EP0722899A2 - Procédé et dispositif pour compenser les forces de tension sur la largeur d'une bande en mouvement - Google Patents

Procédé et dispositif pour compenser les forces de tension sur la largeur d'une bande en mouvement Download PDF

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Publication number
EP0722899A2
EP0722899A2 EP96100446A EP96100446A EP0722899A2 EP 0722899 A2 EP0722899 A2 EP 0722899A2 EP 96100446 A EP96100446 A EP 96100446A EP 96100446 A EP96100446 A EP 96100446A EP 0722899 A2 EP0722899 A2 EP 0722899A2
Authority
EP
European Patent Office
Prior art keywords
web
roller
shaft
tension compensation
tension
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
EP96100446A
Other languages
German (de)
English (en)
Other versions
EP0722899A3 (fr
EP0722899B1 (fr
Inventor
Heinrich Niemann
Johannes Wulf
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.)
Erhardt and Leimer GmbH
Original Assignee
Erhardt and Leimer GmbH
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 Erhardt and Leimer GmbH filed Critical Erhardt and Leimer GmbH
Priority to EP98109833A priority Critical patent/EP0888993B1/fr
Publication of EP0722899A2 publication Critical patent/EP0722899A2/fr
Publication of EP0722899A3 publication Critical patent/EP0722899A3/fr
Application granted granted Critical
Publication of EP0722899B1 publication Critical patent/EP0722899B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • B65H23/00—Registering, tensioning, smoothing or guiding webs
    • B65H23/02—Registering, tensioning, smoothing or guiding webs transversely
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2403/00—Power transmission; Driving means
    • B65H2403/50—Driving mechanisms
    • B65H2403/52—Translation screw-thread mechanisms
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2404/00—Parts for transporting or guiding the handled material
    • B65H2404/10—Rollers
    • B65H2404/15—Roller assembly, particular roller arrangement
    • B65H2404/152—Arrangement of roller on a movable frame
    • B65H2404/1521—Arrangement of roller on a movable frame rotating, pivoting or oscillating around an axis, e.g. parallel to the roller axis
    • B65H2404/15212—Arrangement of roller on a movable frame rotating, pivoting or oscillating around an axis, e.g. parallel to the roller axis rotating, pivoting or oscillating around an axis perpendicular to the roller axis
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2511/00—Dimensions; Position; Numbers; Identification; Occurrences
    • B65H2511/20—Location in space
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2511/00—Dimensions; Position; Numbers; Identification; Occurrences
    • B65H2511/20—Location in space
    • B65H2511/21—Angle
    • B65H2511/214—Inclination
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2511/00—Dimensions; Position; Numbers; Identification; Occurrences
    • B65H2511/20—Location in space
    • B65H2511/21—Angle
    • B65H2511/216—Orientation, e.g. with respect to direction of movement
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2515/00—Physical entities not provided for in groups B65H2511/00 or B65H2513/00
    • B65H2515/30—Forces; Stresses
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2515/00—Physical entities not provided for in groups B65H2511/00 or B65H2513/00
    • B65H2515/30—Forces; Stresses
    • B65H2515/32—Torque e.g. braking torque

Definitions

  • the invention relates to a method and a device for compensating tension forces across the width of a running web according to the type mentioned in the preambles of claims 1 and 5.
  • Such a device is known from US Pat. No. 2,066,306. It consists of a roller that is freely rotatable on a shaft. The shaft is guided at both ends in scenes and is gripped by a lever linkage. This prevents the two ends of the shaft from moving in the same direction, so that the shaft and with it the roller can only be pivoted about an axis.
  • this known device has the disadvantage that sliding movements occur both in the scenes and in the lever linkages when the shaft is pivoted.
  • the associated frictional forces limit the accuracy of the voltage compensation that can be achieved by this device.
  • tension compensation is not possible if the difference in tension force between the two web sides is less than the considerable static friction forces in the links and lever linkages.
  • the invention is therefore based on the object of providing a device of the type mentioned at the outset which ensures precise compensation of the tensioning force over the width of the web.
  • a signal proportional to the torque exerted by the web on the tension compensation roller is detected and used as a correction signal for a control.
  • the torque exerted by the web is regulated to the setpoint zero by swiveling the tension compensation roller. This ensures that the tension forces of both web halves are the same in the steady state of the control. Since the swiveling of the tension compensation roller takes place actively through the control, friction influences and the inertia of the tension compensation roller play only a subordinate role for the tension compensation. They only limit the speed at which a clamping force difference is corrected.
  • the accuracy of the tension compensation is determined exclusively by the precision of the detection of the torque exerted by the web on the tension compensation roller and the quality of the controller.
  • the bearing forces of one of the rollers it is advantageous to measure the bearing forces of one of the rollers and to calculate their difference.
  • the difference in the bearing forces of both ends of a roller is proportional to the torque that the web exerts on the roller when the web is running in the center.
  • the bearing forces of the roller can be determined particularly easily and precisely by force measuring devices provided in the bearings.
  • the bearing forces are preferably determined on the tension compensation roller. This ensures that the tensioning force of the web is correctly detected without being influenced by the friction of other rolls.
  • the position of the tension compensation roller is either regulated and thus actively adjusted or kept freely pivotable.
  • a freely pivotable holding has the particular advantage that the tension compensation between the two web halves takes place particularly precisely and independently of the accuracy of the force measurement.
  • the position of the tension compensation roller is only regulated and thus actively adjusted if there are large deviations between the setpoint and actual value. This ensures that a large difference in tension force between the two web halves is corrected very quickly, since the actuators for pivoting the tension compensation roller can exert considerably more force than the web itself. This is particularly important with large rollers which have a correspondingly large moment of inertia . In this case, the pivot bearing of the tension compensation roller is blocked in order to ensure effective power transmission through the control to the tension compensation roller.
  • the device according to claim 5 has a pivotally held tension compensation roller.
  • This is freely rotatable on a shaft, the ends of which are supported in a swivel bearing. This ensures that the space around the tension balancing roller is free so that the running of the web is in no way disturbed is.
  • the swivel bearing of the shaft is realized by toothed gears provided on both sides of the tension compensation roller. If the web exerts a torque on the tension compensation roller, this tries to push the tension compensation roller on the side of the higher tensioning force away in the direction of the force.
  • the toothed gear converts this movement of the tension compensation roller into a rotary movement of the shaft. This is in turn converted by the opposing toothed gear into an opposing adjustment movement of the opposite end of the shaft.
  • This mechanism ensures that the tension compensation roller is only pivoted about an axis and cannot be moved as a whole. This in turn causes the tension compensating roller not to reach any of its end stops when the total tension force of the web varies. The tension compensation across the width of the web is therefore ensured under all operating conditions.
  • the use of toothed gears for pivotably holding the shaft results in particularly low frictional forces, since the teeth of the toothed gears roll against one another without sliding against one another.
  • the shaft ends are supported in the scenes via roller bearings that roll on the scenes. In this way, frictional forces emanating from the scenes are largely suppressed.
  • the force required to pivot the tension compensating roller is therefore very low, so that the tension compensation of the web can also take place without the active adjustment of the tension compensation roller solely by the torque transmitted by the web.
  • the desired clamping force compensation is therefore achieved in a particularly cost-effective manner using the simplest of means.
  • the device can be constructed very compactly, so that even existing systems can be converted without problems by simply changing a roller.
  • ball or roller bearings have proven themselves as rolling bearings. These have very favorable running properties, in particular the frictional force, which is damaging for an exact tension compensation, is negligible.
  • the ball or roller bearing is only on one side of a rail or column as a counter bearing and rolls on it. This counter bearing limits the freedom of movement of the tension compensation roller to one level. This prevents pivoting of the Tension compensation roller around an axis perpendicular to the desired swivel axis, which would result in a lateral path.
  • the counter bearing ensures the correct position of the parts of the toothed gear so that its teeth always interlock correctly.
  • the toothed gear from a rack and a gear.
  • the gear meshes directly with the rack, which minimizes the friction losses of the pivot bearing.
  • the toothed rack is fixed, the toothed wheel must roll on the tension compensating roller when it is adjusted, the toothed wheel being rotated together with the shaft.
  • the racks are preferably provided on both ends of the shaft on diagonally opposite sides of the shaft axis. This means that the adjustment of the shaft ends is synchronized in opposite directions to each other.
  • the tension compensation roller can therefore only be pivoted about a fixed, predetermined pivot axis, which runs through the center of gravity of the tension compensation roller when the gear meshing with the rack.
  • the racks could also be provided on the same side of the shaft axis.
  • one of the toothed gears should have an intermediate gear which reverses the rotational movement of this side. In order to minimize the frictional forces between the gearwheel and the toothed rack, it is favorable to equip them with involute or cycloid teeth.
  • the center line of the web does not undergo any change in length due to the tension compensation roller.
  • This is achieved according to claim 9 in that the pivot axis of the tension compensation roller is shifted to its jacket. The pivot axis affects the Tension compensation roller in the area in which it is wrapped in the web, so side and longitudinal registers remain unaffected.
  • the tension compensating roller can be adjusted very simply by rotating the threaded spindle or worm in its height.
  • the pivoting of the tension compensation roller can be carried out actively by the actuators.
  • the shaft In order to prevent the tension compensation roller from pivoting freely under the pressure of the web, the shaft is blocked against rotation about its longitudinal axis.
  • the pivoting of the tension compensation roller by means of actuators offers the advantage that its inertia can be overcome more easily than if the web itself had to exert the actuating force.
  • control device receives its actual value from force measuring devices which are provided in the bearings of a roller.
  • the measured force values are subtracted from each other via a subtractor, the output value of which is proportional to the torque exerted by the web on the tension compensation roller.
  • This value is regulated by the control device to the nominal value of zero, so that the tensioning forces of the web in both web halves are equal to one another in the steady state of the control device.
  • FIG. 1 shows a device 1 for compensating tension forces across the width of a web 3 running in the direction of arrow 2.
  • This web 3 is deflected on rollers 4, 5, 6 held in bearings 12, the central roller 5 being designed as a tension compensation roller is.
  • the tension compensation roller 5 is freely rotatably mounted on a shaft 7 which is held pivotably about a pivot axis 8 running through its center of gravity S. Both ends 9 of the shaft 7 are supported in bearings 10 which are held on a frame 11 and together form a pivot bearing for the shaft 7.
  • FIGS. 2 and 3 show the bearing 10 consisting of a housing block 15, the cover is removed.
  • a stationary threaded spindle 16 This meshes with a gear 17, the toothing 18 of which is only indicated.
  • the gear 17 is connected to the shaft 7 in a rotationally fixed manner.
  • the web 3 presses the shaft 7 with a force F and tries to move it in this direction. Since the gear 17 meshes with the threaded spindle 16, it must roll on the threaded spindle 16 during this displacement, so that it is simultaneously rotated in the direction 19.
  • the shaft 7 is held in mirror image for the illustration according to FIG. This has the effect that the described rotation 19 of the gear 17 and thus the shaft 7 at its opposite end 9 causes a displacement directed against the force F.
  • the movements of the ends 9 of the shaft 7 are therefore synchronized in opposite directions to one another, so that the shaft 7 and thus the tension compensation roller 5 can only be pivoted about the pivot axis 8 indicated in FIG.
  • FIG. 3 shows the bearing 10 according to FIG. 2, the gearwheel 17 with the shaft 7 being removed in order to be able to see the parts underneath.
  • the shaft 7 carries a roller bearing 21, which is shown alone and only with its receiving opening 22.
  • the roller bearing 21 runs between the columns 20, the spacing e of which is slightly larger than the outer diameter D of the roller bearing. It is thereby achieved that the roller bearing 21 rests only on one of the two columns 20 and rolls on it without sliding.
  • the backdrop guide means that the shaft 7 can only move within one plane ⁇ .
  • through holes 24 are provided in the plane of movement of the rolling bearing, in which stops, not shown, are provided to limit the travel of the shaft 7 on both sides.
  • a shock absorber could be provided in one of the through bores 24, which dampens vibratory movements of the shaft 7.
  • FIG. 10 An alternative embodiment of the bearing 10 is shown in FIG. It consists of the housing block 15, on which a cover 30 is fixed.
  • the cover 30 has an opening 31 penetrated by the shaft 7.
  • the shaft 7 is supported on the pillars 20 by means of the roller bearing 21 and is connected to the gear 17 in a rotationally fixed manner.
  • the gear 17 meshes with an intermediate gear 32, the shaft 33 of which is also supported on the columns 20 via a further roller bearing 34.
  • the shafts 7, 33 are supported by roller bearings 35 on a cage 36 which keeps the mutual distance M between the shaft axis 23 and the shaft axis 37 constant.
  • the two roller bearings 21, 34 allow the cage 36 to move up and down in the direction of the force F. However, they prevent the cage 36 from moving sideways and pivoting.
  • an intermediate gear 32 is provided in mesh with the threaded spindle 16 and the gear 17, the axis 37 of which is aligned with the jacket 40 .
  • the gears 17, 32 are dimensioned accordingly in their diameter.
  • the threaded spindle 16 penetrates the housing block 15 at its lower end.
  • the threaded spindle 16 can be connected to an actuator, for example an electric motor or a hydraulic motor, which turning them.
  • This rotation of the threaded spindle 16 is transmitted to the shaft 7 via the gear wheels 32 and 17.
  • the bearing 10 located at the opposite end 9 of the shaft 7 then also has an actuator. Both actuators are coupled in opposite directions, so that a bearing 10 causes an upward movement of the shaft end 9 and the opposite bearing 10 causes a downward movement of the shaft end 9.
  • a braking device 41 is provided on the slide 36. It acts against the shaft 7 and prevents it from rotating relative to the cage 36 in the tightened position. In the released position, the braking device 41 is spaced from the shaft 7, so that the tension compensation roller 5 can pivot freely.
  • FIG. 5 shows an alternative embodiment of the device 1 with active adjustment of the tension compensation roller 5.
  • the basic structure corresponds to the device 1 according to FIG. 1, the shaft 7 being blocked against rotation about its longitudinal axis 23.
  • the threaded spindles 16 of the bearings 10 are connected to actuators 50. These can be, for example, electric motors with flanged gears or hydraulic motors.
  • the actuators 50 set the threaded spindles 16 in rotation and in this way cause the ends 9 of the shaft 7 to be adjusted in height.
  • the actuators 50 are operatively connected to displacement sensors 51 which detect the adjustment path of the threaded spindle 16.
  • the signal obtained from the displacement sensor 51 is also proportional to the displacement of the end 9 of the shaft 7.
  • Force measuring devices 52 are provided between the bearings 10 and the frame 11, which from the tension compensating roller 5 and the web 3 exert bearing forces F.
  • Edge sensors 54 are provided on both web edges 53 for continuous detection of the web position.
  • the actuators 50, the displacement sensors 51, the edge measuring devices 52 and the edge sensors 54 are operatively connected to a control device 55.
  • This control device 55 has the task of compensating for differences in tension force in both web halves by adjusting the tension compensation roller 5.
  • a totalizer 56 is operatively connected on the input side to the force measuring devices 52 and calculates the difference in the measured bearing forces, which is proportional to that of the web 3 on the Tension compensation roller 5 is exerted torque.
  • the output signal of the summer 56 is fed via a further summer 57 to a controller 58, which preferably has a P, PI or PID behavior.
  • the correction signal obtained by the controller 58 is fed to a non-inverting input 59 and an inverting input 60 from summers 61, 62 which are operatively connected to the actuators 50 via power amplifiers (not shown).
  • this control loop causes the shaft 7 to be adjusted in the opposite direction, that is to say it is pivoted.
  • the mean value of the adjustment paths from the ends 9 of the tension compensation roller 5 is also regulated.
  • the displacement sensors 51 are connected to a further summer 63, the output signal of which is proportional to the average of the adjustment paths of both ends 9 of the shaft 7.
  • This signal is regulated in a further controller 64 to a constant setpoint.
  • the controller 64 also preferably has a P, PI or PID behavior.
  • the correction signal obtained from the controller 64 reaches non-inverting inputs 65, 66 of the summers 61, 62 and therefore causes both ends 9 of the shaft 7 to be adjusted in the same direction.
  • This control loop determines the central position of the voltage compensation roller 5 and thus the position of its pivot axis 8 recorded.
  • the signal f calculated by the circuit block 68 is multiplied in a multiplier 69 by a signal which corresponds to the total force exerted by the web 3 on the tension compensation roller 5.
  • This signal is obtained from a summer 70 which is operatively connected to the force measuring devices 52 on the input side. Via an inverting input 71, the summer 70 is connected to a coefficient element 72, with the aid of which the weight of the tension compensation roller 5 is subtracted from the values measured by the force measuring devices 52.
  • the multiplier 69 calculates that difference in force at both ends of the shaft 7 which is caused by the off-center web travel. This value is fed to an inverting input 73 of the summer 57, so that a signal proportional to the tension force difference between the two web halves is present at the output 74 of the summer 57.
  • a window comparator 75 is connected to the output 74 of the summer 57 and compares the control deviation with two fixed limit values. A zero level is present at a digital output 76 of the window comparator 75 if the control deviation is within the range between the limit values.
  • the digital output 76 is operatively connected to a hold input 77 of the controller 58, which becomes inactive in the event of a zero level. This is important so that integrators in controller 58 do not assume undefined output values.
  • the output 76 is operatively connected to a braking device of the bearing 10, which, when a level is present, blocks the shaft 7 against rotation about its longitudinal axis, so that the actuators 50 can adjust the tension compensation roller 5.
  • the control device 55 can be implemented by analog or digital computing circuits.
  • implementation using a microcomputer is advantageous, since in this case additional functions and changes in the control algorithms can easily be taken into account by adapting the program.

Landscapes

  • Controlling Rewinding, Feeding, Winding, Or Abnormalities Of Webs (AREA)
  • Registering, Tensioning, Guiding Webs, And Rollers Therefor (AREA)
EP96100446A 1995-01-20 1996-01-13 Procédé et dispositif pour compenser les forces de tension sur la largeur d'une bande en mouvement Expired - Lifetime EP0722899B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP98109833A EP0888993B1 (fr) 1995-01-20 1996-01-13 Procédé et dispositif pour compenser les forces de tension sur la largeur d'une bande en mouvement

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19501644A DE19501644C2 (de) 1995-01-20 1995-01-20 Verfahren und Vorrichtung zum Ausgleich von Spannkräften über die Breite einer laufenden Bahn
DE19501644 1995-01-20

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP98109833A Division EP0888993B1 (fr) 1995-01-20 1996-01-13 Procédé et dispositif pour compenser les forces de tension sur la largeur d'une bande en mouvement

Publications (3)

Publication Number Publication Date
EP0722899A2 true EP0722899A2 (fr) 1996-07-24
EP0722899A3 EP0722899A3 (fr) 1997-07-02
EP0722899B1 EP0722899B1 (fr) 1998-12-16

Family

ID=7751922

Family Applications (2)

Application Number Title Priority Date Filing Date
EP96100446A Expired - Lifetime EP0722899B1 (fr) 1995-01-20 1996-01-13 Procédé et dispositif pour compenser les forces de tension sur la largeur d'une bande en mouvement
EP98109833A Expired - Lifetime EP0888993B1 (fr) 1995-01-20 1996-01-13 Procédé et dispositif pour compenser les forces de tension sur la largeur d'une bande en mouvement

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP98109833A Expired - Lifetime EP0888993B1 (fr) 1995-01-20 1996-01-13 Procédé et dispositif pour compenser les forces de tension sur la largeur d'une bande en mouvement

Country Status (5)

Country Link
US (1) US5663510A (fr)
EP (2) EP0722899B1 (fr)
JP (1) JP2996908B2 (fr)
CA (1) CA2167466C (fr)
DE (3) DE19501644C2 (fr)

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CN108772424B (zh) * 2018-07-17 2024-07-23 桂林电子科技大学 成品铝箔板形离线动态检测自动控制系统及其使用方法
US20220002107A1 (en) * 2020-07-01 2022-01-06 CSG Holding, Inc. Webtension transducer load cell with integrated data interface
CN112938593A (zh) * 2021-02-01 2021-06-11 安徽理工大学 一种耐磨性强的吸汗布料的加工工艺及其加工装置
IT202200009695A1 (it) 2022-05-11 2023-11-11 Fosber Spa Un dispositivo per regolare ed equalizzare la tensione in un materiale nastriforme, e un ondulatore comprendente detto dispositivo
CN117104969A (zh) * 2023-09-15 2023-11-24 德州鑫泽复合材料有限公司 一种复合材料予浸机原料分离装置及分离方法
CN117088048B (zh) * 2023-10-07 2024-03-08 上海赛摩物流科技有限公司 一种用于输送线的链条智能自动张紧机构
CN117388461B (zh) * 2023-12-07 2024-03-12 北京一控系统技术有限公司 箔材离线板形检测装置及检测方法
CN118723652B (zh) * 2024-09-03 2024-12-06 浙江洲一铝业有限公司 一种铝箔收卷用卷绕纠偏装置
CN119218804B (zh) * 2024-12-03 2025-03-04 安徽如领新材料科技有限公司 一种电子玻璃柔性间隔膜收卷设备
CN121157266B (zh) * 2025-11-05 2026-04-17 江苏海时益新材料科技有限公司 一种缠绕膜压延生产设备

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DE59600976D1 (de) 1999-01-28
CA2167466C (fr) 1999-05-11
EP0722899A3 (fr) 1997-07-02
US5663510A (en) 1997-09-02
EP0722899B1 (fr) 1998-12-16
EP0888993A1 (fr) 1999-01-07
EP0888993B1 (fr) 1999-12-22
JPH08225206A (ja) 1996-09-03
DE59604001D1 (de) 2000-01-27
JP2996908B2 (ja) 2000-01-11
DE19501644A1 (de) 1996-08-01
CA2167466A1 (fr) 1996-07-21
DE19501644C2 (de) 1998-02-19

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