US3041815A - Strand tensioning and metering apparatus - Google Patents

Strand tensioning and metering apparatus Download PDF

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Publication number
US3041815A
US3041815A US586864A US58686456A US3041815A US 3041815 A US3041815 A US 3041815A US 586864 A US586864 A US 586864A US 58686456 A US58686456 A US 58686456A US 3041815 A US3041815 A US 3041815A
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Prior art keywords
strand
torque
tension
capstan
wrap
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US586864A
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English (en)
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Norman E Klein
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Deering Milliken Research Corp
Milliken Research Corp
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Milliken Research Corp
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Priority to US586864A priority Critical patent/US3041815A/en
Priority to FR1175229D priority patent/FR1175229A/fr
Priority to GB40448/60A priority patent/GB864478A/en
Priority to GB15799/57D priority patent/GB864477A/en
Priority to CH350588D priority patent/CH350588A/fr
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    • D—TEXTILES; PAPER
    • D02—YARNS; MECHANICAL FINISHING OF YARNS OR ROPES; WARPING OR BEAMING
    • D02G—CRIMPING OR CURLING FIBRES, FILAMENTS, THREADS, OR YARNS; YARNS OR THREADS
    • D02G3/00—Yarns or threads, e.g. fancy yarns; Processes or apparatus for the production thereof, not otherwise provided for
    • D02G3/22—Yarns or threads characterised by constructional features, e.g. blending, filament/fibre
    • D02G3/26—Yarns or threads characterised by constructional features, e.g. blending, filament/fibre with characteristics dependent on the amount or direction of twist
    • D02G3/28—Doubled, plied, or cabled threads
    • D02G3/285—Doubled, plied, or cabled threads one yarn running over the feeding spool of another yarn

Definitions

  • This invention relates to ply action twisters, and more particularly to new and improved equalizer strand tension control arrangements for such apparatus.
  • a separate strand of yarn is fed to each of these two capstans, each yarn from a separate source of supply, with one of the strands being driven in ballooned relation about the source of supply for the other of the strands.
  • the ballooned yarn strand serves to impart rotation to the capstan unit, and by bringing the two strands together at a Y-ply point beyond the two canted capstans and along the axis of rotation of the idler gear a highly advantageous plying action will take place, thereby forming a two ply cord which is continually pulled away from the ply point by a suitable means.
  • These capstans serve very effectively to meter the yarn fiow of the two strands each at the same rate to the plying point and under wide variations of tension.
  • the tension in the two strands being plied be approximately equalized, particularly in the case of resilient or elastic material such as nylon, in order to avoid the formation of a yarn or cord which has unbalanced twist or corkscrew configuration, wherein tensile strength is impaired.
  • a further object is to provide an improved metering capstan array having an inner strand constant tension feedback control.
  • Still a further object of this invention is to provide an improved ply action metering capstan array having an inner strand dynamic feedback control which is speed responsive.
  • Another object of the invention is to provide an improved ply action apparatus having a feed back tension control for each of the outer ballooned strand and the inner strand.
  • a further object is to provide an improved ply action apparatus having a dynamic feed back control for each of the outer ballooning strand and the inner strand, both tension controls being responsive to the rate of rotation of the ballooned strand about the ply axis, whereby differential strand tension will be held to a minimum during normal running operation and during starting and stopping of the apparatus.
  • a still further object of the invention is to provide an improved ply action apparatus of the type wherein a false twist is inserted in the strands during a portion of the pre-plying operation and is taken out of the strand during plying thereof, which is so arranged as to permit the inner strand to be maintained under low tension at the point of twist insertion while being maintained under a torque-controlled higher tension as it proceeds thereafter to the ply point.
  • Still a further object of the invention is to provide an improved strand tension device particularly adaptable to ply action apparatus and employing a torque-brakecontrolled rotatable yarn engaging member and a separately rotatable yarn guide for maintaining tension on e a strand, the member and guide being each rotatable about a common axis.
  • a still further object is to provide an improved strand tension device, particularly adapted to ply action apparatus, in which two members are rotatable, one by direct action of one of two strands being plied and the other by intercoupling the two members through the second strand, with the second member having a controlled braking torque exerted thereon to thereby control the tension of the second strand.
  • FIGURE 1 illustrates schematically the general arrangement of a ply action apparatus incorporating the invention
  • FIGURE 2 is a view in partial section of a metering and tensioning capstan arrangement according to the in vention and as illustrated generally in FIGURE 1;
  • FIGURE 3 is a fragmentary plan view of the arrangement of FIGURE 1, further illustrating the capstan arrangement;
  • FIGURE 4 is a plan View of the face magnet of FIG- URE 3;
  • FIGURE 5 is a partial diametral section view of a modified capstan arrangement according to the invention.
  • FIGURES 6 and 7 are section views taken on lines 66 and 77 of FIGURE
  • FIGURE 8 is a perspective view of one of the gears of the embodiment of FIGURE 5;
  • FIGURE 9 is a fragmentary sectional view of a further capstan brake modification
  • FIGURE 10 is a partial sectional view of still another modification according to one aspect of the invention.
  • FIGURES 11 and 12 are perspective and diametral section views of the cap end portion of the preferred embodiment of the wrap-around tensioning capstan;
  • FIGURE 13 is a perspective view of the outer end portion of a modified wrap-around tensioning capstan
  • FIGURE 14 is a section view taken along line 14-14 of FIGURE 13;
  • FIGURES l5 and 16 are plan and fragmentary side elevation views of a modified embodiment according to another aspect.
  • a preferred embodiment of the invention takes the form of a pair of symmetrically arranged capstans having individual axis of rotation canted with respect to each other and with respect to a major axis of rotation common to both capstans, the capstans being arranged for meshed engagement with a common idler gear which is in turn rotatably mounted for free rotation about said major axis.
  • Strands being plied are fed to a ply point in substantially synchronously metered relation by passing the strands in tractive engagement each with a separate one of the two metering capstans of an equalizer or metering capstan array.
  • the outer ballooning strand first passes through an additive pre-tensioning device, then through a hollow spindle and in variable wraparound engagement with a wrap-around step dynamic balloon shape and tension control, after which it passes in a balloon about the supply package for the second or inner strand, and thence through a coupling or driving guide on the equalizer or meter-ing capstan array and in tractive engagement with one of the two metering capstans, from which it passes to the inverted Y-ply point.
  • the inner strand proceeds from its supply package upwardly through a pre-tensioning arrangement (preferably of the pad or pinch-tensioning type) then through an axial bore in a rotatable wrap-around tension capstan (which functions on a torque control principle) concentrio with the plying axis, passing thence about and in variable wrap-around engagement with the peripheral surface of the Wrap-around capstan, then in tractive engagement with the other of the two metering capstans, from which it then progresses to the inverted Y-ply point.
  • a pre-tensioning arrangement preferably of the pad or pinch-tensioning type
  • a rotatable wrap-around tension capstan which functions on a torque control principle
  • the rotatable wrap-around tension capstan is braked by suitable means (which in the preferred embodiment operates on a magnetic eddy current principle), causing the tension in the inner strand as it passes to the metering capstan to be controlled by the degree of wrap-around about the peripheral surface of said Wrap-around capstan; the degree of Wrap-around being in turn a function of the braking torque exerted on the wrap-around capstan by the magnetic brake and the difierence in the input tension of the inner strand as it passes thereto and the required inner strand output tension to yield a torque on the capstan of equal and opposite magnitude to the brake torque therein.
  • the braking action (and thus the strand output tension) is dependent upon the speed of rotation of the capstan array, and the tension on the inner strandis dynamically controlled similarly to the outer ballooned strand, matching the action of the Wrap-around step dynamic tension and balloon shape control since this outer strand is governed by a similar speed-tension response characteristic.
  • the net result is an improved ply action apparatus including substantially balanced dynamic tensioning means for both the inner and outer strands, with resultant minimizing of differential tensions in the two strands prior to their being plied.
  • a further advantage resides in the fact that the inner strand tension may be maintained at a low value at the point of twist insertion (with resulant minimizing of broken ends in the inner strand) while controllably regulating the tension between this twist point and the ply point at such higher tension value as may be desired for matching the tension of the outer strand.
  • a strand of a yarn A from an external source, such as supply package 11, is fed through adjustable tensioning assembly 13, thence axially through the center of hollow rotatably driven spindle shaft 15, through a radial opening in the shaft 15, then in wrap-around relation about wrap-around step tension balloon shape control 17 (of conventional construction), which forms a dynamic strand-tension responsive negative feed-back tension and balloon shape control device, such as shown for instance in the Klein and Wright application Serial No.
  • Strand B is fed from an internal source of yarn disposed within the thus formed balloon (for example, from a yarn package 21 mounted within the cylindrical housing 19, which package and housing are restrained against rotation as by an off center Weight 22, as shown, or by magnetic action, etc.), through adjustable pre-tensioning assembly 23 (in the instant example a plurality of disctype tensioners 23a mounted in spaced apart relation on a shock-mounted plate 23b) and thence about a guide roller 24 and through an axial bore in an axially disposed torque wrap-around capstan 26 in the capstan array 49, thence in sliding frictional wrap-around relation about the end of the capstan 26, then in tractive wrap-around relation about the other rotatable capstan 79b of the array 40, and thereupon proceeding to the ply point of the two strands.
  • adjustable pre-tensioning assembly 23 in the instant example a plurality of disctype tensioners 23a mounted in spaced apart relation on a shock-mounted plate 23b
  • adjustable pre-tensioning assembly 23 in the instant example a plurality of
  • the plied yarn or cord AB is fed from the ply point by a constant speed driven feed roll arrangement 25, and thence on to a take-up bobbin 27 driven in any suitable manner, as by surface contact roll 29.
  • the spindle shaft 1'5, feed roll arrangement 25 and surface drive roll 29 may be synchronously driven from either common or independent sources of power, as described and illustrated in the above mentioned co-pending application of Klein and Wright, and is, therefore, not shown herein.
  • Capstan array 49 is mounted on a supporting bracket 32 suitably secured at its base end 34 as by screws 35 to the upper end of cylindrical housing 19, and having formed at its upper end an adjustable internally threaded split clamping sleeve 36.
  • Capstan array 49 comprises a housing 42, the lower end 44 of which is threaded for complementary engagement with threaded sleeve 36.
  • the housing 42 is securely held in threaded engagement with the clamping sleeve 36 as by a bolt 38 extending through a pair of ears 39 formed on the sleeve 36, as more clearly seen in FIGURES 2 and 3.
  • shouldered recesses in housing 42 Press fit into shouldered recesses in housing 42 are two low-friction bearings 46 and 48 (i.e. ball bearings or other suitable construction as may be desired) which support within the inner race thereof for free rotation therein a rotor shaft 56, the axis of rotation of which is aligned with the axis of rotation of spindle shaft 15 as illustrated in the instant embodiment.
  • the lower end recess in the housing 42 is internally threaded below the lower end of bearing 48, as indicated by the numeral 50, for the reception of a complementary threaded ferromagnetic field adjustment ring 52.
  • Field adjustment ring 52 has a plurality of radial air cooling holes 54 formed therein. The purpose of this ring 52 will be described in more detail as the desc.ption proceeds.
  • rotor shaft 56 The lower end of rotor shaft 56 is threaded and has a securing nut 58 secured thereto for preventing upward axial displace ment thereof. If desired, a set screw 59 may be employed to retain the nut 58 in secured relation on rotor shaft 56.
  • rotor shaft 56 is enlarged to form a head 60 having a pair of opposed upwardly and inwardly inclined faces 61a and 61b, adjacent each of which is supported one of the strand metering capstans 70a and 70b.
  • Each of capstans 70a and 70b is arranged for rotation about an axis perpendicular to the plane of its respective adjacent face 61a and 61b, and to this end stub shafts 62 are threadedly secured in a respective tapped bore in each of the faces 61a and 61b.
  • each of stub shafts 62 is a standoff collar 63 against one end of which is secured the inner race of a low friction bearing 64 held on the end of the stub shaft by a lock nut 66 threadedly secured on the free end of the shaft.
  • the outer race of each of the bearings 64 is press fitted into the bore of respective capstans 70a and 70b, whereby each capstan is thus adapted for free rotation about its respective stub shaft 62.
  • capstans 70a and 70b have a single sharp-angled groove formed therein as indicated at 72, in order to provide maximum tractive action between the yarn strands A, B and their respective capstans 70a and 70b; however, this traction arrangement for the capstans may be modified as may be desired to fit the needs of any particular instance of use.
  • Capstans 70a and 70b are coupled together for synchronous rotation about their respective canted axes through the medium of a rotatable idler face gear 80 in meshed relation with beveled gears 76 formed integral with, as illustrated, or connected to the adjacent end of each of the capstans 70a and 70b.
  • To this end face gear 80 has a central shouldered recess which is press fitted over the outer race of a bearing 82, the retention of which is assisted by a snap ring 84 releasably fitted Within a shallow groove in the inner peripheral wall of the recess.
  • Rotor shaft 56 has an axial bore running therethrough, in the upper end of which is formed a counterbored shouldered recess 92 for press fitted reception of the outer race of a low friction ball bearing 94.
  • the nut 58 at the lower end of rotor 56 has a skirt 96 formed thereon, the lower end of which skirt has a shouldered recess formed therein for press fitted reception of the outer race of another low friction ball bearing 98.
  • torque shaft 100 has formed thereon or suitably secured thereon (as by a press fit as illustrated), for rotation therewith, a yarn guiding and torque transmitting wrap-around capstan 104 having a spiral end groove 106 formed therein for the guiding of strand B, as will become more readily apparent hereinafter.
  • the groove 106 takes the form of a single spiral groove and connects with the' bore 102 in torque shaft 100 through an enlarged 01f center aperture 105.
  • the aperture 105 is so offset from the axis of axial capstan 26, including torque shaft 100 and capstan 104, as to form a yarn engaging surface such that the strand B passing therethrough will be substantially coaxial with the torque shaft 100. It will be apparent that this arrangement of the aperture 105 will not only serve to maintain the strand B in a dynamically balanced position as it proceeds through the torque shaft 100 and the center aperture 105 in the cap 104, but will also accomplish the highly advantageous function of substantially reducing, if not completely eliminating, strand contact with the inner surface of tube shaft as it passes therethrough. Dynamic balancing of end cap 104 may readily be accomplished in any suitable or desired manner, as by the forming of the off center aperture of suflicient size as to offset formation of groove 106, or by addition of balancing weight or the like, as may be desired.
  • the lower end of torque shaft 100 has secured thereto, as by a set screw 110, a metallic disc 108 which is preferably made of low magnetic reluctance material such as aluminum, etc.
  • a face magnet 112 Supported in concentric relation beneath metallic disc 108 is a face magnet 112 having a plurality of circumferentially spaced, alternately north, south poles 114.
  • Face magnet 112 may be sup ported in any suitable manner, as for example, by being secured through the medium of securing screws 118 to a support flange 116 which forms a part of support bracket 32.
  • support flange 116 may also serve to support guide roll 24 for axial guiding of the strand to torque shaft 100.
  • strand A passes through spindle shaft 15, and then in variable surface contact with wrap around step 17, after which it passes in balloon form through guide 20 and in tractive engagement with capstan 70a, from which it proceeds to the ply point.
  • the tension in this strand is preadjusted by adjustment of the adjustable static pre-tensioning array 13, in order to provide the desired balloon size range for the strand as it passes in balloon shape about the housing 19.
  • the tension in the strand A as it proceeds through the balloon portion of its path is self-maintained by the variable wrap-around of the strand on wrap-around step 17 by interacting negative feed-back response between the step 17 and the balloon strand.
  • the variation of wrap-around of the ballooning strand on wrap-around step 17 is a function of strand input and balloon tension, wind resistance to balloon movement and rate of rotation of the balloon, among other factors, and varies in such a manner by negative feed-back response as to tend to keep the tension constant in the strand A.
  • an increase or decrease in balloon tension causes a smaller or larger wrap angle on the step 17, and this effects a negative feed-back control response between the strand and the step 17 in that a decreased or increased tension multiple is thereby applied to the strand by the step 17 as a function of the change in wrap angle, and this in turn tends to restore the balloon tension and size in a negative direction toward the desired value.
  • This system of yarn tension control for strand A is quite advantageous as is well known in the art and serves to maintain a substantially constant tension in strand A during normal operation at one balloon velocity.
  • the control exerted by this wrap-around step system is a function of balloon rotational velocity, variations of balloon velocity such as may occur for example during starting and stopping of the apparatus cause corresponding variations in the balloon tension of strand A. It is, therefore, extremely desirable that any dynamic tension control for the inner strand B maintain a tension control which is a function of the rate of rotation of the balloon A in as closely a similar manner to the speed responsive tension control exerted by the wrap-around step 17 as is possible.
  • the axial wrap-around torque capstan 26 (including torque shaft 100, torque transmitting wrap-around cap 104, and disc 108, as described above), which serves in conjunction with face magnet 112 as a further dynamic strand-tension-responsive negative feed-back tension control device to maintain a normally constant output tension on the strand B as it proceeds from the cap 104 to the metering capstan 70b.
  • the torque capstan assembly 26 functions in a negative feed-back responsive manner to maintain a desired tension level in the strand B closely analogous to the function of variable wrap angle step 17 for the strand A.
  • strand B proceeds from guide roller 24 axially through axial bore 102 in torque shaft 160 through groove 106 and cap 104, and then in wraparound relation about the circumferential peripheral surface of cap 104, from which it passes through and in tractive rolling frictional engagement with metering capstan 70b, after which it proceeds to the ply point.
  • the entire capstan array 40 Upon rotation of the entire capstan array 40 through the action of balloon strand A as exerted on the capstan array through its engagement with coupling guide 20 and/or metering capstan 70a, the entire capstan array 40, in cluding the disc 108, will be rotated about its common or major axis, and drag torque will be exerted on torque transmitting wrap-around capstan 26 through the rotation of disc 108 in the magnetic field between face magnet 112 and field adjustment ring 52.
  • This disc 108 causes eddy currents to be set up therein proportional to the rate of cutting of the magnetic lines of force which in turn generate a magnetic field of proportional intensity which reacts with the field from magnets 114 to oppose the rotation of the disc 108, and thus the rotation of the entire torque capstan 26.
  • the extent of eddy currents generated in the disc 108, and thus the extent of braking action exerted on the torque capstan 26 by the magnet 112 is therefore a function of the rate of rotation of the disc 108.
  • the rate of rotation of disc 108 will be substantially the same as the rate of rotation of the balloon of strand A, and thus the drag or brake torque exerted on torque capstan 26 will be a function of the rate of rotation of the balloon of strand A.
  • the greater the speed of rotation of the balloon of strand A the greater will be the braking action exerted by magnet 112 on wrap-around torque capstan 26, and vice versa. It will, therefore, be apparent that due to this braking torque, torque capstan 26 will tend to rotate retrogressively relative to (i.e.
  • the braking action of magnet 112 on disc 108 is a function of the rate of rotation of disc 108 (and thus for all practical purposes the rate of rotation of the balloon of strand A).
  • the brake action thereon by magnet 112 is sub stantially constant, and for all practical purposes may be said to be actually constant.
  • the magnet 112 will exert a constant predetermined brake torque on disc 108 and the remaining portions of torque capstan 26, including torque wrap around cap 104, whereby the strand tension between torque wrap-around cap 104 and metering capstan 7017 will be maintained at a substantially constant predetermined tension value.
  • the brake torque exerted on disc 108 of the torque capstan 26 may readily be varied for any particular rate of rotation of the disc 103 relative to the magnet 112 by increasing or decreasing the flux density of the magnetic field passing through disc 188. In the instant embodiment, this is facilely accomplished through the medium of axially adjustable field adjustment ring 52, which is threadedly secured in the lower threaded recess of housing 42. By manually rotating the housing 42, including field adjustment ring 52 secured thereto, the axial position of the housing 42 and ring 52 will be varied, and thereby the spacing between ring 52 and the pole faces 114 of magnet 112 will be varied with corresponding inverse variation of the magnetic field density in the air gap between pole faces 114 and the ferro-magnctic ring 52.
  • the ring 52 serves as a low reluctance portion of the magnetic path between each of the adjacent north-south poles 114, and thus the variation of the air gap between the ring 52 and the poles 114 will correspondingly result in an inverse variation in the magnetic flux density in the air gap therebetween, in which air gap the disc 108 is positioned.
  • the field adjustment ring 52 has formed therein a plurality of radial openings 54 to permit the circulation of air thcrethrough in order to carry off a portion of the generated heat resulting from the eddy currents in disc 10%.
  • axial torque capstan 26 has been illustrated as an assembly of several separate parts, including disc 108, torque shaft and torque wrap-around cap 104, and such assembly is the most desirable from the standpoint of ease of construction and assembly, it will be apparent that all or a part of this assembly might, if desired, be made as an integral unit.
  • FIGURES 5-8 there is illustrated a modified embodiment according to the invention, which also incorporates a torque capstan assembly 226 having a torque brake which is a function of the rate of rotation of the balloon of strand A.
  • a mechanical slip clutch-brake arrangement is utilized to maintain a desired brake torque betwen the torque capstan assembly 226 and the rotor shaft 256.
  • This arrangement is similar in other respects to the arrangement of the first described embodiment, and will thus be described only in the differing details thereof.
  • the rotor shm 256 is mounted in bearings 246, 248 in a similar manner to the rotor shaft 56 of the previous embodiment, ad has secured thereto a retaining nut 258 having the lower ball bearing support for torque shaft 200 press fit into a recess in its lower end.
  • a gear 262 which is engaged in meshed relation with a secoid gear 264 disposed laterally thereof and :rotatably about an axis parallel to the axis of torque shaft 200.
  • the gear 264 has an axial tubular extension 265 which is press fit within the inner race of each of two spaced apart low friction ball bearings 268, 270 which in turn are press fit into upper and lower shouldered recesses in a lateral extension 244 of the capstan housing 242.
  • Slidably mounted within an axial bore extending through gear 264 and its extension 265 is an axially adjustable shaft 266 which supports a third gear 274 in concentric relation with gear 264, through the medium of a ball bearing 276 the inner race of which is press fit onto the lower end of shaft 266 and the outer race of which is press fit into a recess in the lower end of gear 274.
  • a retaining nut 278 serves to assure the retention of bearing 276 on shaft 266.
  • gear 274 The axial disposition of gear 274 relative to gear 264 is determined by the axial position of shaft 266, which position may readily be varied as desired through the medium of an adjustment nut 267 which engages the threaded upper end of shaft 266 and rides on the upper end of gear extension tube 265.
  • the gear 274 meshes with a gear 272 which is press fit onto the lower end of torque shaft 200.
  • the gear ratios of gears 262, 264, on the one hand and gears 272, 274 on the other, are preferably such that a low order differential (i.e. of the order of that provided by one or two teeth difference, or more if desired) exists therebetween.
  • the gears 264 and 274 are operatively coupled together through the medium of a plurality of friction blocks 284 of nylon or other suitable material.
  • Blocks 284, as illustrated are rectangular in cross section and are loosely fitted within a corresponding pluraltiy of openings 280 formed in symmetrical spaced apart relation in gear 264 and extending parallel to the axis thereof.
  • the openings 280 each have formed at their lower end a fulcrum lip 282.
  • annular groove or recess 288 which is radially aligned with the plurality of openings 280, and in which the lower ends of friction blocks 284 ride as guided by the depending separating segments 269 between slot openings 280 (see FIGURES 6-8).
  • each of the friction blocks 284 has a boss 286 formed at its lower end which serves, together with an annular retaining lip 290 which may be formed on the rim of groove 288, to prevent longitudinally upward movement of the blocks 284 out of groove 288.
  • the mass of the friction blocks 284 which lies below the fulcrum lip 282 may be varied as desired to create a desired mass unbalance of these blocks about the fulcrum points formed by their respective fulcrum lips 282.
  • the rotor shaft 256 will be rotated about its axis in a similar manner to that of rotor shaft 56 of the previous embodiment as through the rotational action of ballooning strand A.
  • Rotation of rotor shaft 256 causes corresponding rotation of gears 262 and 264.
  • R- tation of gear 264 in turn tends to effect rotation of gears 272 and 274, together with torque wrap-around capstan 226, through the medium of resulting centrifugal action of friction blocks 284 which frictionally engage the outer peripheral surface of the annular groove 288 in gear 274.
  • the torque transmitting action between rotor shaft 256 and torque wrap-around capstan 226 is thus a function of the dilferential centrifugal force exerted by the plurality of blocks 234 on the groove 288 of the gear 274, as well as being a function of the coefiicient of friction between the blocks 284 and the engaging surface of groove 288.
  • the differential centrifugal force exerted by blocks 284 on the peripheral surface of groove 288 is in turn a function of the vertical position of the friction blocks relative to their respective fulcrum points, and the speed of rotation of rotor shaft 256.
  • the torque transmitted from shaft 256 to torque wrap-around capstan 226 is a function of the speed of rotation of rotor shaft 256 and the balloon of strand A.
  • the friction blocks 284 will exert a substantially constant predetermined centrifugal clutch-brake action on the gear 274 to thereby exert a corresponding predetermined substantially constant (for constant rotative speed of the capstan array) torque on the torque wrap-around capstan 226.
  • the strand B proceeding from its wrap-around position on the periphery of torque wrap-around cap 204 exerts a counter-torque on cap 204, which is transmitted through torque shaft 200 to the gears 272, 274 and the brake-clutch arrangement between gear 274 and gear 264.
  • the strand B will build up a suliicient wraparound angle on the periphery of torque wrap-around cap 204 to create an output tension in strand B as it proceedsto the metering capstan 270b sufficient to counter-balance the torque transmitted to the cap 204 by the gear and clutch-brake system 262, 264, 284, 272, 274.
  • the effective centrifugal clutch-brake action may be selectively varied to produce a selected output tension in strand B for any particular rate of rotation of the balloon of strand A.
  • centrifugal clutch-brake action on torque wrap around capstan 226 for any particular setting of the shaft 266 will be a function of the speed of rotation of the balloon of strand A, the clutch-braking action being greater at high speeds than at low speeds due to the increased difierential centrifugal force exerted by the blocks 284.
  • capstan 226 through the clutch-brake system is similarly drag or brake torque in the sense of resisting the torque exerted by the strand B on the torque wrap-around capstan 226 which latter torque may 'be viewed as tending to rotate the capstan 226 relative to rotor shaft 256, irrespective of whether the gear ratios are so arranged that the torque capstan tends to lead or lag the rotor shaft.
  • This system is, therefore, also highly advantageous when used in conjunction with a wrap-around step tension balloon shape control such as that illustrated at 17 in FIGURE 1.
  • this second embodiment is in some ways more advantageous than the preceding embodiment in that there is less power consumed and less heating of the parts in the braking assembly.
  • FIGURE 9 there is also employed a friction clutch-brake arrangement which efiectively reduces the power required to maintain the desired brake torque on the torque shaft 300 of the torque wrap-around capstan.
  • the torque imparted to the torque shaft 3% by the friction clutch 'brake arrangement will be substantially constant for all operating speeds of the balloon strand A and of torque shaft 300.
  • the rotor shaft end nut 358 has gear teeth formed on the periphery of the lower end thereof which engage with an idler gear 362 of a differential idler gear system 360 rotatably mounted on a shaft 370 which is suitably supported eccentrically of the axis of the torque shaft 300.
  • Idler gear system 369 has a second gear 364 fixedly connected to or formed integral with gear 362; the differential ratio between the gears 362 and 364 or the idler gear system 360 being small (e.g. of the order of that provided by one or two teeth difference, or more if desired).
  • Gear 364 meshes with gear 366 which is loosely mounted on the torque shaft 390 for rotation thereon.
  • Torque shaft 300 has fixedly secured thereto in any suitable manner a friction disc 368 beneath the lower end of nut-gear 358 and in face-to-face relation with gear 366.
  • Gear 366 is adjustably held in thrust engagement with the friction disc 368 through the medium of a thrust spring 372, thrust bearing 373, and thrust nut 374, the latter of which is threadedly mounted on the lower end of torque shaft 300.
  • thrust spring 372, thrust bearing 373, and thrust nut 374 By axially adjusting the thrust nut 374 the thrust exerted by gear 366 on friction disc 368 may be varied as desired to effect the desired torque transmission between gear 366 an disc 368.
  • FIGURE 10 there is shown schematically a simplified arrangement wherein a pair of simple pigtail guides are substituted for the metering capstans. 456 is rotatably mounted on a suitable support 432 through the medium of one or more low friction bearings 448.
  • Torque capstan 426 is suitably rotatably mounted in low friction bearings 494 and 498 which are press fit in spaced apart relation in shouldered end recesses in the axial bore of rotor 456. Torque capstan 426 has an eddy current disc fixedly secured to its lower end, a portion of which is disposed in the air gap of one or more magnets 412. An axial bore 462 is formed in torque capstan 426 which suitably connects with a spiral groove 406 formed at or near the upper end of the torque capstan.
  • guides 476a and 47% (which may suitably be of the pigtail type for ease of thread-up, if desired) which serve to guide the strands A and B, respectively, to the ply point.
  • FIGURES 13 and 14 there is disclosed an alternate embodiment of the torque wrap-around cap.
  • the torque metering cap 104a has a symmetrical spiral groove 106a formed in its upper end in a substantially S-shape.
  • This groove 106a obviously might also be formed in a reverse S-shape, as might the groove 106 be reversed, if desired, in the event that the arrangement or rotational direction of the parts is such as to cause the wrap-around of strand B in the opposite direction to that for which the illustrated capstans are designed.
  • the groove may in some instances be radial, etc., or may take the form of a transverse port in the side of the Wrap-around cap and connecting the axial bore 102 of torque shaft with the wrap-around periphery of the wrap-around cap.
  • the center of groove 136a connects with the axial bore 195:: formed therein and which is arranged for alignment with the bore 102 of the torque shaft 100.
  • This cap 194:: has the advantage of ease of dynamic balance due to its symmetrical groove 106a; however, due to the bore 165a being axial rather than off center as in the embodiment of FIGURES 1, 10 and 11, etc., it will be apparent that this arrangement will not in itself guide the strand B through bore 105:: precisely coaxially since the surface of bore 16511 is necessarily displaced from the axis of cap 164a by a distance equal to the radius of the bore.
  • the bore 105 of slightly smaller diameter than the bore through the torque shaft 100 in order to more nearly center the strand, and particularly in order to guide the strand along a line out of contact with the interior of bore 192. It will be seen that in operation the strand B may be guided through either path of the double spiral groove 106a in the course of its passage from bore 105a to the circumferential periphery of the cap.
  • FIGURES 15 and 16 there is shown a further modification for increasing the eifective traction on the strand B (or both strands if desired) as it passes over its metering capstan, and which may suitably be employed with any of the embodiments except that of FIG- URE 10.
  • the strand metering capstan 5701) has formed thereon a pair of grooves 572k in lieu of the single groove disclosed in the preceding embodiments in order to provide an increased angle of tractive engagement between the strand B and the metering capstan 57Gb to insure against possibility of slippage thereon.
  • the strand guide finger plate 575 is fixedly mounted on the head upper end of rotor shaft 556, as through an Allen cap screw 576.
  • the finger plate 575 has an intermediate wide smooth strand guiding surface 577 formed thereon which serves to guide the strand as it proceeds from the periphery of cap 584 to the first or inner groove 5721;.
  • the strand guiding surface 577 tapers to a terminal yarn engaging finger 578 which lies above and between the two grooves 57%, and serves to guide the strand in intra groove cross-over after the strand has passed almost completely around the inner groove 572b and during its transfer to the second or outer groove on the metering capstan 57Gb. After passage around the second groove the strand B then proceeds in the usual manner to the ply point.
  • FIGURE 1 a fluid or air and paddle wheel assembly might be substituted for the magnet and disc arrangement; while in FIGURE 5 a similar or other viscous fluid brake might be substituted for the centrifugally operable mechanical friction brake.
  • FIGURE 5 a similar or other viscous fluid brake might be substituted for the centrifugally operable mechanical friction brake.
  • electromagnetic or hybrid electromagnetic-permanent magnet types of brakes might be utilized, if desired, in lieu of the permanent magnet type brakes illustrated, such being particularly useful in permitting adjustment of the inner strand tension through electromagnetic brake torque control during full operation of the apparatus.
  • Ply action apparatus for plying together two or more strands, comprising a rotatable strand guiding means for guiding each of the strands to a ply point, first dynamic strand-tension-responsive negative-feed-back tension control means for a first strand being plied, and second dynamic strand-tension-responsive negative-feed-back tension control means for a second strand being plied, each of said tension control means being substantially mutually independent of one another and being negative-feed-back responsive to the tension in its respectively tensioned strand to vary its tension compensating eifect on said respective strand in an amount inversely proportional to the tension in said respective strand.
  • each of said tension control means has a substantially similar tension control characteristic.
  • Ply action apparatus for plying together two or more strands, comprising a rotatable strand guiding means for guiding each of the strands to a ply point, first dynamic feed back tension control means for a first strand being plied, and second dynamic feed back tension control means for a second strand being plied, said second tension control means comprises a rotatable capstan, torque brake means operatively connected to said capstan, and means for guiding said second strand into sliding frictional variable wraparound engagement with said capstan, the wraparound angle being a function of the tension in said second strand and the braking torque exerted on said capstan by said torque brake means.
  • Ply action apparatus wherein means are provided for driving said first strand in ballooned relation about a portion of the path of said second strand, said first tension control means comprising a wraparound step, and means for rotating said wraparound step.
  • Ply action apparatus according to claim 1, further comprising strand metering means for metering each of the strands as it proceeds in its path during plying.
  • each of said tension control means having a tension control characteristic which is a function of the rotational velocity of said balloon.
  • Ply action apparatus for plying together two or more strands, comprising a rotatable strand guiding means for guiding each of the strands to a ply point, first dynamic feed back tension control means for a first strand being plied, and second dynamic feed back tension control means for a second strand being plied each of said tension control means being substantially mutually independent of one another and being responsive to the tension in its respectively tensioned strand to vary its tension compensating eflect on said respective strand, one of said tension control means including a centrifugally operable brake, a rotatable strand engaging member, and a step-down drive connection between said strand engaging member and said centrifugally operable brake.
  • Ply action apparatus for plying together two or more strands, comprising a rotatable strand guiding means for guiding each of the strands to a ply point, first dynamic feed back tension control means for a first strand being plied, and second dynamic feed back tension control means for a second strand being plied each of said tension control means being substantially mutually independent of one another and being responsive to the tension in its respectively tensioned strand to vary its tension compensating effect on said respective strand, one of said tension control means including a magnetic brake having a disc rotor and a stator, and a strand engaging member rotatable in synchronism with said rotor.
  • Ply action apparatus for plying together two or more strands, comprising a rotatable strand guiding means for guiding each of the strands to a ply point, first dynamic feed back tension control means for a first strand being plied, and second dynamic feed back tension control means for a second strand being plied each of said tension control means being substantially mutually independent of one another and being responsive to the tension in its respectively tensioned strand to vary its tension compensating effect on said respective strand, said second tension control means including a rotatable strand engaging capstan, and including a torque brake operatively connected to said capstan.
  • Ply action apparatus according to claim 11 wherein said capstan has an axial strand guiding bore therein and a transversely extending strand guiding surface formed thereon and disposed between said bore and the periphery of said capstan.
  • a strand tension device comprising a pair of members rotatably mounted in concentric relation about a common axis, said members being also rotatable relative to one another about said common axis, strand guide means on one of said members resistive to torque exerted by a strand in one direction about said axis, and strand guide means on the other of said members resistive to torque exerted thereon by a strand in the opposite direction about said axis.
  • a strand tension device comprising a pair of members rotatably mounted in concentric relation one within the other, said members being also rotatable relative to one another about their common axis, strand guide means on one of said members resistive to torque exerted by a strand in one direction about said axis, and strand guide means on the other of said members resistive to torque exerted thereon by a strand in the opposite direction about said axis.
  • a strand tension device according to claim 14, the inner of said concentric members having an axial strand guiding hole therein.
  • a strand tension device according to claim 15, wherein one of said guide means includes a transverse slot at one end of said inner member.
  • a strand tension device according to claim 16 wherein said slot has a spiral configuration.
  • a strand tension device wherein the inner of said concentric members extends axially beyond the outer of said members, said inner member having an axial strand guiding hole formed therein and extending therethrough at least partially in an axial direction.
  • a strand tension device wherein the extended end of said inner member forms a cylindrical yarn engaging step, said guide means on the outer of said members having a strand guiding surface disposed axially inwardly from the end of said cylindrical step so as to cause a strand fed from the extended end and about said guide means on said inner member to tend to be wrapped about said step upon relative rotation of said members.
  • a strand tension device according to claim 14 wherein there is provided brake means adapted to resist rotation of one of said members.
  • a strand tension device according to claim 14 wherein there is provided brake means operatively connected to one of said members and adapted to resist rotation thereof.
  • a strand tension device according to claim 21 wherein said brake means comprises a magnet coupled to the inner of said members through magnetic induction.
  • a strand tension device according to claim 22 wherein said brake is an eddy current magnetic brake.
  • a strand tension device according to claim 14 wherein there is provided brake means operatively connected to the inner of said members and adapted to resist rotation thereof, said brake means comprising a friction brake.
  • a strand tension device according to claim 24 wherein said friction brake forms an operative connection between said members.
  • a strand tension device according to claim 25 wherein said operative connection comprises a difierential gear ratio system and a friction clutch-brake operatively connecting said members.
  • a strand tension device according to claim 14 and including a centrifugally operable brake operatively connected to one of said members.
  • a strand tension device according to claim 14 wherein there is provided brake means operatively connected to the inner of said members and adapted to resist rotation thereof, said operative connection comprising a differential drive ratio system.
  • a strand tension device comprising a member rotatably mounted for continuous rotating movement about an axis, strand engaging means on the peripheral surface of said member, a portion of the said engaging surface of said strand engaging means extending in a direction transverse to said axis for guiding a strand and positively transmitting a torque from said strand to said member in a first rotative direction about said axis, torque drag means comprising a substantially constant torque brake adapted to impart a substantially constant drag torque to said member in a direction opposite to said strand-exerted torque, and means additional to said strand adapted to impart rotation to said member.
  • a strand tension device according to claim 29 wherein said constant torque brake is selectively adjustable.
  • a strand tension device according to claim 29 wherein said additional means comprises guide means separate from said member and adapted to guide said strand and a second strand in rotatively intercoupled relation about said axis.
  • a strand tension device comprising a member rotatably mounted for movement about an axis, strand engaging means on the peripheral surface of said member, a portion of the said engaging surface of said strand engaging means extending in a direction transverse to said axis for guiding a strand and positively transmitting a torque from said strand to said member in a first rotative direction about said axis, torque drag means comprising a substantially constant torque brake adapted to impart a substanially constant drag torque to said memher in a direction opposite to said strand-exerted torque, and means additional to said strand adapted to impart rotation to said member, said additional means comprises a second strand, and guide means separate from said member for each of said strands and intercoupling the rotative movement about said axis of said first mentioned strand with said second strand.
  • a strand tension device wherein said brake is a hysteresis magnet brake having a rotatable element and a normally stationary element, said rotatable element being rotatable in synchronism with said first mentioned member.
  • a strand tension device comprising a member rotatably mounted for movement about an axis, strand engaging means on the peripheral surface of said member, a portion of the said engaging surface of said strand engaging means extending in a direction transverse to said axis for guiding a strand and positively transmitting a torque from said strand to said member in a first rotative direction about said axis, torque drag means comprising a substantially constant torque brake adapted to impart a substantially constant drag torque to said member in a direction opposite to said strand-exerted torque, and means additional to said strand adapted to impart rotation to said member, said magnetic brake comprises two relatively movable component members including a magnet and a metallic disc member concentric with said axis, one of said component members of said brake being mounted for rotation with said first mentioned member.
  • a strand tension device comprising a member having an end peripheral surface and a radially outer peripheral surface and being mounted for rotation about an axis; rotation-resisting torque means arranged for operative connection to said member to apply a rotation resisting torque to said member; a substantially axially disposed strand guide; said member having a strand engaging means having a strand engaging torque transmitting surface transverse to said axis and operatively connected through said member to said rotation-resisting torque means, for guiding a strand between said axially disposed guide and the radially outer peripheral surface of said member; and strand guide means disposed in spaced-apart relation to said member and transversely spaced from said axis, said last named strand guide means being mounted for rotation about said axis.
  • a strand tension device comprises a rotatable capstan, and support means for said capstan, said support means being rotatable about said axis.
  • a strand tension device according to claim 36 wherein there is further provided a second capstan mounted on said support means for guiding a second strand, said capstans being adapted to rotate in synchronous relation about secondary axes separate from said first mentioned axis.
  • a strand tension device according to claim 37 wherein one of said capstans has a double annular groove formed thereon, and intra-groove guide means separate from said one capstan for guiding a strand from one to the other of said grooves.
  • a strand tension device according to claim 35 wherein said member has an axially extending hole formed therein, the bounding surfa.-e of said hole forming said axially disposed guide.
  • Ply action apparatus for plying together two or more strands, comprising a rotatable strand guiding means for guiding each of the strands to 2. ply point, first dynamic feed back tension control means for a first strand being plied, and second dynamic feed back tension control means for a second strand being plied each of said tension control means being substantially mutually independent of one another and being responsive to the tension in its respectively tensioned strand to vary its tension compensating efifect on said respective strand, one of said tension control means including a centrifugal brake having a rotor and a stator, and a strand engaging member rotatable in synchronism with said rotor.
  • Ply action apparatus according to claim 40 further comprising a step-down drive connection between said strand engaging member and said rotor.
  • Ply action apparatus for plying together two or more strands, comprising a rotatable strand guiding means for guiding each of the strands to a ply point, first dynamic feed back tension control means for a first strand being plied, and second dynamic feed back tension control means for a second strand being plied each of said tension control means being substantially mutually independent of one another and being responsive to the tension in its respectively tensioned strand to vary its tension compensating effect on said respective strand, one
  • tension control means including a magnetic brake having a rotor and a stator, and a strand engaging member rotatable in synchronisrn with said rotor.
  • Ply action apparatus for plying together two or more strands, comprising a rotatable strand guiding means for guiding each of the strands to a ply point, first dynamic feed back tension control means for a first strand being plied, and second dynamic feed back tension control means for a second strand being plied each of said tension control means being substantially mutually independent of one another and being responsive to the tension in its respectively tensioned strand to vary its tension compensating effect on said respective strand, one of said tension control means including a brake having a rotor and a stator, and a strand engaging member rotatable in synchronous with said rotor.
  • Ply action apparatus according to claim 43 further comprising a step-down drive connection between said strand engaging member and said rotor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Textile Engineering (AREA)
  • Tension Adjustment In Filamentary Materials (AREA)
  • Tyre Moulding (AREA)
  • Yarns And Mechanical Finishing Of Yarns Or Ropes (AREA)
  • Winding Filamentary Materials (AREA)
US586864A 1956-05-23 1956-05-23 Strand tensioning and metering apparatus Expired - Lifetime US3041815A (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US586864A US3041815A (en) 1956-05-23 1956-05-23 Strand tensioning and metering apparatus
FR1175229D FR1175229A (fr) 1956-05-23 1957-05-16 Dispositif pour régler l'avance et la tension des fils
GB40448/60A GB864478A (en) 1956-05-23 1957-05-17 Apparatus for plying strands together
GB15799/57D GB864477A (en) 1956-05-23 1957-05-17 Devices for controlling the tension in a strand of yarn
CH350588D CH350588A (fr) 1956-05-23 1957-05-23 Dispositif de câblage d'au moins deux fils

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US586864A US3041815A (en) 1956-05-23 1956-05-23 Strand tensioning and metering apparatus

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US3041815A true US3041815A (en) 1962-07-03

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US586864A Expired - Lifetime US3041815A (en) 1956-05-23 1956-05-23 Strand tensioning and metering apparatus

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US (1) US3041815A (fr)
CH (1) CH350588A (fr)
FR (1) FR1175229A (fr)
GB (2) GB864478A (fr)

Cited By (3)

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US3295304A (en) * 1964-09-09 1967-01-03 Apparatus for twisting and plying strands
US3388542A (en) * 1967-08-29 1968-06-18 Alfred W. Vibber Apparatus for and method of twisting and plying strands
US4894982A (en) * 1987-10-13 1990-01-23 Officine Meccaniche Riva S.R.L. Twisting machine particularly for twisted threads

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Publication number Priority date Publication date Assignee Title
FR2565261B1 (fr) * 1984-06-05 1987-05-15 Verdol Sa Procede pour la realisation de fils cables de grande regularite et dispositif pour sa mise en oeuvre
DE8806816U1 (de) * 1988-05-25 1989-09-21 Saurer-Allma Gmbh, 8960 Kempten Kabliermaschine
FR2632981B1 (fr) * 1988-06-21 1990-09-21 Icbt Lyon Machine de cablage de fils comportant un dispositif regulateur perfectionne
FR2632982B1 (fr) * 1988-06-21 1990-09-21 Icbt Lyon Machine de cablage de fils
FR2673956B1 (fr) * 1991-03-14 1993-05-28 Ic Bt Lyon Machine de cablage de fils comportant un ensemble regulateur de tension et de longueur perfectionne.

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US2689449A (en) * 1952-06-20 1954-09-21 Us Rubber Co Automatic balloon control
US2732680A (en) * 1953-03-12 1956-01-31 vibber
US2736160A (en) * 1953-06-16 1956-02-28 vibber
US2753679A (en) * 1951-08-31 1956-07-10 Schmoller Fritz Von Twisting device
US2869313A (en) * 1954-11-17 1959-01-20 Alfred W Vibber Method of and apparatus for plying strands

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BE523245A (fr) *
US2753679A (en) * 1951-08-31 1956-07-10 Schmoller Fritz Von Twisting device
US2689449A (en) * 1952-06-20 1954-09-21 Us Rubber Co Automatic balloon control
US2732680A (en) * 1953-03-12 1956-01-31 vibber
US2736160A (en) * 1953-06-16 1956-02-28 vibber
US2869313A (en) * 1954-11-17 1959-01-20 Alfred W Vibber Method of and apparatus for plying strands

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3295304A (en) * 1964-09-09 1967-01-03 Apparatus for twisting and plying strands
US3388542A (en) * 1967-08-29 1968-06-18 Alfred W. Vibber Apparatus for and method of twisting and plying strands
US4894982A (en) * 1987-10-13 1990-01-23 Officine Meccaniche Riva S.R.L. Twisting machine particularly for twisted threads

Also Published As

Publication number Publication date
GB864478A (en) 1961-04-06
FR1175229A (fr) 1959-03-23
CH350588A (fr) 1960-11-30
GB864477A (en) 1961-04-06

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