US3912145A - Web tension control system - Google Patents

Web tension control system Download PDF

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Publication number
US3912145A
US3912145A US447695A US44769574A US3912145A US 3912145 A US3912145 A US 3912145A US 447695 A US447695 A US 447695A US 44769574 A US44769574 A US 44769574A US 3912145 A US3912145 A US 3912145A
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United States
Prior art keywords
web
tension
dancer
assembly
roll
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Expired - Lifetime
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US447695A
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English (en)
Inventor
Edward F Meihofer
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Butler Automatic Inc
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Butler Automatic Inc
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Application filed by Butler Automatic Inc filed Critical Butler Automatic Inc
Priority to US447695A priority Critical patent/US3912145A/en
Priority to IT67536/75A priority patent/IT1030255B/it
Priority to FR7506534A priority patent/FR2263187B1/fr
Priority to JP2586475A priority patent/JPS5327436B2/ja
Priority to DE19752509382 priority patent/DE2509382A1/de
Priority to GB8968/75A priority patent/GB1501292A/en
Application granted granted Critical
Publication of US3912145A publication Critical patent/US3912145A/en
Assigned to BUTLER AUTOMATIC INC. reassignment BUTLER AUTOMATIC INC. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: BUTLER GREENWICH INC.
Assigned to SHAWMUT BANK, N.A., reassignment SHAWMUT BANK, N.A., SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BUTLER AUTOMATIC INC.
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    • 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
    • B65H23/04—Registering, tensioning, smoothing or guiding webs longitudinally
    • B65H23/18—Registering, tensioning, smoothing or guiding webs longitudinally by controlling or regulating the web-advancing mechanism, e.g. mechanism acting on the running web
    • B65H23/188—Registering, tensioning, smoothing or guiding webs longitudinally by controlling or regulating the web-advancing mechanism, e.g. mechanism acting on the running web in connection with running-web
    • B65H23/1888—Registering, tensioning, smoothing or guiding webs longitudinally by controlling or regulating the web-advancing mechanism, e.g. mechanism acting on the running web in connection with running-web and controlling web tension

Definitions

  • a balanced, undamped, low inertia, preloaded dancer assembly contacts the web and web tension upsets are reflected in movements of the dancer assembly. Such movements are detected by a transducer and applied to an electronic controller which provides a continuous, proportional output signal to either the overspeed or underspeed clutch.
  • the clutch applies a drive torque or holdback torque component to the draw roll which changes the web tension as needed to reposition the dancer assembly to its reference position.
  • Web tension may vary because of variations in the modulus of elasticity of the web along its length, changes in web thickness, speed of the web-consuming machine and for other reasons.
  • a number of systems have been devised to provide this tension control and they often include a floating dancer assembly in contact with the moving web which changes position in response to web tension changes. Dancer position is then used to control the speed of a driven roll in contact with the web.
  • the dancer is normally preloaded so that, in operation, it tends to assume a selected reference position which is indicative of the desired web tension.
  • any increase in tension causes the dancer to move in one direction from its reference position. This movement initiates an increase in the speed of the driven roll which tends to decrease the tension in the web so that the dancer returns to its reference position.
  • a decrease in web tension causes the dancer to move in the opposite direction from its reference position, producing a decrease in the speed of the driven roll so that web tension increases sufficiently to return the dancer to its reference position.
  • any web tension upsets are reflected in movements of the dancer which, in turn, control the speed of the driven roll to compensate for the tension upsets.
  • the outfeed device operates in a comparable way to maintain uniform tension in web exiting such processing apparatus.
  • the speed of the draw roll is changed by over and underspeed clutches operating off the main line shaft.
  • the clutches are controlled by limit switches which sense extreme positions of the dancer.
  • the dancer moves up until it trips one switch which then actuates the overspeed clutch, resulting in an increase in the speed of the draw roll which lessens web tension so that the dancer moves down until it trips the other limit switch.
  • This actuates the underspeed clutch, resulting in a decrease in speed of the draw roll and an increase in web tension, causing the dancer to travel upwards again, and so on.
  • the present invention aims to provide a web tension control system which maintains accurate control over the tension in a moving web over a wide range of web speeds, e.g. from 50 fpm to 2,500 fpm and higher.
  • a further object of the invention is to provide a web tension control system which is relatively inexpensive to make, maintain and operate.
  • Another object is to provide a web tension control system which corrects for even small tension upsets.
  • a further object of the invention is to provide a system of this general type which maintains uniform web tension over a wide range of tensions.
  • a further object is-to provide a web tension control system which can compensate for downstream changes in web tension and speed.
  • Yet another object of the invention is to provide a system of this type which is easily constructed from standard electromechanical components.
  • a further object of the invention is to provide a web tension control system which is quite stable in operation even at high web speeds.
  • Yet another object is to provide a system of this type which is relatively efficient as compared with those requiring separate control motors because energy is coupled back into the mechanical drive system rather than being dissipated.
  • a balanced, low inertia, undamped, floating roll dancer assembly is positioned in the web path between the driven roll and guide roll.
  • the dancer assembly is comprised of a pair of parallel rolls which engage the web on opposite sides thereof and which are spaced from each other in the direction of web travel.
  • the rolls are rotatively mounted in a frame which, in turn, pivots on low friction bearings about an axis which is parallel to the axes of rotation of the rolls.
  • the dancer assembly is suitably preloaded so that it assumes a position of maximum web storage. During operation of the system, when the web is under tension, the dancer assembly tends to assume a reference position midway between its maximum and minimum storage positions.
  • the dancer assembly Since the dancer assembly is balanced, no preloading is required to compensate for the weight of the dancer assembly. This is important when it is necessary to process web under low tension because ten pounds of loading pressure just to raise the dancer may represent as much as fifty pounds of web tension. Also, the assemblys small mass and low friction mounting means that the dancer has relatively low mechanical inertia. Thus, it can change position very quickly in response to a web tension change to develop the proper corrective signal for the controller.
  • the dancer assembly is specially designed so that its movements do not affect the relationship between the torques applied to the assembly by the tensioned web and the loading device.
  • the controller develops electrical signals corresponding to both dancer position and dancer velocity. These signals are summed and the resultant signal is applied to a lag circuit which compensates for the small amount of mechanical inertia in the system.
  • the output of the lag circuit is applied to continuously control the overspeed and underspeed clutches modulating between them, depending upon whether drive torque or holdback torque must be applied to the draw roll in order to restore the proper web tension that will cause the assembly to return to, and remain in, its reference position.
  • the dancer assembly pivots so as to shorten the web path between the driven roll and the guide roll.
  • This dancer movement produces a corresponding electrical signal which causes the controller to increase the torque coupling in the overspeed clutch, thereby increasing the driving torque on the driven roll.
  • the tension in the web beyond the driven roll is thus decreased, as is the torque component on the dancer assembly due to web tension, sufficiently to return the dancer assembly to its reference position.
  • the dancer assembly pivots so as to lengthen the path of the web between the driven roll and the guide roll.
  • This dancer movement causes the controller to increase the torque coupling in the underspeed clutch so that the necessary holdback torque is applied to the driven roll to increase web tension just enough to return the dancer assembly to its reference position.
  • the present system senses the tension in the web and responds to a change therein by continuously modulating the torque on the driven roll, rather than its speed, to effect tension correction.
  • This torque control is maintained over a predetermined range of web speeds in the vicinity of the speed of the line shaft, e.g. i 4%.
  • the system can tolerate web slippage, web elongation, and even downstream web speed changes over this preselected speed range. Any energy savings during torque modulation is coupled back into the machine line shaft so that the rating of the drive motor can be kept to a minimum.
  • the controller responds to both dancer position and rate so that it exercises very fast and continuous control over the torque applied to the driven roll. Any change in that torque is reflected almost immediately (i.e. five Hz or less) in a corrective change in web tension that will tend to return the dancer to its reference position.
  • the subject dancer assembly in conjunction with the electronic controller and over and underspeed drives constitutes a true integrating type of system.
  • even a small change in dancer position due to a small tension upset results in a corrective torque component being applied to the driven roll.
  • the system responds quickly and is quite stable and exercises control only over the relatively short preselected web speed range, the excursions of the dancer assembly about its reference position are very short (e.g. 1/16 inch) and web storage provided by only the two offset dancer rolls is quite adequate even at high web speeds.
  • the present arrangement provides continuously variable torque control over the draw roll up to the full rating of the clutches to maintain a constant trim on web tension from a web-up speed as low as 50 fpm to normal operating speeds as high as 2500 fpm.
  • the tension can be maintained to an accuracy of as high as 1% and even lower over the entire web speed range.
  • FIG. 1 is a diagrammatic view of the web tension con trol system embodying the principles If this invention.
  • FIG. 2 is a schematic diagram showing in greater detail certain elements of the FIG. 1 system.
  • FIG. 1 of the drawings since this is a balanced system, the web can travel in either direction through the system.
  • the web W is traveling from left to right.
  • Web is trained around a driven draw roll and thence passed through a dancer assembly indicated generally at 12. From there, it is trained under a guide roll 14 and drawn into the web-consuming machine (not shown).
  • the dancer assembly 12 moves from its reference position to lengthen or shorten the web path as necessary to maintain uniform tension in the web.
  • the dancer motion is detected by a control section shown generally at 16 which responds by applying a drive torque or a holdback torque to the draw roll 10. That, in turn, decreases or increases the tension in the web W entering the dancer assembly as needed to return the dancer assembly to its reference position.
  • the draw roll 10 has a shaft 10a which is coupled to the control section 16. Web slippage relative to roll 10 is minimized by means of a nip roll 18 which is supported via its shaft 18a at the ends of a pair of elongated end plates 22. The opposite ends of plates 22 are connected by pivots 24 to the machine frame (not shown). Nip roll 18 is pressure loaded against roll 10 by suitable means illustrated herein as pressure cylinders 26 acting between end plates 26 and the machine frame.
  • the dancer assembly 12 is comprised of a pair of parallel rolls 32 and 34 which are spaced apart in the direction of web travel and engage web W on opposite sides thereof.
  • the opposite ends of rolls 32 and 34 are journaled in a pair of end plates 36a and 36b.
  • a pair of stub shafts 38a and 38b project laterally from the centers of plates 36a and 36b, respectively, and these shafts are journaled in a pair of bearing assemblies 42a a 42b, respectively.
  • the components of the dancer assembly 12 are arranged with respect to the draw roll 10 and guide roll 14 so that it is a completely balanced system.
  • the stretch of web between draw roll 10 and roll 32 is parallel to the stretch of web between roll 34 and guide roll 14. Both of these are perpendicular to the plane defined by the dancer rolls when the assembly is in its reference (e.g. horizontal) position.
  • the dancer assembly pivots on its bearing assemblies 42a, 42b in one direction or the other from its reference position, it either lengthens or shortens the path of the web W between rolls 10 and 14. Since the dancer is balanced, no loading is required to compensate for the weight of the dancer and, therefore, the system can operate at very low web tensions.
  • the dancer assembly is biased toward its web storage position by suitable means illustrated herein as a loading cylinder 44.
  • the end of cylinder 44 is provided with an ear 46 which is connected by a pivot 48 to an car 52 attached to the machine frame.
  • the loading cyclinder shaft 44a is pivotally connected at 49 to one of the dancer assembly end plates, i.e. plate 36a.
  • the pivotal connection 49 between shaft 44a and the end frame is situated outboard of shaft 38a so that the cylinder can impart an appreciable torque to the dancer assembly.
  • Fluid under pressure is fed to cylinder 44 by way of a pressure regulator 50 and the cylinder pressure is adjusted so that the torque exerted by the cylinder on the dancer assembly just offsets the opposing torque due to the desired tension in web W so that the dancer assembly tends to assume a reference position as seen in FIG. 1.
  • a duplicate loading cylinder can be stalled at the opposite side of the assembly, i.e. at plate 361), to minimize racking of the assembly.
  • the loading cylinder 44 could just as well be arranged to push down on plate 36a (and/or 36b) on the other side of bearing assembly 42a, (42b).
  • the present dancer assembly is specially designed so that no changes in web tension arise because of changes in the relationship between the torques on the assembly due to web tension and cylinder 44 at different angular positions of the assembly. More particularly, one of the shortcomings of many prior dancer roll systems stems from the fact that as the dancer assembly moves from its reference position, the forces on the dancer due to web tension and dancer loading vary as a function of the angle to which the dancer assembly pivots due to a tension upset. Consequently, in those prior systems, the dancer assembly itself introduces unwanted tension changes in the web which adversely affect the stability of the overall system.
  • any rotation of the dancer assembly on shafts 38a and 38b is sensed by a suitable detector illustrated herein as a potentiometer 56 which is connected electrically to the control section 16. More specifically, the potentiometer 56 applies a signal to an electronic controller 58 in section 16 which corresponds to the deviation of the dancer assembly from its illustrated reference position.
  • the controller 58 provides an output to a variable slip overspeed clutch 62 or a variable slip underspeed clutch 64 coupled to draw roll 10, depending upon whether drive torque or holdback torque should be applied to the roll to correct web tension.
  • the clutches 62 and 64 are driven by the machine line shaft 66.
  • a toothed pulley 68 rotating with the line shaft 66 is connected by a timing chain 72 to a toothed pulley 74 affixed to the input shaft 62a of clutch 62 and also to a toothed pulley 76 connected to the input shaft 64a of clutch 64.
  • the pulley 74 has fewer teeth than pulley 68 and pulley 76 has correspondingly more teeth than pulley 68 to obtain the desired speed differential between the two clutches over the desired speed range of, say i4% of the line shaft speed.
  • the two clutches also have output shafts 62b and 64b which carry toothed pulleys 78 and 82, respectively, which are connected by a timing chain 84 to a toothed pulley 88 on the end of the draw roll shaft 10a.
  • the clutches are set to magnetically couple a selected torque to the draw roll 10 as needed to maintain the dancer assembly in its reference position.
  • the torque coupling changes required to compensate for web tension variations are made by controlling the current in the clutch coils.
  • a variable slip magnetic particle clutch suited for this purpose is manufactured by W. J. Industries Inc. and the Vickers Division of Sperry Rand Corp. although other comparable electric, pneumatic or friction clutches can also be used, as long as they permit continuously varying control over the torque applied to the draw roll.
  • the dancer assembly 12 and control section 16 together function as an error position integrator so that the infeed responds to even very small tension changes.
  • the control section 16 includes feedback between the clutches and the controller and within the controller itself to keep instabilities within the system to a minimum.
  • the infeed maintains very close control over web tension i.e. within 1% of the desired tension.
  • the excursions of the dancer assembly 12 from its reference position are very small, i.e. on the order of 1/16 inch during normal operation and only 1 to 2 inches during an emergency stop situation. Since the dancer and overall system have very fast response and only controls web speed within 14% of line speed, the dancer assembly does not require much storage capacity even at web speeds in excess of 2500 fpm.
  • the controller 58 contributes substantially to the basic stability of the overall system. It includes a regulated, dual polarity power supply 82 connected to the potentiometer 56. The output of the potentiometer, taken from the wiper 56a thereof, is applied to a dc amplifier 84 and to a differentiator 86.
  • the output of the amplifier is a signal corresponding to the position of the dancer, while the output of the differentiator is proportional to the dancer velocity.
  • These two signals are summed and applied to a lag circuit 88 illustratively consisting of a high gain amplifier 89 and an RC circuit 92 connected between the amplifier 89 input and output.
  • the lag circuit is basically an integrator and provides a negative phase shift to compensate for the mechanical inertia that remains in the infeed system.
  • the circuit 88 output is applied directly to a diode 94 and by way of an inverter 96 to a diode 98, both diodes being arranged to pass only positive going signals.
  • a positive going signal is applied either to diode 94 or diode 98, depending upon the direction of dancer movement. For purposes of discussion, we will assume that an increase in web tension which causes the dancer assembly 12 to rotate clockwise in FIG. 1 produces a positive going signal at diode 94.
  • the output of diode 94 is applied by way of a voltage regulator 102 to an overspeed firing circuit 104.
  • the output of circuit 104 is used to trigger a pair of SCRs 106 and 108 connected to pass current during alternate half cycles from a center tapped transformer 110 to a series circuit consisting of the coil 62c of overspeed clutch 62 and a resistor 112.
  • the output of the regulator 102 determines the firing angle of the SCRs and therefore controls the current in the clutch coil.
  • a diode 111 is connected across coil 62c to accomodate back EMF due to a collapsing field in coil 62c.
  • similar circuitry follows the diode 98 to control the underspeed clutch 64.
  • the diode 98 output is applied via a voltage regulator 114 to an underspeed firing circuit 116 whose output is used to trigger a pair of SCRs 118 and 122.
  • These SCRs are arranged to conduct current from a transformer 124 during alternate half cycles to a series circuit consisting of the underspeed clutch coil 64c and a resistor 126, with a diode 127 in parallel with the coil.
  • the output of the lag circuit also controls the firing angle of these SCRs and thus the current through coil 640.
  • a voltage proportional to the current through the coil 64c appears at the junction of that coil and the resistor 126 and is fed back to the input of regulator 114 where it is summed with the signal from diode 98.
  • the signal applied to the firing circuit 116 controls the current through the underspeed clutch coil 640 so that it is always proportional to the output of the lag circuit 88. Resultantly, very close control is maintained over the torque coupling between the underspeed clutch 64 and the draw roll 10 in response to counterclockwise dancer movement indicative of a web tension decrease.
  • the present system controls web tension by sensing web tension changes using a balanced, specially loaded, undamped dancer having low mechanical inertia and thus fast response to tension upsets.
  • the dancer motion is sensed and a signal is applied to a controller which continuously develops proportional control signals for the continuously controllable overspeed and underspeed clutches.
  • these clutches are modulated so as to apply just the proper torque component to the draw roll to maintain the dancer in its reference position.
  • the clutches are set to always drive the draw roll at speeds slightly less than or slightly more than line shaft speed, the excursions of the dancer are quite small, e.g. 1/16 inch, and system operation is quite stablefAlso, there is no dancer loading cylinder pulsing problem.
  • web tension can be controlled with great accuracy over the full range of web speeds of from 50 fpm to 2500 fpm.
  • the clutches are set to run 4% underspeed and 4% overspeed and this amount may vary in different applications. As a general rule, however, it has been found that if the speed difference is much less than i2% of line shaft speed, tension upsets take a fairly long time to correct. Also, if the difference is much more than 10% of shaft speed, there is relatively large energy dissipation incident to tension control.
  • the present system can accommodate downstream web speed changes because the clutches operate off the main line shaft, as does the downstream webconsuming machine so they compensate for any such change. Further, any speed upsets are not translated into web tension upsets as is the case with some prior infeeds.
  • the present infeed is much less expensive than prior systems, costing only about one-half as much as the type shown in U.S. Pat. No. 3,087,663 and on the order of one-third less than the type depicted in said U.S. Pat. No. 3,659,767 and its mechanical clutch-type drive is only on the order of one-third the size of the differential drives and motors in those prior infeeds, yet it is easier to operate and control.
  • a system for controlling tension in a moving web comprising A. a draw roll for engaging said web,
  • a balanced, undamped, low inertia dancer assembly positioned between the draw roll and the guide roll, said dancer assembly including 1. a frame, and 2. a pair of spaced-apart dancer rolls rotatively supported by the frame so that their axes are parallel to the draw and guide roll axes and for engaging opposite sides of said web,
  • D. means for pivotally mounting the frame so that it can pivot about an axis midway between and parallel to the dancer rolls in response to changes in the tension of the web
  • F. means for detecting movement of the dancer assembly away from its reference position in response to a change in web tension and producing an output signal in response thereto
  • G means responsive to said output signal for applying the proper torque correction to the draw roll to change the tension in the web such that the dancer assembly tends to return to its reference position.
  • B. means for mounting the nip roll so as to form a nip with the draw roll to minimize slippage of web on the draw roll.
  • the torque applying means comprises A. a pressurizable loading cylinder having a movable shaft,
  • C. means for pivotally connecting the loading cylinder and its shaft between the frame and the support so that when the cylinder is pressurized, the frame is pivoted about its axis so as to lengthen the web path between the draw roll and the guide roll, and
  • D. means for pressurizing the cylinder so as to maintain the assembly in its reference position at said selected web tension.
  • the detecting means include a potentiometer whose resistance changes as the assembly deviates from its reference position.
  • the controller comprises 1. a first current regulator responsive to the output of the detecting means for controlling the current in the overspeed clutch,
  • the coupling means include A. means for amplifying the output of the detecting means,
  • C. means for summing the outputs of the amplifying and differentiating means so that the signal applied to the current regulators reflects the instantaneous position and velocity of the dancer assembly.
  • the coupling means also include a lag circuit connected between the summing means and the current regulators.
  • D. means for summing the second signal at the input of the second current regulator, so as to provide negative feedback to more closely regulate the currents in the overspeed and underspeed clutches.
  • a system for maintaining uniform tension in a moving web comprising A. a draw roll for engaging the web,
  • a dancer assembly positioned adjacent the draw roll, said dancer assembly including 1. at least one dancer roll rotatively supported parallel to the axis of the draw roll and for engaging the moving web,
  • G an electronic controller connected between the detecting means and the clutches for controlling the clutches in accordance with the output signal from the detecting means so that the draw roll controls the tension in the web as needed to maintain the dancer assembly in its reference position.
  • controller is comprised of A. a position amplifier connected to amplify the output signal from the detecting means,
  • C. means for summing the outputs of the amplifier and differentiator so as to produce a signal representing the instantaneous position and velocity of the dancer assembly
  • controlling means include means for applying the output signal from the summing means alternatively to said clutches.
  • a system for controlling tension in a moving web comprising A. a driven roll for engaging the web,
  • D. means for sensing a tension change in the web and developing a control signal corresponding thereto
  • E. means for coupling the control signal to the clutch to vary the torque coupling from the prime mover to the driven roll to produce a compensating tension change in the web.
  • the coupling means include a current regulator responsive to said control signal for controlling the current in the clutch.
  • C. means for applying said control signal alternatively to the first and second current regulators so that the proper torque is coupled to the driven roll.

Landscapes

  • Controlling Rewinding, Feeding, Winding, Or Abnormalities Of Webs (AREA)
  • Registering, Tensioning, Guiding Webs, And Rollers Therefor (AREA)
US447695A 1974-03-04 1974-03-04 Web tension control system Expired - Lifetime US3912145A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US447695A US3912145A (en) 1974-03-04 1974-03-04 Web tension control system
FR7506534A FR2263187B1 (es) 1974-03-04 1975-03-03
JP2586475A JPS5327436B2 (es) 1974-03-04 1975-03-03
IT67536/75A IT1030255B (it) 1974-03-04 1975-03-03 Dispositivo regolatore della tensione di un materiale nastriforme in movimento
DE19752509382 DE2509382A1 (de) 1974-03-04 1975-03-04 Einrichtung zur steuerung der spannung einer bandfoermigen materialbahn
GB8968/75A GB1501292A (en) 1974-03-04 1975-03-04 Web tension control apparatus

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US447695A US3912145A (en) 1974-03-04 1974-03-04 Web tension control system

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US3912145A true US3912145A (en) 1975-10-14

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US447695A Expired - Lifetime US3912145A (en) 1974-03-04 1974-03-04 Web tension control system

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US (1) US3912145A (es)
JP (1) JPS5327436B2 (es)
DE (1) DE2509382A1 (es)
FR (1) FR2263187B1 (es)
GB (1) GB1501292A (es)
IT (1) IT1030255B (es)

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US4266461A (en) * 1979-07-05 1981-05-12 Karg Corporation Tandem braiding system and components thereof
US4445044A (en) * 1981-07-02 1984-04-24 L. E. Buess, Inc. Angular position transducer having a bipolar analog output signal
US4464916A (en) * 1982-05-28 1984-08-14 The Minster Machine Company Loop follower straightener control in a press installation
US4513898A (en) * 1982-03-22 1985-04-30 Centronics Data Computer Corp. Web loop control apparatus and method
US4775086A (en) * 1985-08-27 1988-10-04 Hiroshi Kataoka Take-out/take-up tension control apparatus
US4896808A (en) * 1987-09-17 1990-01-30 Koening & Bauer Aktiengesellschaft Device for the controlled infeed of a web to a printing machine, method for regulating a corresponding control signal, and device for performing the method
WO1991001216A1 (en) * 1989-07-25 1991-02-07 Sterling Envelope Corporation Dual-envelope making machine and method of using
US5517914A (en) * 1994-09-30 1996-05-21 Tilton, Sr.; Danny E. Web tension regulator for printing machine
US5558263A (en) * 1994-07-26 1996-09-24 Eastman Kodak Company Apparatus and method for non-contact active tensioning and steering of moving webs
US5704304A (en) * 1994-05-27 1998-01-06 Burton & Noonan Level lining apparatus and method
WO1998003328A1 (en) * 1996-07-24 1998-01-29 Johnson James R Fastener tape material, bag utilizing fastener tape material, and method of manufacture thereof
US5783258A (en) * 1997-03-06 1998-07-21 Garapick; Ronald T. Method for treating lumber
US5894797A (en) * 1995-08-30 1999-04-20 Goss Graphic Systems, Inc. Tension control device for a printing press
US5956929A (en) * 1997-04-18 1999-09-28 I.D. Images, Inc. Packaging system for the tube stock continuous film media
US5964390A (en) * 1994-11-23 1999-10-12 Sca Hygiene Products Ab Arrangement and web tension control unit for web delivery
US6279472B1 (en) * 1999-08-31 2001-08-28 Miyakoshi Printing Machinery, Co., Ltd. Web curling prevention device for a rotary printing press or the like
US6554223B1 (en) 2000-04-04 2003-04-29 The Procter & Gamble Company Apparatus and a method for aligning a web
US6659006B2 (en) 1995-08-30 2003-12-09 Goss Graphic Systems Inc. Tension control device for a printing press
US6843038B1 (en) * 2003-08-21 2005-01-18 Illinois Tool Works Inc. Method and apparatus for controlling zipper tension in packaging equipment
US20050166670A1 (en) * 2004-02-04 2005-08-04 The Procter & Gamble Company Method of determining a modulus of elasticity of a moving web material
US20070131036A1 (en) * 2005-12-09 2007-06-14 Stephan Schultze Method for determining a web tension
US20110020043A1 (en) * 2007-08-09 2011-01-27 Konica Minolta Holdings, Inc. Device and method for drawing a web of printable carrier material
US8733686B2 (en) 2010-10-25 2014-05-27 The Procter & Gamble Company Alternative apparatus for reducing web feed rate variations induced by parent roll geometry variations
US8733685B2 (en) 2010-10-25 2014-05-27 The Procter & Gamble Company Apparatus for reducing web feed rate variations induced by parent roll geometry variations
US8733687B2 (en) 2010-10-25 2014-05-27 The Procter & Gamble Company Alternative apparatus for reducing web feed rate variations induced by parent roll geometry variations
US8740130B2 (en) 2010-10-25 2014-06-03 The Procter & Gamble Company Alternative method for reducing web feed rate variations induced by parent roll geometry variations
US8757535B2 (en) 2010-10-25 2014-06-24 The Procter & Gamble Company Method for reducing web feed rate variations induced by parent roll geometry variations
US8770878B2 (en) 2011-02-08 2014-07-08 Xerox Corporation System and method for monitoring a web member and applying tension to the web member
CN104355160A (zh) * 2014-10-31 2015-02-18 黄山富田精工制造有限公司 一种张力控制装置
WO2015056116A1 (en) * 2013-10-15 2015-04-23 Kimberly-Clark Worldwide, Inc. Active center pivot device for controlling sheet tension and method of using same
US9033200B2 (en) 2012-02-20 2015-05-19 Xerox Corporation Method and device for controlling tension applied to a media web
US9434573B2 (en) 2010-10-25 2016-09-06 The Procter & Gamble Company Alternative method for reducing web feed rate variations induced by parent roll geometry variations
US9434572B2 (en) 2010-10-25 2016-09-06 The Procter & Gamble Company Alternative method for reducing web feed rate variations induced by parent roll geometry variations
CN108819502A (zh) * 2018-06-01 2018-11-16 广州来丽智能科技有限公司 张力控制机构及具有其的数码喷印设备
US11008127B2 (en) 2016-10-31 2021-05-18 Zing-Pac, Inc. Floating platen system
US11447356B2 (en) 2020-05-18 2022-09-20 Butler Automatic, Inc. System and method for aligning and joining the same sides of two web materials

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US4896808A (en) * 1987-09-17 1990-01-30 Koening & Bauer Aktiengesellschaft Device for the controlled infeed of a web to a printing machine, method for regulating a corresponding control signal, and device for performing the method
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US5647276A (en) * 1994-09-30 1997-07-15 Tilton, Sr.; Danny Eugene Web tension regulator for printing machine
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US5964390A (en) * 1994-11-23 1999-10-12 Sca Hygiene Products Ab Arrangement and web tension control unit for web delivery
US6276587B1 (en) 1994-11-23 2001-08-21 Sca Hygiene Products Ab Arrangement for delivering a web of material from a storage reel to a process line, and a unit included in the arrangement
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US6279472B1 (en) * 1999-08-31 2001-08-28 Miyakoshi Printing Machinery, Co., Ltd. Web curling prevention device for a rotary printing press or the like
US6554223B1 (en) 2000-04-04 2003-04-29 The Procter & Gamble Company Apparatus and a method for aligning a web
US6843038B1 (en) * 2003-08-21 2005-01-18 Illinois Tool Works Inc. Method and apparatus for controlling zipper tension in packaging equipment
US20050124479A1 (en) * 2003-08-21 2005-06-09 Haws Lewis A. Method for controlling zipper tension in packaging equipment
US7121063B2 (en) * 2003-08-21 2006-10-17 Illinois Tool Works Inc. Method for controlling zipper tension in packaging equipment
US20050166670A1 (en) * 2004-02-04 2005-08-04 The Procter & Gamble Company Method of determining a modulus of elasticity of a moving web material
US6993964B2 (en) * 2004-02-04 2006-02-07 The Procter & Gamble Company Method of determining a modulus of elasticity of a moving web material
US20070131036A1 (en) * 2005-12-09 2007-06-14 Stephan Schultze Method for determining a web tension
US20110020043A1 (en) * 2007-08-09 2011-01-27 Konica Minolta Holdings, Inc. Device and method for drawing a web of printable carrier material
US8757535B2 (en) 2010-10-25 2014-06-24 The Procter & Gamble Company Method for reducing web feed rate variations induced by parent roll geometry variations
US9434573B2 (en) 2010-10-25 2016-09-06 The Procter & Gamble Company Alternative method for reducing web feed rate variations induced by parent roll geometry variations
US8733687B2 (en) 2010-10-25 2014-05-27 The Procter & Gamble Company Alternative apparatus for reducing web feed rate variations induced by parent roll geometry variations
US8740130B2 (en) 2010-10-25 2014-06-03 The Procter & Gamble Company Alternative method for reducing web feed rate variations induced by parent roll geometry variations
US8733686B2 (en) 2010-10-25 2014-05-27 The Procter & Gamble Company Alternative apparatus for reducing web feed rate variations induced by parent roll geometry variations
US9434572B2 (en) 2010-10-25 2016-09-06 The Procter & Gamble Company Alternative method for reducing web feed rate variations induced by parent roll geometry variations
US8733685B2 (en) 2010-10-25 2014-05-27 The Procter & Gamble Company Apparatus for reducing web feed rate variations induced by parent roll geometry variations
US8770878B2 (en) 2011-02-08 2014-07-08 Xerox Corporation System and method for monitoring a web member and applying tension to the web member
US9033200B2 (en) 2012-02-20 2015-05-19 Xerox Corporation Method and device for controlling tension applied to a media web
WO2015056116A1 (en) * 2013-10-15 2015-04-23 Kimberly-Clark Worldwide, Inc. Active center pivot device for controlling sheet tension and method of using same
US9309081B2 (en) 2013-10-15 2016-04-12 Kimberly-Clark Worldwide, Inc. Active center pivot device for controlling sheet tension and method of using same
CN104355160A (zh) * 2014-10-31 2015-02-18 黄山富田精工制造有限公司 一种张力控制装置
US11008127B2 (en) 2016-10-31 2021-05-18 Zing-Pac, Inc. Floating platen system
CN108819502A (zh) * 2018-06-01 2018-11-16 广州来丽智能科技有限公司 张力控制机构及具有其的数码喷印设备
US11447356B2 (en) 2020-05-18 2022-09-20 Butler Automatic, Inc. System and method for aligning and joining the same sides of two web materials

Also Published As

Publication number Publication date
JPS5115765A (es) 1976-02-07
JPS5327436B2 (es) 1978-08-08
IT1030255B (it) 1979-03-30
GB1501292A (en) 1978-02-15
DE2509382A1 (de) 1975-09-11
FR2263187A1 (es) 1975-10-03
FR2263187B1 (es) 1980-12-26

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