EP0722899B1 - 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
EP0722899B1
EP0722899B1 EP96100446A EP96100446A EP0722899B1 EP 0722899 B1 EP0722899 B1 EP 0722899B1 EP 96100446 A EP96100446 A EP 96100446A EP 96100446 A EP96100446 A EP 96100446A EP 0722899 B1 EP0722899 B1 EP 0722899B1
Authority
EP
European Patent Office
Prior art keywords
shaft
web
roller
bearing
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.)
Expired - Lifetime
Application number
EP96100446A
Other languages
German (de)
English (en)
Other versions
EP0722899A3 (fr
EP0722899A2 (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 device for compensating clamping forces on the Width of a running web according to that mentioned in the preamble of claim 1 Art.
  • Such a device is known from US Pat. No. 2,066,306 A. It consists of one Roller that is freely rotatable on a shaft. The shaft is at both ends guided in scenes and gripped by a lever linkage. This prevents one movement in the same direction of both shaft ends, so that the shaft and with it the roller is held pivotable only about an axis.
  • this known device has the disadvantage that both in the scenes and in the lever linkage Swiveling the shaft sliding movements take place.
  • the related Frictional forces limit the accuracy of what can be achieved with this device Voltage equalization. In particular, voltage compensation is not possible if the tension difference between both sides of the web is less than the considerable There is hate friction in the scenes and lever arm.
  • the invention has for its object a device of the aforementioned To create a type that ensures precise compensation of tension across the width of the web, without hindering the web.
  • the device according to claim 1 has a pivotally held tension compensation roller on This is freely rotatable on a shaft, the ends of which are in a pivot bearing are supported. This ensures that the space around the Tension compensation roller is free, so that the running of the web is not disturbed in any way is.
  • the pivot bearing of the shaft is supported by the tension compensation roller on both sides provided toothed gear realized. Practice the web on the tension compensation roller torque off, this tries the tension compensation roller on the side of the higher clamping force in the direction of force.
  • the toothed gear sets this movement of the tension compensation roller in one Rotation of the shaft around. This is in turn from the opposite gear in an opposite adjustment movement of the opposite end of the Wave implemented.
  • This mechanism ensures that the tension balancing roller is only pivoted about an axis and not shifted overall can be. This in turn causes that with varying total clamping force the tension compensating roller does not reach any of its end stops. Of the Tension compensation across the width of the web is therefore among all occurring Operating conditions ensured.
  • the application of toothed gears for Swiveling holding the shaft results in particularly low frictional forces since the teeth the toothed gear gripping each other without sliding against each other.
  • the shaft ends are supported in the scenes via roller bearings, which are located on the scenes pass on. In this way, frictional forces emanating from the scenes largely suppressed.
  • the one for pivoting the tension compensation roller The force required is therefore very low, so that the tension compensation of the web even without active adjustment of the tension compensation roller solely by that of the Railway transmitted torque can take place.
  • the desired clamping force compensation is therefore achieved particularly inexpensively with the simplest of means. Also lets the device build very compact, so that existing systems through simple replacement of a roller can be converted without problems.
  • ball or roller bearings have proven themselves as rolling bearings. This have very favorable running properties, especially those for an exact Tension compensation harmful friction force is negligible. That 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 on one level. This prevents pivoting of the Tension compensation roller around a perpendicular to the desired swivel axis Axis that would result in a lateral path. In addition, the counter bearing a correct position of the parts of the toothed gear, so that its teeth always interlock correctly.
  • the rack and pinion one To form gear.
  • the gear meshes directly with the rack, which minimizes the friction losses of the swivel bearing. Since the rack is fixed, the gear must turn on when adjusting the tension compensation roller roll this, whereby the gear is rotated together with the shaft.
  • the racks are on both ends of the shaft at diagonally opposite Provided sides of the shaft axis. This causes the adjustment of the Shaft ends are synchronized in opposite directions to each other.
  • the tension compensation roller can therefore only be pivoted about a fixed, predetermined pivot axis, the gear meshing with the rack through the center of gravity of the tension compensation roller runs.
  • the racks could be the same Side of the shaft axis can be provided. In this case one of the toothed gears would have to have an intermediate gear that reverses the rotational movement of this side. To minimize the frictional forces between the gear and the rack it is convenient to equip them with involute or cycloid teeth.
  • the tension compensation roller can be easily turned by turning the threaded spindle or adjust the screw in its altitude.
  • the actuators it is favorable to connect the actuators to a control device.
  • the control device receives its actual value from force measuring devices which are in the bearings of a roller are provided.
  • the measured force values are over subtracted from each other, the output value of which from the web torque exerted on the tension compensation roller is proportional.
  • This Value is regulated by the control device to the setpoint zero, so that in the steady state State of the control device the tension forces of the web in both Web halves are equal to each other. Because the pivoting of the tension compensation roller actively done through the regulation, play frictional influences, as well the inertia of the tension compensation roller for tension compensation only a subordinate role. They only limit the speed at which one Clamping force difference is corrected.
  • the accuracy of the clamping force compensation is exclusively from the precision of the detection of the web on the tension compensation roller exerted torque and the quality of the controller.
  • the bearing forces of one of the rollers are measured and their difference calculated.
  • the difference in the bearing forces of both ends of a roller is with a central web run, proportional to the torque that the web has on the roller exercises.
  • the roller's bearing forces can be particularly easily and precisely adjusted by in determine the force measuring devices provided in the bearings.
  • the Bearing forces determined on the tension compensation roller This ensures that the The tension of the web is correctly unaffected by the friction of other rollers is detected. It also eliminates time delays between the pivoting of the tension compensation roller and the effect on it Tension of the web is reduced to a minimum.
  • the scheme can therefore Compensate any tension difference of the web faster.
  • Figure 1 shows a device 1 for compensating clamping forces across the width a path 3 running in the direction of arrow 2.
  • This path 3 is on in bearings 12 held rollers 4, 5, 6 deflected, the middle roller 5 as a tension compensation roller is trained.
  • the tension compensation roller 5 is freely rotatable a shaft 7 mounted about a pivot axis extending through its center of gravity S. 8 is pivotally held. Both ends 9 of the shaft 7 are supported in bearings 10, which are held on a frame 11 and together a pivot bearing for the Form wave 7.
  • Figure 2 shows the bearing 10 consisting of a housing block 15, the Cover is removed.
  • a stationary one Threaded spindle 16 This meshes with a gear 17, the teeth 18 only is 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 drive it to move in that direction. Since the gear 17 with the threaded spindle 16 combs, it must roll on this displacement on the threaded spindle 16, so that it is simultaneously rotated in direction 19.
  • the shaft 7 is held in mirror image to the representation according to Figure 2. This causes the described rotation 19 of the gear 17 and thus the shaft 7 at its opposite end 9 is a displacement directed against the force F. causes.
  • the movements of the ends 9 of the shaft 7 are therefore opposite to each other synchronized so that the shaft 7 and thus the voltage compensation roller 5 only is pivotable about the pivot axis 8 indicated in FIG.
  • FIG. 3 shows the bearing 10 according to FIG. 2, the gear wheel 17 with the shaft 7 removed to see the parts underneath.
  • the housing block 15 are defined at a distance e two columns 20, the guide for the shaft 7 form.
  • the shaft 7 carries a roller bearing 21, which alone and only with its Receiving opening 22 is shown.
  • the roller bearing 21 runs between the columns 20, whose distance e from each other is slightly larger than the outer diameter D of Rolling bearing is. This ensures that the roller bearing 21 only on one of the two Columns 20 abuts and rolls on it without sliding.
  • the backdrop guide causes that the shaft 7 can only move within one plane ⁇ .
  • FIG. 10 An alternative embodiment of the bearing 10 is shown in FIG. It exists from 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 by means of Rolling bearing 21 is supported on the columns 20 and rotatably connected to the gear 17.
  • the gear 17 meshes with an intermediate gear 32, the shaft 33 via further roller bearing 34 is also supported on the columns 20.
  • the waves 7, 33 are Supported via roller bearings 35 on a cage 36, the mutual distance M between the shaft axis 23 and the shaft axis 37 keeps constant.
  • the two Rolling bearings 21, 34 allow the cage 36 to move up and down in the direction force F. However, they prevent sideways movement and swiveling of the cage 36.
  • a stop 38 is provided which presses against the shaft 33.
  • the Ball 39 held resiliently.
  • the stop 38 limits the movement of the cage 36 only in one direction, but at the opposite end 9 of the shaft 7 there is another Bearing 10 provided diagonally opposite bearing, the movement of there provided cage 36 limited in the opposite direction. Since both cages 36 with the Shaft 7 are connected, is a movement of the shaft 7 in the direction of its longitudinal axis 23 excluded.
  • a braking device 41 is provided on the carriage 36. It works against them Shaft 7 and prevents its rotation relative to the cage in the tightened position 36. 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 the tension compensation roller 5.
  • the basic structure corresponds to the Device 1 according to Figure 1, wherein the shaft 7 against rotation about its Longitudinal axis 23 is blocked.
  • the threaded spindles 16 of the bearings 10 are with actuators 50 connected. These can, for example, be flanged electric motors Gearboxes or hydraulic motors.
  • the actuators 50 offset the threaded spindles 16 in rotation and thus cause a height adjustment of the ends 9 of the shaft 7.
  • the actuators 50 are in operative connection with displacement sensors 51 which detect the adjustment path of the threaded spindle 16.
  • 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 adjusting differences in tension in both web halves by adjusting to compensate for the tension compensation roller 5.
  • a totalizer 56 is on the input side in operative connection with the force measuring devices 52 and calculates the Difference of 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 Totalizer 56 is fed to a controller 58 via a further totalizer 57, which preferably has a P, PI or PID behavior.
  • the one obtained from controller 58 Correction signal is a non-inverting input 59 and a inverting input 60 supplied by summers 61, 62, which are not shown Power amplifiers are operatively connected to the actuators 50.
  • This control loop is used when there is a difference in bearing force between the ends 9 of the shaft 7 causes an opposite height adjustment of the shaft 7, so this panned. Constantly about the position of the pivot axis 8 of the shaft 7 hold, the average of the adjustment paths from the ends 9 of the tension compensation roller 5 regulated.
  • the displacement sensors 51 are equipped with a further summer 63 connected, whose output signal is the average of the adjustment paths of both Ends 9 of the shaft 7 is proportional.
  • This signal is in a further controller 64 regulated to a constant setpoint.
  • the controller 64 also preferably has a P-, PI or PID behavior.
  • the correction signal obtained from controller 64 arrives non-inverting inputs 65, 66 of the summers 61, 62 and therefore causes one Adjustment of both ends 9 of the shaft 7 in the same direction the middle position of the tension compensation roller 5 and thus the position of its Pivot axis 8 held.
  • the signal f calculated by the circuit block 68 is also multiplied in a multiplier 69 a signal multiplied by the total of the web 3 on the tension compensation roller 5 corresponds to the force exerted.
  • This signal is from a summer 70 won, the input side with the force measuring devices 52 in operative connection stands.
  • the summer 70 is connected via an inverting input 71 connected to a coefficient element 72, by means of which the weight of the tension compensation roller 5 from those measured by the force measuring devices 52 Values is subtracted.
  • the multiplier 69 calculates that difference in force between the two Ends of the shaft 7, which is caused by the off-center web run. This Value is fed to an inverting input 73 of the summer 57, so that on Output 74 of the summer 57 is proportional to the tension difference between the two web halves Signal pending.
  • a window comparator 75 is connected to the output 74 of the summer 57 and compares the control deviation with two fixed limit values. At a digital output 76 of the window comparator 75 is at a zero level when the control deviation is within the range between the limits. The digital output 76 is operatively connected to a hold input 77 of the controller 58, which is in the Inactive in the event of a zero level. This is important so that integrators in controller 58 do not accept undefined output values. Output 76 is also available a braking device of the bearing 10 in operative connection, which is pending at one level the shaft 7 blocked from 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 arithmetic circuits will.
  • implementation using a microcomputer is advantageous because in this case additional functions and changes to the control algorithms can be easily 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)

Claims (10)

  1. Dispositif pour compenser les forces de tension sur la largeur d'une bande (3) tirée sur des cylindres (4, 5, 6), d'une bande de papier ou d'une feuille de préférence, avec un cylindre de compensation de tension (5)renvoyant la bande (3), doté d'une libre possibilité de rotation, et monté sur un arbre (7) gui peut tourner autour de son axe longitudinal (53), l'arbre (7) étant supporté dans un support pivotant (10) maintenu dans un bâti (11), et l'arbre (7) étant maintenu des deux côtés du cylindre de compensation de tension (5) avec un couplage de sens contraire du mouvement de ses deux extrémités et étant guidé dans des coulisses (20), caractérisé en ce que l'arbre (7) est maintenu avec une possibilité de mouvement par des engrenages (16, 17, 32) de part et d'autre du cylindre de compensation de tension (5), et est supporté dans les coulisses (20) par l'intermédiaire de paliers à roulement (21).
  2. Dispositif suivant la revendication 1, caractérisé en ce que le palier à roulement (21) est un palier à billes ou à rouleaux fixé sur l'arbre (7), et qui s'appuie sur un rail ou une colonne (20) en tant que butée.
  3. Dispositif suivant la revendication 1, caractérisé en ce que l'engrenage (16, 17, 32) est formé par une crémaillère (16), qui est en liaison active avec une roue dentée (17) solidaire de l'arbre (7).
  4. Dispositif suivant la revendication 3, caractérisé en ce qu'une roue intermédiaire (32) est prévue comme liaison active entre la crémaillère (16) et la roue dentée (17) de l'arbre (7).
  5. Dispositif suivant la revendication 4, caractérisé en ce que l'axe (37) de la roue intermédiaire (32) est aligné sur la surface d'enveloppe (40) du cylindre de compensation de tension (5).
  6. Dispositif suivant l'une au moins des revendications 3 à 5, caractérisé en ce que la crémaillère (16) est réalisée sous forme de broche filetée ou de vis sans fin.
  7. Dispositif suivant la revendication 6, caractérisé en ce que des servomoteurs (50), mutuellement couplés en sens contraire, attaquent les deux broches filetées (16) ou les vis sans fin, et en ce que l'arbre (7) est bloqué contre un mouvement de rotation autour de son axe longitudinal (23).
  8. Dispositif suivant la revendication 7, caractérisé en ce que les servomoteurs (50) sont en liaison active avec un dispositif de régulation (55), qui est du moins influencé par des dynamomètres (52) prévus sur les paliers (12) de l'un des cylindres (4, 5, 6), du cylindre de compensation de tension (5) de préférence.
  9. Dispositif suivant la revendication 8, caractérisé en ce que le dispositif de régulation (55) est influencé par au moins un capteur de lisière (54), qui détermine la position du bord (53) de la bande.
  10. Dispositif suivant la revendication 8, caractérisé en ce que les dynamomètres (52) sont en liaison active avec un comparateur à fenêtre (75), qui compare le couple exercé par la bande (3) sur le cylindre de compensation de tension (5) à une zone située entre deux valeurs limites, le cylindre de compensation de tension (5) étant maintenu avec une libre possibilité de pivotement pour des couples à l'intérieur de la zone, et étant sinon réglé dans sa position par les servomoteurs (50).
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
DE19501644 1995-01-20
DE19501644A DE19501644C2 (de) 1995-01-20 1995-01-20 Verfahren und Vorrichtung zum Ausgleich von Spannkräften über die Breite einer laufenden Bahn

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 EP0722899A2 (fr) 1996-07-24
EP0722899A3 EP0722899A3 (fr) 1997-07-02
EP0722899B1 true 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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CN108677002B (zh) * 2018-05-16 2019-08-23 山西太钢不锈钢股份有限公司 一种适用于连轧卧式退火炉的炉内张力补偿控制方法
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
CN109230740A (zh) * 2018-08-01 2019-01-18 北京龙马负图科技有限公司 一种手动压力绷带张力调节指示装置
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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
CN116180371B (zh) * 2022-12-21 2023-09-01 连云港鹰游新立成纺织科技有限公司 一种便于展平的纺织布料定型机及其使用方法
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
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CA2167466C (fr) 1999-05-11
US5663510A (en) 1997-09-02
CA2167466A1 (fr) 1996-07-21
EP0888993A1 (fr) 1999-01-07
DE59600976D1 (de) 1999-01-28
EP0722899A3 (fr) 1997-07-02
DE19501644C2 (de) 1998-02-19
DE59604001D1 (de) 2000-01-27
JPH08225206A (ja) 1996-09-03
EP0888993B1 (fr) 1999-12-22
JP2996908B2 (ja) 2000-01-11
EP0722899A2 (fr) 1996-07-24
DE19501644A1 (de) 1996-08-01

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