently supported trough which is adjustable relative to the stationary ironer roller;
- FIG. 5 shows a side view of a laundry lack with a compensation of the frictional force caused by the roller drive forces
- FIG. 7 shows an embodiment of a laundry mangle corresponding to FIG. 5 with a stationary mangle roller and adjustable trough and
- FIG. 8 shows a side view corresponding to FIG. 1 from the suction side of a laundry shortage.
- the ironing roller 10 is rotatably mounted on a pair of lever arms 12 in bearings 14 and is driven in the counterclockwise direction according to the direction of the arrow, seen in FIG.
- a Häzyli ⁇ der 16 attacks, through which the roller 10 about a pivot axis 18 in a known manner both up and down from or into the here ⁇ firmly arranged heated bow trough 20 can be pivoted.
- the pivot axis 18 is formed, for example, by a torsion shaft which connects the two arms of the pair of lever arms 12 as part of the lever linkage.
- the laundry items 22 pass through the mangle from the input side to the output side, that is to say seen from the left to the right in the direction of the arrow in FIG.
- the bearing axis 24 held in the two bearings 14 on the end side has essentially a horizontal orientation and extends transversely to the longitudinal directions of the two arms of the pair of lever arms 12.
- the bearing axis 24 essentially coincides with the longitudinal axis of the heatable trough 20, and is therefore ko ⁇ to this axially arranged.
- the fictitious longitudinal axis of the trough 20 is obtained in this case if the ends of the trough 20 which are free upwards are connected to one another by means of a fictitious plane and a line is drawn approximately centrally between the two free ends.
- the pivot axis 18 forming a bearing point at the ends of the respective lever arm is supported with its two end pins in a pair of levers 26 forming a further part of the lever linkage, the levers of which are each pivotable about a pivot pin 28 and via a linkage part 30 are connected to the bow trough 20.
- the position of this pair of levers 26 can be determined with the aid of two actuators 32 and 34, which limit the pivoting range, with one that can be predetermined Set game.
- a threaded rod 36 articulated on the trough 20 is passed through an eyelet at the free end of one arm of the pair of levers 26, on the right and left of this lever, as seen in the figure, which, for example, as a screw head or Actuators 34 and 32 designed as adjusting screws are arranged.
- An adjusting device for this purpose should preferably be provided for both levers of the pair of levers 26.
- the pair of levers 26 can thus be moved freely with play along the threaded rod 36 and is limited in movement in particular by the actuator 34.
- the possible swivel range of the pair of levers 26 is shown in FIG. 1 by double arrows.
- the working cylinder 16 which acts on the pair of lever arms 12 at the front, is arranged at an angle such that, in addition to a vertically directed force component, it can also exert a horizontal force component on the bearing axis 24 which corresponds to the horizontal force component of the frictional force R counteracts and essentially corresponds to this in size, so that the ironing roller 10 counteracts the direction of the frictional force R from the trough surface on the inlet side to the side Reduction of the normal voltage acting there is pushed away.
- the magnitude of the frictional force R can be calculated or measured. For the rest, their size and direction are largely known on the basis of empirical values in the case of insufficient operation. On the basis of the values for the frictional force R obtained in this way, the angle of attack of the working cylinder 16 and the force to be applied by it can be derived.
- the working cylinder 16 set a fixed, enlarged distance or reduced distance on the inlet side or on the outlet side between the bow trough 20 and the ironing roller 10.
- the ironing roller 10 is not fixed with its pivot axis 18, but rather is pivotably mounted in the direction of the double arrows by means of the pair of levers 26 with a play that can be predetermined, the lack of laundry during operation provides a dynamic balancing of forces in which the mangle roller 10 to the trough 20 automatically adjusts as a function of the friction values that occur in such a way that the friction values are compensated.
- the working cylinder 16 acts as a type of damping member that elastically cushions the loads that occur and also to minimize the Contributes to the coefficient of friction.
- the working cylinder 16 is articulated with its direction of force running vertically on the pair of lever arms 12.
- the adjusting means or the force-generating device is formed by a spring accumulator in the form of a compression spring 38 which is movably guided on the rod 36 and which, seen in the figure, shows the lower end of the lever of the pair of levers 26 assigned to it to the left, i.e. during the Operation in the trough 20 rotating counterclockwise and rubbing therein roller 10, tries to push to the right against the acting frictional force R.
- the size of the spring pressure is set at start-up by actuating the actuator 34 in accordance with the average friction force to be expected, which can be calculated, measured or also obtained from empirical values.
- the possible swivel range of the pair of levers 26 is again shown in FIG. 2 by double arrows.
- the actuator 32 also serves to safely limit the relevant range of movement of the pair of levers 26 and could also be omitted.
- the corresponding floating bearing of the pivot axis 18 in turn provides a dynamic adaptation to changing friction values by means of the adjusting means, here in the form of the compression spring 38.
- the mounting of the pivot axis 18, and therefore the respective bearing point is provided in an elongated hole 40 of a stationary stand 42 instead of on a pair of levers 26, as shown in FIGS. 1 and 2.
- the pivot axis 18 is adjustable by means of adjusting means, which are also formed by actuators 32 and 34, wherein here the compression spring 38 tries to press the bearing of the pivot axis 18 or the respective pin of the torsion shaft in FIG. 2 from left to right against the stop of the actuator 34.
- the resilient mounting is preferably to be provided on both sides or both ends of the pivot axis 18 of the pair of levers 12.
- the trough 20 can be moved on rollers 46 when the bearing axis 24 is mounted in a fixed position.
- the force of a compression spring 38 can be adjusted by means of an actuator in the form of an adjusting screw 34.
- This spring 38 which presses the trough 20 in the horizontal direction, acts here in the same way as in the setting device according to FIGS. 2 and 3. Thanks to the force of the compression spring 38, the trough 20 is moved to the left in FIG that the bracket pressure increases on the outlet side and decreases on the inlet side until a substantially constant surface pressure prevails along the entire bracket gap.
- a limiting member 39 is provided in the form of an adjusting screw, which takes a predetermined distance from the trough 20, so that there is little play between the adjusting screw 39 and trough 20.
- 5 and 6 show an embodiment in which the drive torque exerted on the roller 10 and which also causes the roller friction is largely compensated for.
- the drive torque itself serves to compensate for the frictional force occurring between the roller 10 and the trough 20.
- the mangle roller 10 which is again mounted on a pair of lever arms 12, is driven by a drive unit seated on the bearing axis or on the shaft 24 of the mangle roller 10, consisting of a motor 48 and a gear 50. From this drive unit 48, 50 extends 5 seen downward away a second lever arm 56 formed by two webs 52, 54.
- a rod 58 is articulated on this lever arm 56, which rod applies a force exerted by the lever arm 56 to a stationary steered forwarded angle lever 60, which deflects the force upward by approximately 90 ° in FIG. 5 and delivers it to a further rod 62.
- This actuates a further second angle lever 64, which is articulated on the stationary trough 20 and which transmits the force transmitted by the rod 62 to the lever arm 12 deflected by a further 90 °.
- the angle lever 64 comes close to the pair of levers 26 of the exemplary embodiments according to FIGS. 1 and 2, only that the compensating force is formed here directly by the drive torque of the roller 10, which is generated by means of the lever linkage 56, 58,60,62, 64,12 is transferred to the bearing axis 24.
- FIG. 7 An arrangement corresponding to FIGS. 5 and 6 is shown in FIG. 7.
- the mangle roller 10 is held stationary with its bearing axis 24 and the trough 20 is movably held via a floating bearing in the form of the rollers 46.
- the torque-free mounting of motor 48 and gear 50 within the second lever arm 56 leads to a rotational movement of the second lever arm 56 in the clockwise direction in the drive direction of the ironing roller 10 shown in FIG.
- the trough 20 is moved to the left over the rollers 46 in FIG. 7 from its position shown there via the lever rods, consisting of the parts 58, 60, 62, 64 and 66, with the outlet side the temple gap narrowed.
- the lever rods consisting of the parts 58, 60, 62, 64 and 66
- sensor elements such as are disclosed in PCT / WO 85/03313, for measuring the surface pressure within the ironing gap between the ironing roller 10 and the ironing recess 20.
- the values determined in this way could then be forwarded via a control device to actuators (not shown), which then move the ironing roller 10 and / or the bow trough 20 relative to one another in order to produce a uniform surface pressure, depending on the circumstances.
- actuators can be formed from working cylinders, which act on the end for adjusting the roller 10 on its bearing axis 24.
- the compensating force such that not only the frictional force is compensated, but also that the laundry inlet gap on the inlet side becomes somewhat larger than the outlet gap on the outlet side, so that the laundry items run into the To ease deficiency.
- FIG. 8 shows the so-called exhaust air side of the lack of laundry. This also represents the rear of the ironing roller 10 and an exhaust air opening 66 provided in the center of the bearing 14 is connected in a known and therefore not shown manner to a distributor network of a steam exhaust system. Since on the exhaust air side of the laundry shortage the working cylinder 16 arranged there does not have to take up the transmission-side drive torque, but can only do this via the working cylinder 16 according to FIG. 1, the working cylinder 16 according to FIG. 8 only needs a shorter lever arm of the pair of lever arms 12 to attack, whereby, as shown in particular in FIG. 8, a uniform ironing pressure is achieved. The working cylinder 16 according to FIG. 8 could also act on a longer lever arm, as shown in FIG.
- a working cylinder 16 for support on each arm of the pair of lever arms 12.
- a working cylinder (not shown) arranged, for example, centrally in its longitudinal direction.
- the triangle of forces for the working cylinder 16 shown there is also indicated with vector arrows in FIG.
- the working cylinders 16 can work with a calculated, predeterminable force to compensate for the frictional force, so that a kind of static arrangement is given.
- dynamic compensation would also be conceivable, in which, for example, the respective cylinder 16 is constantly compensated for by a computer unit using appropriate sensors in the bracket column.
Landscapes
- Engineering & Computer Science (AREA)
- Textile Engineering (AREA)
- Treatment Of Fiber Materials (AREA)
- Rolls And Other Rotary Bodies (AREA)
- Main Body Construction Of Washing Machines And Laundry Dryers (AREA)
Abstract
Une calandre à linge comprend au moins un cylindre de calandre (10) retenu dans une position de fonctionnement dans une cuvette chauffable (20) au moyen d'au moins un bras de support (12). Le cylindre de calandre (10) et la cuvette (20) peuvent prendre des positions relatives mobiles, au moyen d'au moins un organe de réglage, afin de délimiter ensemble un côté d'admission et un côté de sortie de pièces de linge (22). Au moyen de l'organe de réglage, on peut exercer sur le cylindre de calandre (10) et/ou sur la cuvette (20) une force qui compense la force de frottement générée pendant le fonctionnement de la calandre, de façon à régler une pression de repassage constante ou croissante du côté de la sortie. La force de frottement (R) générée pendant le calandrage est ainsi compensée, ce qui permet d'effectuer le calandrage en douceur et sans usure. En outre, la capacité de la calandre par rapport aux calandres connues est augmentée.A laundry calender includes at least one calender cylinder (10) retained in an operating position in a heatable bowl (20) by means of at least one support arm (12). The calender cylinder (10) and the bowl (20) can assume movable relative positions, by means of at least one adjusting member, in order to delimit together an inlet side and an outlet side of laundry items ( 22). By means of the adjusting member, a force can be exerted on the calender cylinder (10) and / or on the bowl (20) which compensates for the frictional force generated during the operation of the calender, so as to adjust a constant or increasing ironing pressure on the outlet side. The friction force (R) generated during calendering is thus compensated, which makes it possible to perform calendering smoothly and without wear. In addition, the capacity of the grille with respect to known calenders is increased.
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4132213A DE4132213A1 (en) | 1991-09-27 | 1991-09-27 | FRICTION FORCE COMPENSATION IN THE event of a lack of laundry |
DE4132213 | 1991-09-27 | ||
PCT/EP1992/001937 WO1993006292A1 (en) | 1991-09-27 | 1992-08-24 | Frictional force compensation for laundry mangles |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0605443A1 true EP0605443A1 (en) | 1994-07-13 |
EP0605443B1 EP0605443B1 (en) | 1996-06-05 |
Family
ID=6441627
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP92917609A Expired - Lifetime EP0605443B1 (en) | 1991-09-27 | 1992-08-24 | Frictional force compensation for laundry mangles |
Country Status (7)
Country | Link |
---|---|
US (2) | US5499464A (en) |
EP (1) | EP0605443B1 (en) |
JP (1) | JP3231766B2 (en) |
DE (2) | DE4132213A1 (en) |
DK (1) | DK0605443T3 (en) |
ES (1) | ES2087551T3 (en) |
WO (1) | WO1993006292A1 (en) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5510418A (en) * | 1988-11-21 | 1996-04-23 | Collagen Corporation | Glycosaminoglycan-synthetic polymer conjugates |
DE4132213A1 (en) * | 1991-09-27 | 1993-04-08 | Boewe Passat Reinigung | FRICTION FORCE COMPENSATION IN THE event of a lack of laundry |
DE10152641A1 (en) * | 2001-02-14 | 2002-08-22 | Kannegiesser Aue Gmbh | ironer |
EP1233101B1 (en) | 2001-02-14 | 2007-08-08 | Kannegiesser Aue GmbH | Trough mangle |
JP2007511676A (en) * | 2003-10-22 | 2007-05-10 | ウステル・テヒノロジーズ・アクチエンゲゼルシヤフト | Fixture for quality monitoring device on loom |
DE102005000782A1 (en) | 2005-01-05 | 2006-07-20 | Voith Paper Patent Gmbh | Drying cylinder for use in the production or finishing of fibrous webs, e.g. paper, comprises heating fluid channels between a supporting structure and a thin outer casing |
DE102005000794A1 (en) * | 2005-01-05 | 2006-07-13 | Voith Paper Patent Gmbh | Apparatus and method for producing and / or refining a fibrous web |
DE102005000795A1 (en) * | 2005-01-05 | 2006-07-13 | Voith Paper Patent Gmbh | Apparatus and method for producing and / or refining a fibrous web |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE24331C (en) * | TH. A. EDISON in Menlo-Park, New-Jersey, V. St. A | Innovation in registering voltameters | ||
DE279277C (en) * | ||||
DD24331A (en) * | ||||
GB191202010A (en) * | 1912-01-25 | 1912-11-28 | Henry Crofts Longsdon | Improvements in Machines for Ironing, Smoothing or Glossing Linen and the like. |
NL37527C (en) * | 1934-04-16 | |||
NL64704C (en) * | 1947-10-27 | |||
DE1211122B (en) * | 1963-10-29 | 1966-02-24 | Waescherei Guenther | Flexible ironer tray for a laundry ironer |
DE6605766U (en) * | 1965-07-27 | 1970-08-06 | Miele & Cie | IRONING MACHINE |
DE1813594A1 (en) * | 1968-12-10 | 1970-06-25 | Siemens Elektrogeraete Gmbh | Trough deficiency |
GB2088416B (en) * | 1981-11-03 | 1984-03-21 | Neil & Spencer Ltd | Improvements in or relating to calender ironing machines |
DE3401802A1 (en) * | 1984-01-19 | 1985-07-25 | Kleindienst GmbH, 8900 Augsburg | Hot mangle |
AU3884285A (en) * | 1984-01-19 | 1985-08-09 | Geiger Friedrich | Heibmangel |
DE3507168A1 (en) * | 1985-03-01 | 1986-09-04 | Herbert Kannegiesser Gmbh + Co, 4973 Vlotho | Mangle for smoothing damp laundry articles |
DE3618423A1 (en) * | 1986-02-04 | 1987-08-06 | Effma Waeschereitechnik & Masc | Laundry mangle |
DE3627632A1 (en) * | 1986-08-14 | 1988-02-18 | Transferon Waeschereimasch | Bowl mangle |
DE9004179U1 (en) * | 1990-04-11 | 1990-07-26 | Herbert Kannegiesser Gmbh + Co, 4973 Vlotho | Ironing machine for ironing wet laundry |
DE4132213A1 (en) * | 1991-09-27 | 1993-04-08 | Boewe Passat Reinigung | FRICTION FORCE COMPENSATION IN THE event of a lack of laundry |
-
1991
- 1991-09-27 DE DE4132213A patent/DE4132213A1/en not_active Withdrawn
-
1992
- 1992-08-24 JP JP50572093A patent/JP3231766B2/en not_active Expired - Fee Related
- 1992-08-24 EP EP92917609A patent/EP0605443B1/en not_active Expired - Lifetime
- 1992-08-24 ES ES92917609T patent/ES2087551T3/en not_active Expired - Lifetime
- 1992-08-24 WO PCT/EP1992/001937 patent/WO1993006292A1/en active IP Right Grant
- 1992-08-24 DE DE59206507T patent/DE59206507D1/en not_active Expired - Fee Related
- 1992-08-24 US US08/211,053 patent/US5499464A/en not_active Expired - Fee Related
- 1992-08-24 DK DK92917609.7T patent/DK0605443T3/en active
-
1995
- 1995-12-18 US US08/574,362 patent/US5598649A/en not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO9306292A1 * |
Also Published As
Publication number | Publication date |
---|---|
US5499464A (en) | 1996-03-19 |
DE59206507D1 (en) | 1996-07-11 |
DE4132213A1 (en) | 1993-04-08 |
EP0605443B1 (en) | 1996-06-05 |
US5598649A (en) | 1997-02-04 |
WO1993006292A1 (en) | 1993-04-01 |
JP3231766B2 (en) | 2001-11-26 |
JPH06510923A (en) | 1994-12-08 |
DK0605443T3 (en) | 1996-10-21 |
ES2087551T3 (en) | 1996-07-16 |
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