US3445077A - Strand distributing and receiving apparatus and method - Google Patents

Strand distributing and receiving apparatus and method Download PDF

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Publication number
US3445077A
US3445077A US658185A US3445077DA US3445077A US 3445077 A US3445077 A US 3445077A US 658185 A US658185 A US 658185A US 3445077D A US3445077D A US 3445077DA US 3445077 A US3445077 A US 3445077A
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Prior art keywords
strand
shaft
angular velocity
continuously
convolutions
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English (en)
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Joseph I Cole
Harold S Moss
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Nassau Smelting and Refining Co Inc
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Nassau Smelting and Refining Co Inc
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES OR PROFILES, OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C47/00—Winding-up, coiling or winding-off metal wire, metal band or other flexible metal material characterised by features relevant to metal processing only
    • B21C47/02—Winding-up or coiling
    • B21C47/10—Winding-up or coiling by means of a moving guide
    • B21C47/14—Winding-up or coiling by means of a moving guide by means of a rotating guide, e.g. laying the material around a stationary reel or drum
    • B21C47/143—Winding-up or coiling by means of a moving guide by means of a rotating guide, e.g. laying the material around a stationary reel or drum the guide being a tube
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H54/00—Winding, coiling, or depositing filamentary material
    • B65H54/76—Depositing materials in cans or receptacles
    • B65H54/80—Apparatus in which the depositing device or the receptacle is rotated

Definitions

  • strand which is advanced continuously at constant speed be distributed in compact spiral layers on the receiver by utilizing a rotating distributor having an exit point through which the advancing strand is passed.
  • a rotating distributor makes unnecessary any rotation of the receiver, which rotation might result in centrifugal forces disrupting the pattern of convolutions previously laid on the receiver.
  • An object of the invention resides in new and improved methods and apparatus for distributing strand into spiral convolutions on a receiver.
  • An apparatus constructed in accordance with the principles of the invention and usable to practice the method of the invention employs a nonreciprocating, rotating clistributor, in the form of a flier tube through which strand material is continuously advanced, and a nonreciprocating, nonrotating receiver, in the form of a table or platform for receiving and supporting plural layers of spiral convolutions of strand.
  • a novel rotary speed regulating system for varying the angular velocity and angular acceleration of the rotating flier tube with time in a predetermined manner, a compact pattern of layers of spiral convolutions are laid upon the receiver.
  • the apparatus is set normally to lay each successive 3,445,077 Patented May 20, 1969 "ice convolution of strand just touching the last laid convolution in the same layer.
  • Successive layers of coiled strand are distributed on the receiver in alternate inwardly and outwardly spiraled configurations.
  • the particular position which each element of strand assumes upon the receiver is governed by (1) the angular velocity, angular acceleration and rate of change of angular acceleration of the rotating ilier tube at the time of distribution of the strand element and (2) the vertical distance between the flier tube and a reception point of the strand element on the receiver.
  • the vertical distance between the flier tube and the receiver is increased by the thickness of the strand after the distribution of each layer of convolutions.
  • the vertical distance between the topmost layer of strand on the receiver and the ier tube remains constant during strand distribution and the desired compact pattern of plural layers of spiral convolutions is maintained.
  • FIG. 1 is a plan view of apparatus'constructed in accordance with the principles of the invention for distributing onto a receiver a continuously advancing strand in accordance With'a desired pattern;
  • FIG. 2 is a side elevational view, the parts broken away, showing a portion of the strand distributing apparatus of FIG. l and also illustrating a receiving and supporting apparatus which is constructed in accordance with the principles of the invention for providing a compact pattern of spiral convolutions of distributed strand;
  • FIG. 3 is a circuit diagram illustrating a control circuit suitable for operating the apparatus to produce the desired compact pattern of spiral convolutions of strand;
  • FIG. 4 is a schematic illustration of the desired pattern of strand distribution, constituting one of several layers of compactly distributed spiral convolutions of strand.
  • FIG. 5 is a plot of required distributor angular velocity versus both time (solid line) and laying radius (dotted line) describing the distribution of strand from a continuously rotated distributor, included in the apparatus of FIG. l, through which the strand is advanced at constant linear velocity, in order to produce the desired pattern of FIG. 4.
  • the apparatus includes a continuously rotated distributor or tlier tube 12 for laying the strand 11 on a receiver apparatus 13 including a tub or drum 14 on a non-rotating receiver table or platform 16 for supporting coiled strand.
  • the ier tube is mounted for rotation in stationary bearings 15.
  • the strand 11 is continuously advanced through the ier tube 12 at a constant linear velocity by a capstan 17.
  • the capstan is driven by a constant speed rolling mill, such as is shown in Cole et al.
  • a pulley 22 is mounted on the distributor or flier tube 12 and is driven by a belt 23 to rotate the ier tube at a continuously varying angular velocity.
  • a compact pat- 3 tern of spiral convolutions of strand may be distributed by the flier tube on the receiver apparatus 13.
  • the strand would be laid in successive circular convolutions of identical radius.
  • the constant linear velocity of the advancing strand and the constant angular velocity of the tlier tube would determine this eiective laying radius.
  • the desired spiral (FIG. 4), having equidistant separation a between each convolution, is of a type known as the Spiral of Archimedes. See Lionel S. Marks, Mechanical Engineers Handbook (sixth edition, McGraw-Hill), pp. 2-61 and 262. Referring to the Archimedes spiral shown in FIG. 4, let:
  • r1, r2, r3 equal the radii of points on successive convolutions all taken at the same angular position.
  • l1 2, l2 3, [3 4 equal the length of an arc of one convolution between points r1-r2, r2-r3, ra-r.,
  • a equals the distance between the center lines of adjacent convolutions (constant).
  • w1, W2, w3 equal the instantaneous angular velocity of the ier tube at points r1 r2, r3
  • V the linear velocity of a point on the strand (constant).
  • valves for angular velocity w can be plotted either as a function of time or of laying radius. This infomation may then be used to preset the apparatus 4 of FIGS. 1 and 2 to achieve the desired coil size and spacing between convolutions.
  • the required instantaneous angular velocity of the flier tube 12 to lay any point on the arc of the spiral, at a distance r feet from the center may be calculated.
  • a coil having a 3 ft. outer diameter, a 2 ft. inner diameter, and a 0.2 ft. spacing between the center lines of adjacent convolutions is desired and wherein the linear velocity of the strand is 20 ft./sec.:
  • the slope of either curve continually increases as it is traced from a point of greater to lesser coil radius indicating a continually increasing angular acceleration.
  • a laying radius decreasing by uniform separation a between convolutions will occur with increasing angular acceleration.
  • uniform outward spiraling may be shown to result from rotating the ier tube 12 according to the plotted curves at continuously decreasing angular velocity and continuously decreasing deceleration, the decrease in angular deceleration with time being nonlinear.
  • Tables of data obtained in the above-exemplified manner may be used to determine the required curves of angular velocity versus time necessary for the rotation of the flier tube 12 of FIGS. l and 2 in order to produce any desired pattern of uniformly spaced spiral convolutions of strand on the receiving apparatus 13, for example, a pattern wherein adjacent convolutions just touch each other along their edges.
  • a rotary speed regulating apparatus 26 provides the required speed control to conform the rotation of the flier tube 12 to the calculated curves.
  • a shaft 27 leading from the right angle drive 19 provides an input drive to the speed regulating apparatus 26.
  • a pulley 28 on the shaft 27 drives another pulley 29 through a ⁇ belt 31.
  • the pulley 29 is mounted to drive an input shaft 32 of a conventional variable speed transmission 30.
  • the input shaft 32 is driven at constant speed, dependent upon the speed of rotation of the shaft 18.
  • the variable speed transmission 30 may be of a type in which a pair of V-belt, split pulleys 301 and 302 are mounted, respectively, on the input shaft 32 and an output shaft 33.
  • a V-belt 303 extends between the input shaft and the output shaft pulleys.
  • the respective pulley halves of the pulleys 301 and 302, i.e., 301A and 301B, 302A and 302B, are mounted for axial movement to vary the separation between the halves, thereby varying the effective pulley diameters, due to the presence of tapered inner surafces on the pulley halves.
  • Pulley halves 301A and 302A are both connected to a first lever 304 which is pivotal about a pin 306.
  • Pulley halves 301B and 302B are both connected to a second lever 307 which is pivotal about a pin 308.
  • Each lever 304 and 307 is provided with a pin-like rider 309 Iwhich seats within and moves axially along an externally threaded control shaft 34 to pivot the levers, as the control shaft is rotated.
  • the threading on the control shaft is in opposed directions at opposed ends thereof.
  • rotation of the control shaft 34 in a first direction will, as may be seen by observing FIG. l, separate the threaded lever ends, spreading apart the pulley halves 301A and 301B and bring the pulley halves 302A and 302B toward one another. Reversed rotation of the control shaft 34 will have an opposite effect upon the separation of the respective pulley halves.
  • the spacing between pulley halves determines the effective diameter of each pulley 301 and 302.
  • the ratio of effective diameters of the pulleys 301 and 302 may be varied linearly with the angle of control shaft rotation to vary thereby the speed of rotation of the output shaft 33.
  • the output shaft 33 rotates the flier tube 12 through a first power train which may be traced from a pulley 41 connected to shaft 33, through a belt 44, through a pulley 42, through a shaft 45, through a right-anglt drive 46, through a pulley 43 and then through the belt 23 and the pulley 22.
  • the output shaft ⁇ 33 is also connected by a second power train to rotate the control shaft 34.
  • This second power train includes a pulley 47 connected to shaft 33, a belt 48, and a pulley 49 mounted on the input shaft 51 of an auxiliary variable speed transmission 50.
  • the auxiliary variable speed transmission 50 may be of a type similar to the variable speed transmission 30.
  • An output shaft 52 from the auxiliary transmission 50 drives a shaft 53 through a right angle drive 54.
  • a pulley 56 connected to the shaft 53 drives a belt 57 to rotate a pulley 58 on a shaft 59.
  • a pair of'oppositely facing bevel gears 62 and 63 are rotatable on the shaft 59.
  • a first clutch 64 engaged by energization of a solenoid 264 (FIG. 3), is operable to provide a drive connection between the shaft 59 and the bevel gear 62.
  • a second clutch 66 engaged by energization of a solenoid 266 (FIG. 3), is operable to provide a drive connection between the shaft 59 and the ⁇ bevel gear 63.
  • Alternate engagement of the two clutches 64 and 66 enables the bevel gears 62 and 63 to drive a bevel gear 67, constantly enmeshed with both of the bevel gears, in alternately reversed directions.
  • the disconnected bevel gear 62 or 63 is meanwhile rotated in idling condition upon the shaft 59.
  • the bevel gear 67 is mounted on a threaded shaft 68.
  • a pulley 69 on the threaded shaft 68 drives a pulley 70, mounted on the control shaft 34, through a belt 71.
  • a reversing mechanism including a pair of limit switches 72 and 73 mounted adjacent the threaded shaft 68 and axially spaced therealong, is operable to alternately engage one of the clutches 64 and 66 while simultaneously disengaging the other of the clutches.
  • one of the bevel gears 62 or 63 is driven by the shaft 59 while the other of the *bevel gears turns freely thereon, being disengaged therefrom.
  • Alternate engagement of the clutches -64 and 66 to drive alternately the bevel gears ⁇ 62 and 63, respectively, will rotate the threaded shaft 68 alternately in opposed directions of rotation.
  • a limit switch actuating disc 74 with an internally threaded central opening is mounted on the threaded shaft 68 to ride axially therealong as the shaft is rotated.
  • the limit switch actuating disc will traverse axially along the threaded shaft 68 between the limit switches 72 and 73.
  • the switch functions to alter the condition of engagement of the clutches 64 and 66, thereby reversing the direction of rotation of the threaded shaft 68 and commencing axial movement of the disc 74 back toward the other limit switch.
  • the axial positions of the limit switches 72 and 73 may be made adjustable to afford a means of controlling the inner and outer diameters of a coil to -be laid.
  • the distributing apparatus will function to alternate the rotation of the ier tube 12 cyclically between a condition of acceleration and a condition of deceleration.
  • the input shaft 32 of the variable speed transmission 30 will be rotated at constant speed by the rolling mill.
  • the control shaft 34 is rotated alternately in opposed directions. Note that the direction of rotation of the control shaft 34 will affect only the speed, and not the direction, of rotation of the output shaft 33.
  • the auxiliary variable speed transmission 50 is operated to give a xed speed ratio between the input and output shafts thereof, the speed ratio between the output shaft 33 and the control shaft 34 will remain constant.
  • the output shaft ⁇ will be rotated alternately at continuously increasing speed and at continuously decreasing speed as the limit switch actuating disc 74 travels back and forth between the limit switches 72 and 73 and the control shaft 34 is rotated at continuously varying speed in alternating directions. Since the Ibelt 23 for rotating the flier tube 12 is driven from the output shaft 33 bythe aforementioned iirst power train, the angular velocity of the flier tube rotation will vary with the speed of rotation of the output shaft 33.
  • the curve of angular velocity versus time produced by the apparatus provides only a very rough approximation of the desired solid line curve of FIG. 5.
  • the auxiliary variable speed transmission 50 is of any conventional type, for example, a type similar to that of the transmission 30, the output speed of which is regulatable by rotation of a control shaft 78.
  • a dn've for the control shaft 78 is taken directly from the threaded shaft 68 through pulleys 79 and 81, connected by a belt 82, and a flexible shaft 83 driven by the pulley 82.
  • control shaft 78 is operable in similar manner to the control shaft 34 and is rotated at a speed proportional to that of the threaded shaft 68 to accelerate and decelerate alternately the shaft 52, which constitutes the output shaft of the auxiliary variable speed transmission 50.
  • the addition of an accelerationdeceleration operation in the power train between the output shaft and the control shaft of the principal variable speed transmission 30 conforms the performance capability of the distributing apparatus quite closely to the theoretical solid line curve of FIG. 5.
  • the desired curve may be obtained through a proper selection of drive ratios in the various drive trains between the output shaft 33 and the control shaft 34.
  • variable speed transmissions 30 and 51 may be of other than the type depicted.
  • known variable speed transmissions which are suitable may be included a device wherein parallel, oppositely facing cones are interconnected by an endless belt, adjustable along parallel surfaces of the cones.
  • FIG. 2 a mounting arrangement for the receiving platform or table 16 is shown. This arrangement is designed to maintain constant the vertical distance between an exit point 86 on the flier tube 12 through which the strand 11 is continuously advanced axially and the top layer 87 of convolutions of strand being distributed in the receiving drum 14. By maintaining this vertical distance constant, a uniform laying pattern is preserved for every layer of strand distributed.
  • One end of the lever 89 is joined pivotally by a pin 92 to the receiving platform, while one end of the lever 88, preferably having a supporting roller (not shown) mounted thereon, is transversely movable along a trackway on a bottom surface of the receiving table.
  • the opposite ends of the levers 88 and 89 are, respectively, pinned to and movable transversely on, a supporting base 93.
  • a cam follower 96 resists the tendency of the lever 88 to so pivot by cooperating with the surface of a cam 97 to bear against the lever.
  • a uid cylinder assembly 98 maintains the follower 96 against the lever 88 through a piston rod 99.
  • a valve 101, controlled by a solenoid 201, and a manually controlled valve 100 c0- operate to adjustably regulate the position of the piston rod 99 by selective exhausting of fluid from the fluid cylinder 98 to control the lowering of the receiving table 16.
  • a conventional pneumatic vibrator 102 vibrates the receiving tub or drum 14 continuously on the platform 16.
  • Springs 103 mount the drum on the platform to permit such vibrating. Undesired buildup of one strand convolution on another adjacent an unlled gap is prevented by the vibration causing the upper convolution to fall olf of the lower convolution and into the gap.
  • FIG. 5 showing a control circuit for the apparatus. It is assumed, initially, that a layer 87 (FIG. 2) of outwardly spiraling strand convolutions has just been laid, that the direction of rotation of the threaded shaft 68 (FIG. 1) has just been reversed to begin the disc 74 moving away from the limit switch 73 and toward the limit switch 72, and that the receiving platform or table 16 has just been moved downwardly by a distance equal to the thickness of the strand 11.
  • the clutch 64 is now engaged to drive the bevel gear 62 from the continuously rotated shaft 59, thereby driving the 'bevel gear 67 to rotate the threaded shaft 68 so as to move the disc 74 toward the limit switch 72.
  • the solenoid 264 (FIG. 3) for engaging the clutch 64 is presently coupled across a source of power through a normally closed contact 107-3 of a relay 107, presently not energized.
  • the initial movement of the disc 74 away from the limit switch 73 has returned a contact 73-1 thereof to a normal closed condition and a contact 73-2 thereof to a normal open position, as shown in FIG. 5.
  • the control shaft 34 of the principal variable speed transmission 30 and the control shaft 78 of the auxiliary variable speed transmission 50 are rotated from the pulleys 69 and 79, respectively, on the threaded shaft.
  • the ends of the levers 304 and 307 provided with the riders 309 are spaced apart along the control shaft 34 by a distance greater than the spacing between the pins 306 and 308.
  • the halves of V-belt pulley 301 are, therefore, spaced axially apart from each other by a greater distance than that between the halves of V-belt pulley 302.
  • the effective diameter of the driven pulley 302, thus, is greater than that of the drive pulley 301 and the angular velocity of the output shaft 33 is less than that of the input shaft 32.
  • the threaded shaft 68 and the control shaft 34 rotate in the same direction, as may be seen in FIG. l. Therefore, the rotation of the threaded shaft 68 which moves the disc 74 toward the limit switch 72 is accomplished by a rotation of the control shaft 34 which moves the riders 309 t0- ward one another.
  • the levers 304 and 307 pivot to increase the effective diameter of the drive pulley 301 and t0 decrease the eifective diameter of the driven pulley 302 as the control shaft continues to rotate. Therefore, the angular velocity off the output shaft 33 begins to increase.
  • the rotation of the output shaft 33 at increasing angular velocity continues.
  • the continuous increase in angular velocity or acceleration of the shaft 33 is fed back continuously through the power train, including the auxiliary variable speed transmission 50, to rotate the control shaft 34.
  • the riders 309 are drawn together along the control shaft at an increasing rate, varying the effective diameters of pulleys 301 and 302 with increasing speed. This causes a continuously increasing angular acceleration to be imparted to output shaft 33.
  • the operation of the apparatus as thus far described, provides a good rst approximation to the desired solid line curve of FIG. 5.
  • the disc 74 advances axially along the threaded shaft 68 to a position whereat the limit switch 72 is engaged.
  • Normally open contacts 72-1 and 72-2 (FIG. 3) are closed through this engagement of limit switch 72.
  • the closing of contact 72-1 completes a circuit through the relay 107, the closed contact 73-1 and the contact 72-1.
  • the relay is energized, operating to close normally open contacts 107-1 and 107-2 and to open the normally closed contact 107-3.
  • the holding contact 107-1 maintains the relay 107 energized so long as the contact 73-1 of limit switch 73 remains closed.
  • the opening of the contact 107-3 deenergizes the solenoid 264 to disengage the clutch 64.
  • the closing of the contact 107-2 energizes the solenoid 266 to engage the clutch 66 and thereby connect the shaft 59 to the bevel gear 63, reversing the direction of rotation of the threaded shaft 68.
  • the closing of contact 72-2 by the limit switch 72 meanwhile, provides a current path to energize the solenoid 201.
  • the receiving platform control valve 101 (FIG. 4) is thereby operated to start exhausting fluid from the cylinder 98 to lower the receiving platform 16.
  • the exhausting of uid is terminated upon the reopening of the contact 72-2, deenergizing the solenoid 201.
  • the deenergization of the solenoid 201 occurs upon the disc 74 commencing its return movement away from the limit switch 72 and toward the limit switch 73.
  • the operation of the apparatus is so timed that the contact 72-2 will reopen to stop the downward movement of the receiving table 16 at a position vertically spaced from its previous position by the thickness of the strand 11.
  • the manual ow control valve 100 provides the necessary adjustment capability to so time the operation.
  • the angular velocity of the rotating ier tube 12 will begin to decrease, changing with time in moving to the left on the solid line curve of FIG. 5.
  • a new layer of out- Wardly spiraling convolutions of strand similar to the pattern of FIG. 4, will now be laid on the previous layer 87 at an identical vertical distance from the exit point 86 on the rotating ier tube 12. This will occur as the exit point orbits the axis of rotation of the hier tube.
  • the limit switch actuating disc 74 again engages the limit switch 73.
  • the contact 73-1 (FIG. 3) is opened, deenergizing the relay 107 to open the contacts 107-1 and 107-2 and close the contact 107-3.
  • the solenoid 264 is once again energized and the solenoid 2-66 is deenergized.
  • the direction of rotation of the threaded shaft 68 again reverses and the disc 74 starts traversing back toward the limit switch 72.
  • the contact 73-1 closes as the disc ceases engagement with limit switch 73.
  • the limit switch actuating disc 74 is now moving along the threaded shaft 68 toward the limit switch 72 and the angular velocity of the ier tube 12 is increasing continuously to Wind an additional layer of spiral convolutions in an inward direction. This is the condition of the apparatus initially described. The apparatus can now continue to function, repeating continuously the abovedescribed cycle of operations.
  • the strand 11 is advanced continuously at constant linear speed through the exit point 86 (FIG. 2) orbited continuously about the axis of the flier tube 12 at a xed radial distance from the axis.
  • the angular velocity and angular acceleration of the orbiting ier are both varied continuously in the same direction of change by operation of the speed regulating apparatus 26 to lay spiral convolutions of strand on a receiver 13.
  • the time rate of change of orbital angular acceleration is also varied, through use of the auxiliary variable speed transmission 50, so as to lay the spiral convolutions in a desired compact pattern.
  • the direction of change of these variables is reversed alternately through alternated operation of the clutches 64 and 66 to provide for the distribution of alternately inwardly spiraling and outwardly spiraling layers of convolutions.
  • the exit point 86 and the receiver 13 are moved relatively apart vertically by a distance equal to the thickness of the strand 11 upon each such reversal, in order to preserve the desired spiral pattern in successive layers of distributed strand.
  • rotatable distributor means having an exit point for receiving the advancing strand and directing the strand through the exit point and toward the receiver;
  • An apparatus for distributing strand as set forth in claim 1, rwherein said speed regulating means comprises:
  • a receiver which comprises:
  • distributor means responsive to reversal of the direction of continuous variation in distributor means angular velocity for moving vertically the receiving and supporting means and the distributing means relatively apart by an additional vertical distance equal to the thickness of the strand.
  • variable speed drive means having a rotating output shaft connected to the distributor means for rotating the distributor means; control means operable on said drive means for continuously varying the angular velocity and the angular acceleration of the rotating output shaft;
  • reversible operating means responsive to rotation of the output shaft for continuously operating the control means in a first direction to continuously increase the output shaft angular velocity with increasing angular acceleration and in a second direction to continuously decrease the output shaft angular ve locity with decreasing angular deceleration;
  • said reversing means includes:
  • said vertical moving means includes:
  • reversible auxiliary variable speed drive means re sponsive to operation of the cyclical reversing means for continuously varying the rate of operation of the control means with time.
  • a iirst variable speed device having an output shaft
  • rotating means for operating said -first variable speed device to rotate said shaft with a continually changing angular velocity
  • a'second variable speed device coupled to said output shaft for operating said rotating means at a continually changing angular velocity
  • rotating distributor means having an exit point orbited at a xed radius about an axis of rotation for directing the advancing strand through the'orbiting exit point and toward the receiving means;
  • An apparatus for distributing an advancing strand into compact layers of spiral convolutions on a platform which comprises:
  • strand receiving and distributing means mounted for rotation about an axis and having an exit point fixed radially Iwith respect to said axis for directing the strand through said exit point and onto the platform;
  • variable speed transmission means for rotating the distributing means about; said axis at varying angular velocity to orbit said exit point about the axis and lay the strand in spiral convolutions'on the platform;
  • a method of forming a strand continuously advancing at constant linear speed into a compact layer of spirally convoluted strand on a horizontal receiver which comprises the steps of:
  • a method of forming a compact layer of spirally convoluted strand including the step of:
  • a method of distributing a moving strand continuously advancing at a constant speed into a plurality of layers of spiral convolutions on a horizontal receiver cornprising the steps of:
  • a method of distributing a moving strand including the steps of:
  • variable speed transmission means cooperable with said variable speed transmission means for rotating said distributing means at a time-varying rate of change of angular acceleration.
  • a method of distributing a continuously advancing strand onto a receiver comprising the steps of:

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Winding, Rewinding, Material Storage Devices (AREA)
  • Gear Transmission (AREA)
  • Wire Processing (AREA)
US658185A 1967-08-03 1967-08-03 Strand distributing and receiving apparatus and method Expired - Lifetime US3445077A (en)

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US3785587A (en) * 1971-06-24 1974-01-15 Republic Steel Corp Coil of continuous elongated material
US3822045A (en) * 1972-06-30 1974-07-02 Gen Electric Archimedes spiral wobble control
EP0053398A1 (en) * 1980-12-03 1982-06-09 Matsushita Electric Industrial Co., Ltd. Coil forming machine
EP0123839A1 (en) * 1983-04-27 1984-11-07 Allied Corporation Strand distributing apparatus and method
EP0448977A2 (de) * 1990-03-26 1991-10-02 British-American Tobacco (Germany) GmbH Verfahren und Vorrichtung zur Herstellung koaxialer Tabak- oder Filterstränge
EP0899214A1 (en) * 1997-08-25 1999-03-03 Servicios Condumex S.A. De C.V. Packing element for housing a wound electrical conductor
US6260781B1 (en) * 1998-12-16 2001-07-17 Lincoln Global, Inc. Method and apparatus for packing wire in a storage drum
US20050023401A1 (en) * 2003-07-30 2005-02-03 Lincoln Global, Inc., A Delaware Corporation Apparatus for packing wire in a storage container by use of reverse winding
EP1726375A1 (en) 2005-05-25 2006-11-29 Lincoln Global, Inc. Method for forming a large diameter weld wire by imparting a desired shape memory on said wire; A packaged supply of wire and a weld wire with such imparted shape memory form
CN102476759A (zh) * 2010-11-26 2012-05-30 深圳市沃尔核材股份有限公司 无张力排线器
CN102992089A (zh) * 2012-12-27 2013-03-27 苏州弘贸纺织有限公司 一种桶底升降型棉条桶

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FR2517462B1 (fr) * 1981-12-01 1986-10-03 France Transfo Sa Procede et dispositif de bobinage des enroulements inductifs equipant les appareils electriques, tels que les transformateurs
ATE214310T1 (de) * 1996-06-26 2002-03-15 Danieli Off Mecc Wickelverfahren und wickelvorrichtung
RU2192323C2 (ru) * 2000-05-24 2002-11-10 Некипелов Владимир Станиславович Способ формирования бунта катанки и устройство для его осуществления

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US1992430A (en) * 1933-05-12 1935-02-26 Edgar H Johnson Panning machine
US2849195A (en) * 1953-08-18 1958-08-26 Driscoll Wire Company Combination wire drawing and packaging device
US2857116A (en) * 1955-03-01 1958-10-21 Anaconda Wire & Cable Co Packaging of wire
US3270978A (en) * 1964-10-28 1966-09-06 Donald P Whitacre Wire-coiling machine with differential drive

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3785587A (en) * 1971-06-24 1974-01-15 Republic Steel Corp Coil of continuous elongated material
US3822045A (en) * 1972-06-30 1974-07-02 Gen Electric Archimedes spiral wobble control
EP0053398A1 (en) * 1980-12-03 1982-06-09 Matsushita Electric Industrial Co., Ltd. Coil forming machine
EP0123839A1 (en) * 1983-04-27 1984-11-07 Allied Corporation Strand distributing apparatus and method
EP0448977A2 (de) * 1990-03-26 1991-10-02 British-American Tobacco (Germany) GmbH Verfahren und Vorrichtung zur Herstellung koaxialer Tabak- oder Filterstränge
EP0448977A3 (en) * 1990-03-26 1993-01-13 B.A.T. Cigaretten-Fabriken Gmbh Method and device for the manufacture of a coaxial tobacco or filter rod and a coaxial tobacco or filter rod obtained by this method
EP0899214A1 (en) * 1997-08-25 1999-03-03 Servicios Condumex S.A. De C.V. Packing element for housing a wound electrical conductor
US6260781B1 (en) * 1998-12-16 2001-07-17 Lincoln Global, Inc. Method and apparatus for packing wire in a storage drum
US20050023401A1 (en) * 2003-07-30 2005-02-03 Lincoln Global, Inc., A Delaware Corporation Apparatus for packing wire in a storage container by use of reverse winding
US7004419B2 (en) * 2003-07-30 2006-02-28 Lincoln Global, Inc. Apparatus for packing wire in a storage container by use of reverse winding
EP1726375A1 (en) 2005-05-25 2006-11-29 Lincoln Global, Inc. Method for forming a large diameter weld wire by imparting a desired shape memory on said wire; A packaged supply of wire and a weld wire with such imparted shape memory form
US20060266794A1 (en) * 2005-05-25 2006-11-30 Lincoln Global, Inc. Method and apparatus for packaging wire in a wire container
CN102476759A (zh) * 2010-11-26 2012-05-30 深圳市沃尔核材股份有限公司 无张力排线器
CN102992089A (zh) * 2012-12-27 2013-03-27 苏州弘贸纺织有限公司 一种桶底升降型棉条桶

Also Published As

Publication number Publication date
NL6811006A (xx) 1969-02-05
DE1774644A1 (de) 1971-07-22
SE344733B (xx) 1972-05-02
FR1584089A (xx) 1969-12-12
BE718866A (xx) 1968-12-31
DE1774644B2 (de) 1972-09-21
GB1225420A (xx) 1971-03-17

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