US3545694A - Apparatus for winding and unwinding strip material - Google Patents

Apparatus for winding and unwinding strip material Download PDF

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Publication number
US3545694A
US3545694A US723155A US3545694DA US3545694A US 3545694 A US3545694 A US 3545694A US 723155 A US723155 A US 723155A US 3545694D A US3545694D A US 3545694DA US 3545694 A US3545694 A US 3545694A
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United States
Prior art keywords
belt
rollers
pulley
winding
tensioning lever
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Expired - Lifetime
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US723155A
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English (en)
Inventor
Kurt Ehrat
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BASF Schweiz AG
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Ciba AG
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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
    • B65H16/00—Unwinding, paying-out webs
    • B65H16/10—Arrangements for effecting positive rotation of web roll
    • B65H16/103—Arrangements for effecting positive rotation of web roll in which power is applied to web-roll spindle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H18/00—Winding webs
    • B65H18/08—Web-winding mechanisms
    • B65H18/10—Mechanisms in which power is applied to web-roll spindle

Definitions

  • Apparatus for winding and unwinding strip [31 1 6107/67 material from a spool includes a belt-driven pulley coupled to [54] APPARATUS FOR WINDING AND UNWlNDlNG STRIP MATERIAL 11 Claims, 12 Drawing Figs.
  • the pairs of driving rollers and the brake are controlled in an alternative manner by means of a cam arrangement associated with and actuated by a spring-loaded tension lever including a strip tensioning roller around which the strip material passes on its way to or from the spool. As the tension in the strip material varies, the tensioning lever will move in one direction or the other from an intermediate position in which the cam means applies the brake to the belt. Movement of the tensioning lever in one direction puts one pair of driving rollers into operation thus to drive the belt and pulley in one direction, and movement of the lever in the opposite direction puts the other pair of driving rollers into operation to drive the belt and pulley in the opposite direction.
  • the motors driving the winding bobbins or spools are started, stopped, or reversed L by the position of a lever whose position is governed by the i the tensioning lever.
  • the brake means consist of a band which envelops a brake cylinder and which is tensioned' by a solenoid for generating the braking force.
  • strip winding devices have certain drawbacks which are primarily derived from the combination of several strip winding devices requiring provision of separate drive motors with associated switch means for starting, stopping, and reversing the motor, and so forth for each winding bobbin or spool and that all the components must be designed to handle relatively high loads. This is reflected in relatively high cost. Load incurred by the starting and stopping of the motors, activating and deactivating the brake solenoids, are considerable and interference with neighbouring electronic circuits may result. This can be avoided only by providing suppressor devices which add to the cost of the apparatus.
  • the speed of the winding bobbin or spool depends, on the one hand, upon the speed of the strip and, on the other hand, upon whether the spool carries a fully wound roll or an empty roll.
  • the required ratio of the rotary speeds of the full and the empty winding spool may be as high as 1:4 or even more, in order to keep the speed of the strip perfectly constant.
  • the motors must therefore be designed to provide the maximum necessary speed for the empty spool and also to generate the maximum torque for rotating the fully wound spool. In other words, the motors must be robust. In conventional strip winding apparatus this means that the. controlled loads are high and add considerably to the moment of inertia of the winding spool and the roll of strip material wound thereon.
  • I provide apparatus for winding and unwinding strip material, comprising a belt-driven pulley onto and from which the strip material is wound or unwound, at least one tensioning roller over which the strip material is arranged to be passed, the tensioning roller being mounted on a spring-loaded tensioning lever, a first and second pair of drive rollers, and a brake, the two pairs of drive rollers and the brake being alternatively controlled by a cam movable by the tensioning lever so that in a first position of the tensioning lever the cam activates the first pair of drive rollers to engage the belt to drive it in a first direction, in a second position of the tensioning lever the brake is actuated by the cam to stop movement of the belt and in a third position of the tensioning lever the cam activates the second pair of drive rollers to engage the belt to drive it in a direction opposite to said first direction, the drive rollers and brake when engaged with said belt being arranged to provide a frictional force in excess of that between the belt and pulley.
  • the following preferred embodiments include a belt which travels between first and second pairs of continuously driven rollers and a pair of brakeshoes so alternatively controlled by a cam which is movable by a tensioning lever that in a first end position of the tensioning lever the first pair of drive rollers, in a centre position of the tensioning lever the pair of brakeshoes and in the other end position of the tensioning lever the second pair of drive rollers is pressed into contact with the belt and thus activated, the arrangement being such that the driving and braking forces between the drive rollers and brakeshoes respectively and the belt exceed the force of friction between the belt and the pulley that is driven by the belt.
  • FIGS. 1 to 3 are a first embodiment of apparatus according to the invention shown in three different operating states
  • FIG. 4 is a simplified representation of the apparatus in FIGS. 1 to 3 illustrating the kinematics of the proposed arrangement
  • FIG. 5a is an equivalent diagram of the distribution of forces
  • FIG. 5b is a time-speed diagram relating to FIG. 5a;
  • FIG. 6 is a rewinding apparatus combining two complete systems of the kind illustrated in FIGS. 1 to 3;
  • FIG. 7 is a modification of the apparatus according to FIGS. 1 to 3 adapted to provide three different winding speeds
  • FIG. 8 is a simplified section taken on the line VIII- VIII in FIG. 7;
  • FIG. 9 is a diagram for further elucidating the functioning of the embodiment according to FIGS. 7 and 8.
  • FIGS. 10a and 10b represent a modification of a detail in the embodiments according to FIGS. 1 to 3 and 6 to 7.
  • a pulley 4 coupled to a winding bobbin or spool 2 on a shaft 1 for common rotation therewith.
  • the strip material or tape 3 which can be wound on or drawn off the spool 2 runs over rollers 8, 9, l0, and 11.
  • the two rollers 10 and 11 are mounted on fixed axles, whereas the two others 8 and 9 are mounted on a tensioning lever 7 which pivots on a fulcrum at 37.
  • An endless belt 5 engages the periphery of the pulley 4 and is kept taut by tensioning rollers 12 and 13. These tensioning rollers are each mounted on a belt tensioning swivel arm 14 and 15 fulcrumed on fixed pivots l6 and 17.
  • the tension of the belt is maintained by springs 18 and 19 which apply a given pull to the swivel arms 14 and 15.
  • the deflection of the belt tensioning swivel arms is limited by stops 20 and 21.
  • a first pair of forward drive rollers V 22 and 23 and a second pair of reverse drive rollers R 24 and 25 Cooperating with that portion of the belt which travels between the two tensioning rollers 12 and 13 are a first pair of forward drive rollers V 22 and 23 and a second pair of reverse drive rollers R 24 and 25.
  • a brake B comprising brakeshoes 26 and 27.
  • At least one roller of each pair of drive rollers 22, 23 and 24, 25 can be driven by a motor in the direction indicated by arrows.
  • the rollers 22 and 24 run in fixed bearings, whereas the two rollers 23 and 25 are each rotatably mounted on the end of a swivel arm 28 and 29.
  • the swivel arms 28 and 29 are fulcrumed on pivots 30 and 31.
  • Springs 32 and 33 urge the-arms towards the belt 5 and the cooperating fixed rollers 22, 24.
  • the brakeshoe 26 is fixed, whereas the other brakeshoe 27 is mounted on a lever 34 which is deflectable about a pivot at 35.
  • a spring 36 which is attached to the lever 34 urges the movable brakeshoe 27 towards the fixed brakeshoe 2.6.
  • the pivoted end of the tensioning lever 7 is modified to form a quadrant 38 which contains a cam slot 39.
  • the track of this cam slot 39 cooperates with follower elements which in the illustrated embodiment take the form of pins 40, 41, and 42, pins 40 and 42 being affixed to the lever arms 28 and 29 of the drive rollers 23 and 25 and pin 41 being affixed to the lever arm 34 carrying the brakeshoe 27.
  • the pins 40 and 42 are affixed to the ends of their respective levers 28 and 29.
  • the cam slot 39 is so shaped and disposed in relation to the follower elements that only one of the pairs of drive rollers 22, 23 and 24, 25 or the brake can take effect at any one time.
  • the cam slot is formed with a recess E for the reception of one of the pins 40, 41, and 42 to activate the element controlled by the pin.
  • the recess E exceeds the maximum possible deflection of the pins 40, 41, and 42 by an amount d to ensure that the full power of the springs 32, 33, and 36 associated with the pins can be exerted to press the respective element against the belt when one of the pins has been received into the recess.
  • the maximum possible deflection of the pins 41 and 42 is determined by the position of the fixed rollers 22 and 24 and that of the pin 41 by the position of the fixed brakeshoe 26.
  • FIG. 2 shows the tensioning lever in its centre position.
  • the belt is therefore gripped between the two brakeshoes 26 and 27 and neither the pulley 4 nor the winding spool 2 can move.
  • the tensioning arm 7 in the upward direction.
  • the pulley and the winding spool first remain stationary untilthe tensioning lever has been upwardly deflected sufficiently for the swivel arm 34 of the brake 26, 27 to have been retracted by the cam slot 39 in the quadrant 38 and the brake to have been released.
  • the tension at point PE should be as small as possible.
  • the tension at PE is determined by the rating of the spring 44 of the tensioning lever and by the resistance to displacement of the control cam in the quadrant 38, 39 of the tensioning lever. This resistance depends upon the efiort required for deflecting the swivel arms (28, 29 and 34). This effort is numerically defined by the distance H of deflection multiplied by the spring force acting on the swivel am. It is therefore desirable to minimise this distance H and the spring force.
  • the distance H may be reduced to as little as a few tenths of a millimetre.
  • the spring force (springs 32, 33 and 36) which determines the gripping power of the rollers and brake must be so chosen that the friction between the belt and the drive rollers and the belt and the brakeshoes will definitely exceed the friction between the belt and the circumference of the pulley. If this were not the case the belt would not slip on the pulley but it would slip between the drive rollers. Continuous slippage between the drive rollers means excessive wear of the belt. It is therefore desirable that the friction between the belt and the circumference of the pulley should not be very high to permit the gripping force of the drive rollers to be correspondingly reduced and the tension (at PE) to remain fairly small.
  • the friction between the belt and the pulley should not be less than a given minimum to prevent the time required for bringing the spool up to speed to become so long that, in the position as shown in FIG. 2 and at an increasing speed of takeoff of the strip at PE when the roll is at its maximum diameter (i.e. its moment of inertia is a maximum), the tensioning lever and its rollers 8 and 9 would be dragged too far upwards and into contact with the fixed rollers 10 and 11. This would interfere with the proper functioning of the mechanism.
  • the pulling force of the belt on the circumference of the pulley should not therefore be less than a given minimum value, but at the same time it should also not be excessive.
  • the pulling force applied by the belt to the pulley should therefore be substantially constant. It is well known that in the absence of special arrangements the frictional forces, which are governed by various external factors (contamination, surface quality, and so forth), are not usually constant.
  • the special arrangements which in the present instance this embodiment provides comprise a mechanical compensating device which stablises the pull which the belt is capable of applying to the circumference of the pulley. This compensating device will now be described by reference to FIG. 4.
  • FIG. 4 illustrates the proposed system at a time when the pulley is still stationary and the drive rollers 22 and 23 have just been allowed to move into engagement by the control cam (not shown in FIG. 4, but constructed as illustrated in FIGS. 1 to 3) for driving the belt in the forward direction (arrow V).
  • the control cam not shown in FIG. 4, but constructed as illustrated in FIGS. 1 to 3 for driving the belt in the forward direction (arrow V).
  • the portion 5A of the belt therefore rides onto the pulley
  • the actual peripheral pull P, applied to the pulley by the belt is therefore represented by the following equation: P, P, P P P eupor P, P,.-(l l/ezp).
  • FIG. 6 two mechanisms of the kind shown in FIG. 1, (to 3) are combined to form a single rewinding machine .with asingle driving motor M.
  • components corresponding to like components in FIG. I bear the same reference numerals as in FiG. 1.
  • Like components in the lefthand system are likewise identified by the same reference numerals but they are distinguishedby a prime.
  • Each of the two systems functions independently from the other as has already been described with reference to FIGS. 1 to 3. However, for cooperation one system is always set to wind on and the other to wind off, or both systems are braked. In the drawing the left-hand system is set to wind on.
  • the strip material travels from point PE to point PE through guide meanswhich are irrelevant to the invention. Treating and/or viewing stations may be provided between PE and PE. 7
  • FIGS. 7 to 9 illustrate an embodiment of the invention specially designed for several different speed ranges. This embodiment is therefore in effect fitted with three pulleys 4,, 4,, and 4 of different diameters. As a matter of practice a single pulley structurehaving three stepped diameters is utilized.
  • each of the three belts 5,, 5,,, and 5, is associated with a deflectably movable roller 23,, 23,,, and 23,,, and 25,, 25,,
  • each pair of rollers (23,/25,, 2 11/25 23,,,/25m) is in turn associated with a control cam of its own.
  • the three cams are provided on three quadrants 38,, 38,, and 38 affixed to a common strip tensioning lever 7.
  • the three control cams are so contrived and relatively positioned that the system functions as follows: In the highest position of the tensioning lever 7 the roller 23, is pressed into contact with the belt and the highest forward speed is thus obtained. If the tensioning lever drops towards its centre position, the roller 23, is withdrawn and the roller 23,,
  • the tensioning lever 7 thus functions like a gear selector lever.
  • the three cams of the three quadrants 38,, 38 and 38 are naturally again so contrived (cf. FIGS. 1 to 5) that only one of the rollers or the brake can cooperate with one of the belts at the same time.
  • graph form represents the functional dependence of the speed of the winding spool upon the position of the tensioning lever.
  • FIGS. 10a and 10b illustrate a variant of the control cam in which the quadrant 38 formed with a cam track 39 is pivotably mounted and coupled to the tensioning lever 7 by a lost motion mechanism.
  • the control quadrant works on the same shaft as the tensioning lever to which it is coupled by a sliding pin and slot motion 52-51.
  • the pin 52 is fast on the tensioning lever and works in a recess 51 cut into the periphery of the quadrant. Thisarrangement introduces the lost motion into the action of the tensioning lever when the latter reverses its direction of deflection.
  • the delay S introduced by the lost motion- is determined by the length of the recess 51 in the quadrant and the diameter of the pin.
  • the quadrant is engaged as soon as the pin 52 makes contact with the upper end of the recess 51.
  • the tensioning lever is lowered the quadrant is engaged when the pin 52 is intercepted by the bottom end of the recess 51.
  • This hysteresis effect which is thus introduced into the working of the control means prevents the tensioning lever from continuously stopping and starting the belt when the lever oscillates within a small angle. After having started the belt the tensioning lever must therefore be deflected through a distance S before the belt is again stopped.
  • the transmission from the drive motor M (H6. 6) to the drive rollers may be a belt drive, gearing or the like. Either both rollers of a pair or only thefixed roller may be driven.
  • Apparatus for winding and unwinding strip material comprising a belt, a pulley driven by said belt, a winding spool coupled to said pulley, the strip material being wound onto or drawn off said winding spool dependent upon the direction of rotation of said pulley, first and second pairs of driving'rollers between which said belt passes, a brake mechanism for said belt, a spring-loaded tensioning lever, at least one strip material tensioning roller mounted on said lever and around which the strip material passes, and cam means actuated by movement of said tensioning lever as the tension in said strip material passing around said tensioning roller varies and operatively connected respectively with said first and second pairs of belt-driving rollers and said brake mechanisms for alternative activation dependent upon the position of said tensioning lever, said lever when moved to a first position actuating said cam means to activate said first pair of rollers to engage and drive said belt and pulley in one direction, said lever when moved to a second position actuating said cam means to activate said second pair of rollers to engage and drive said belt
  • Apparatus as defined in claim 1 for winding and unwinding strip material and which further includes a plurality of belt-tensioning pulleys around which said belt passes and which are located intermediate said belt-driving rollers and pulley, swivel arms individual to and mounting said belt-tensioning rollers, spring means individual to and biasing said swivel arms and the belt-tensioning rollers thereon into contact with said belt so as to tension it, and stop means individual to said swivel arms for limiting the movement of said swivel arms in the belt-tensionin direction.
  • cam means for winding and unwinding strip material
  • said cam means includes a cam track member actuated by said tensioning lever and cam follower means engaged with said track and individual respectively to said first and second. pairs of belbdriving rollers and said brake mechanism for actuating the same alternatively into engagement with said belt.
  • each pair of belt-driving rollers includes one power-drivenroller engaging said belt and rotating on a fixed axis and a second roller mounted on a spring-loaded swivel arm which normally biases said second roller into pressing engagement withsaid belt
  • said cam means includes a cam track member actuated by said tensioning lever and cam followers engaged with said cam track, said cam track being formed with a'recess and said cam followers being mounted respectively on said swivel arms and serving to shift the corresponding second roller in a direction away from said belt except when the cam follower occupies the recess in said cam track.
  • cam means includes a cam I track fonned integrally with; said tensioning lever and. earn track follower means operatively-connected with said first and second pairs of driving rollers and said brake mechanism.
  • Apparatus as defined in claim 1 for winding and unwinding strip material and which further includes a lost motion mechanism interposed between said tensioning lever and said cam means for delaying actuation of said cam means until said v tensioning lever has moved a predetermined distance from its intermediate position.
  • cam means for winding and unwinding strip material
  • said cam means includes a pivotally mounted cam member provided with a cam track and a plurality of cam track follower means operatively connected with said first and second pairs of driving rollers and said brake mechanism respectively and which further includes a lost motion mechanism interposed between said tensioning lever and said cam member for delaying action of said cam means until said tensioning lever has moved a predetermined distance from its intermediate position.
  • V 10 Apparatus as defined in claim 9 for winding and unwinding strip material wherein said lost motion mechanism includes a pin movable between two spaced abutrnents, said pin being carried by said tensioning lever and said abutrnents being carried by said pivotally mounted cam member, or vice versa.

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  • Controlling Rewinding, Feeding, Winding, Or Abnormalities Of Webs (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
US723155A 1967-04-28 1968-04-22 Apparatus for winding and unwinding strip material Expired - Lifetime US3545694A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH610767A CH473725A (de) 1967-04-28 1967-04-28 Vorrichtung zum Auf- und Abwickeln von bandförmigem Material

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US3545694A true US3545694A (en) 1970-12-08

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US723155A Expired - Lifetime US3545694A (en) 1967-04-28 1968-04-22 Apparatus for winding and unwinding strip material

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US (1) US3545694A (de)
CH (1) CH473725A (de)
DE (1) DE1774173A1 (de)
FR (1) FR1561746A (de)
GB (1) GB1214855A (de)
NL (1) NL6805967A (de)
SE (1) SE331777B (de)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3885747A (en) * 1974-03-28 1975-05-27 Bendix Corp Control device for rolled material feed
US4241884A (en) * 1979-03-20 1980-12-30 George Lynch Powered device for controlling the rotation of a reel
EP0315029A1 (de) * 1987-11-03 1989-05-10 Aktiebolaget PROFOR Abwickeleinrichtung
US20030228964A1 (en) * 2002-06-10 2003-12-11 Biba Scott I. Apparatus and method for braking and controlling tension in a web
US20040020171A1 (en) * 2002-06-10 2004-02-05 Biba Scott I. Web cutter
US7089718B2 (en) 2002-06-10 2006-08-15 Green-Line Products, Inc. Apparatus for heat-shrinking film onto an open-topped container and method of using same
US20110240788A1 (en) * 2010-03-31 2011-10-06 Ricoh Company, Ltd. Sheet conveyance unit and image forming apparatus including same
US20190232690A1 (en) * 2018-02-01 2019-08-01 Seiko Epson Corporation Medium supply device
CN116002428A (zh) * 2022-12-26 2023-04-25 青岛久越新材料科技有限公司 一种高速卷绕机用的基材收紧结构

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4441664A (en) * 1982-07-26 1984-04-10 Anderson Bros. Mfg. Co. Apparatus for feeding web material from a supply roll
GB9119872D0 (en) * 1991-09-17 1991-10-30 Thurne Eng Co Ltd Bag sealing machine

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3885747A (en) * 1974-03-28 1975-05-27 Bendix Corp Control device for rolled material feed
US4241884A (en) * 1979-03-20 1980-12-30 George Lynch Powered device for controlling the rotation of a reel
EP0315029A1 (de) * 1987-11-03 1989-05-10 Aktiebolaget PROFOR Abwickeleinrichtung
AU614099B2 (en) * 1987-11-03 1991-08-22 Ab Tetra Pak Unwinding arrangement
US20030228964A1 (en) * 2002-06-10 2003-12-11 Biba Scott I. Apparatus and method for braking and controlling tension in a web
US20040020171A1 (en) * 2002-06-10 2004-02-05 Biba Scott I. Web cutter
US7089718B2 (en) 2002-06-10 2006-08-15 Green-Line Products, Inc. Apparatus for heat-shrinking film onto an open-topped container and method of using same
US20110240788A1 (en) * 2010-03-31 2011-10-06 Ricoh Company, Ltd. Sheet conveyance unit and image forming apparatus including same
US9027867B2 (en) * 2010-03-31 2015-05-12 Ricoh Company, Ltd. Sheet conveyance unit and image forming apparatus including same
US20190232690A1 (en) * 2018-02-01 2019-08-01 Seiko Epson Corporation Medium supply device
US11040558B2 (en) * 2018-02-01 2021-06-22 Seiko Epson Corporation Medium supply device
CN116002428A (zh) * 2022-12-26 2023-04-25 青岛久越新材料科技有限公司 一种高速卷绕机用的基材收紧结构

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Publication number Publication date
DE1774173A1 (de) 1971-10-14
NL6805967A (de) 1968-10-29
FR1561746A (de) 1969-03-28
SE331777B (de) 1971-01-11
GB1214855A (en) 1970-12-09
CH473725A (de) 1969-06-15

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