US3021664A - Apparatus for winding packages of roving - Google Patents

Apparatus for winding packages of roving Download PDF

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Publication number
US3021664A
US3021664A US850639A US85063959A US3021664A US 3021664 A US3021664 A US 3021664A US 850639 A US850639 A US 850639A US 85063959 A US85063959 A US 85063959A US 3021664 A US3021664 A US 3021664A
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United States
Prior art keywords
roving
builder
bobbin
cam
camming
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US850639A
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English (en)
Inventor
Gaston G Fornes
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Institute of Textile Technology
Original Assignee
Institute of Textile Technology
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Institute of Textile Technology filed Critical Institute of Textile Technology
Priority to US850639A priority Critical patent/US3021664A/en
Priority to GB33851/60A priority patent/GB921375A/en
Priority to CH1193260A priority patent/CH375637A/fr
Application granted granted Critical
Publication of US3021664A publication Critical patent/US3021664A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • D—TEXTILES; PAPER
    • D01—NATURAL OR MAN-MADE THREADS OR FIBRES; SPINNING
    • D01H—SPINNING OR TWISTING
    • D01H1/00—Spinning or twisting machines in which the product is wound-up continuously
    • D01H1/14—Details
    • D01H1/36—Package-shaping arrangements, e.g. building motions, e.g. control for the traversing stroke of ring rails; Stopping ring rails in a predetermined position
    • D01H1/365—Package-shaping arrangements, e.g. building motions, e.g. control for the traversing stroke of ring rails; Stopping ring rails in a predetermined position for flyer type
    • 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
    • B65H54/02—Winding and traversing material on to reels, bobbins, tubes, or like package cores or formers
    • B65H54/28—Traversing devices; Package-shaping arrangements
    • B65H54/32—Traversing devices; Package-shaping arrangements with thread guides reciprocating or oscillating with variable stroke
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2701/00—Handled material; Storage means
    • B65H2701/30—Handled filamentary material
    • B65H2701/31—Textiles threads or artificial strands of filaments
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18296—Cam and slide
    • Y10T74/18304—Axial cam
    • Y10T74/18312—Grooved
    • Y10T74/1832—Multiple screw

Definitions

  • This invention relates to the production of textile yarns and, more particularly, to apparatus for winding packages of roving and the like to produce a package having greater density and stability.
  • Packages of textile roving are formed by winding roving on bobbins in successive, closely-wound layers so that the fully wound bobbin is substantially cylindrical. It is the conventional practice to form the packages with straight, conical ends to insure the stability of the ends of the package, that is, to prevent the end coils of the layers of the wound bobbin from uncoiling due to lack of support from the underlying layers and becoming so tangled that the package must be discarded, or unwound with difficulty.
  • the conventional method of winding the package would result in a straight, conical taper at each end, for that method consists of shortening each succeeding layer by a constant amount.
  • This shape imposes very definite limitations on the amount of roving that can be wound on a bobbin because roving frames of given size are limited to winding roving packages to a certain maximum diameter and because there is a maximum cone angle-measured between the axis of the bobbin and an element of the cone-for which the roving is stable on the bobbin.
  • This maximum angle varies with the amount of tension with which the roving is wound on the bobbin; that is, there is a greater tendency for the tapered ends to break down as the winding tension is increased.
  • the taper angle must be held to a definite maximum for any given set of winding conditions.
  • a true straight taper is diificult to obtain because, as the winding progresses, the underlying layers are compressed by varying amounts which results in an irregularly concave or convex profile along the taper. This irregularity of profile is quite uncontrollable when bobbins are wound by conventional methods, and it necessitates a reduction of the taper angle or a reduction of the Winding tension if the roving is to remain stable on the bobbin.
  • each successive layer is decreased in length, not by uniform increments which results in a conventional, straight taper, but by progressively greater increments. Moreover, the increments by which the length of the initial layers are reduced are less than the mere merits conventionally used in forming straight tapers.
  • the intial large taper angle approximates a conventional, straight taper.
  • the winding tension in the latter half of the package particularly with the higher-than-normal winding tension which may be used with this new method, compresses the layers in the underlying layers of the package so that the approximately straight taper first produced becomes convex, and the overall final end profile approximates a definite geometric curve, such as a parabolic curve.
  • FIG. 1v shows roving 1 wound on a bobbin 2.
  • FIG. 1v shows roving 1 wound on a bobbin 2.
  • Apparatus has been devised for winding bobbins according to the new method, and its performs admirably.
  • the apparatus is, however, quite complex and substantial modification of conventional roving frames is required when the new apparatus is to be incorporated in it.
  • the present invention provides new and greatly simplified apparatus which may be incorporated in an otherwise conventional roving frame without substantial modification of any portion of the frame with the exception that the new combination of components is simply substituted for certain parts of an otherwise conventional frame.
  • a conventional roving frame comprises a plurality of drafting ro l-ls for attenuating each of a large number of ends of sliver so that the number of fibers in cross section is reduced.
  • the ends of roving are then passed to another part of the frame which puts a substantially uniform twist per unit length in the roving and then winds each end onto its own bobbin.
  • the winding operation consists in laying the end of a roving on a bobbin in successive layers, each layer consisting of a plurality of relatively closely-spaced coils wound around the bobbin.
  • the twisting and whirling are both accomplished by the diiferential rotation between the rotating bobbin and a so-oalled fiyer which rotates about the same axis as the bobbin.
  • the roving is led by the flyer to the bobbin and, in order that the coils be layed on the bobbin side by side and in successive layers, the roving frame is provided with means which cause the bobbin to reciprocate axially with respect to the fiyer.
  • a roving frame is also provided with means which reduce the amplitude of each successive reciprocation of the bobbin with respect to the flyer by a fixed and constant amount so that successive layers of roving wound on the bobbin have shorter lengths.
  • the apparatus by which the amplitude of reciprocation of the bobbin with respect to the fiyer is governed is called the builder, the construction of which is well known. Ordinarily, the builder is actuated by and in direct proportion to the motion of the tension gearing.
  • the conventional builder mechanism is replaced by a new combination of elements which comprises a cylindrical builder cam mounted on the roving frame and adapted to be rotatably driven about its longitudinal axis by the same or a similar control shaft such as that conventionally used to drive a builder screw.
  • This cylindrical cam member has on a first portion thereof a first helical camming surface and also has on another portion thereof a second helical camming surface. These first and second camming surfaces are oppositely directed, and each has continuously varying pitch.
  • a pair of builderjaws mounted adjacent the cam member and adapted to be reciprocally moved with respect to the cam member along paths parallel to the axis of the cam.
  • One of the builder jaws is provided with a cam follower which engages the first camming surface of the cam member, and the other builder jaw is provided with a cam follower which engages the second camming surface.
  • Each builder jaw is provided with a tumbler arm bearing surface of predetermined length and extending in the direction of reciprocation of the control shaft.
  • FIG. 1 is an elevation of a package of roving
  • FIG. 2 is a schematic illustration of a portion of a roving frame incorporating the present invention
  • FIG. 3 is a front elevation of a builder mechanism according to the invention.
  • FIG. 4 is a side elevation, pally broken away, of the mechanism shown in FIG. 3;
  • FIG. 5 is a diagram showing the mathematical relations between variables upon which the shape of the helical cam is based.
  • FIG. 6 is a diagrammatic illustration of a cam which may be employed in the construction of the mechanism shown in FIGS. 3 and 4.
  • FIG. 2 there is shown at 11 a portion of the bobbin rail of a roving frame which, as is well known, carries the bobbin-rotating mechanism.
  • the bobbin rail and all the mechanism mounted on it is driven up and down so that the bobbins on which roving is being wound are reciprocated axially with respect to the fiyers.
  • Flyers rotate with respectto the bobbins to put a uniform twist per unit of length in the roving and then wind it on the bobbin in successive layers, each of which layers consists of closely wound coils.
  • a conventional builder mechanism comprises a suitable bracket 12 mounted on the bobbin rail 11 which moves up and down as indicated in FIG. 2.
  • This bracket has a part 13 in which there are suitable vertical tracks or other guiding means for an upper jaw 14 and a lower jaw 15.
  • law 14 is provided with a vertical camming surface 16
  • jaw 15 is provided with a similar carnming surface 17.
  • a square builder screw shaft 18 is connected by a suitable universal joint 19 to a builder screw 20 which is provided with two oppositely threaded portions 21a and 215, the pitch of the threads being uniform throughout.
  • the upper jaw 14 is provided with internal threads which mate with the threaded portion 21a on the screw 29 as a nut on a bolt.
  • the lower jaw 15 is provided with internal threads which mate with the threaded portion 215.
  • a tumbler shaft 22 Adjacent and parallel to the shaft 18 there is a tumbler shaft 22 suitably mounted for rotation about its axis on a stationary part of the machine frame.
  • a so-called builder dog, indicated at 23, is fixed to the tumbler shaft and has oppositely extending arms 24 and 25 which are of sufiicient length in a radial direction so that the arm directed toward the builder shaft at any given time will engage one of the vertical camming surfaces 1601' 17.
  • the arm of the builder dog in engagement with the camming surfaces on the jaws will overrun the end of the camming surface so that there is no longer any resistance to the turning moment exerted on the tumbler shaft by the spring-loaded camming mechanism 26.
  • This mechanism then causes the tumbler shaft to turn enough to bring a toothed sector of the gear 27 into engagement with the gear 28, and the tumbler shaft is positively and rapidly driven through nearly a half revolution before the next toothless sector of the gear 27 comes under the gear 28.
  • the spring-loaded camming mechanism 26 is again in control of the tumbler shaft 22 and causes the shaft to complete the half revolution and bring the other arm of the builder dog to bear on the camming surfaces of the builder jaws.
  • the tumbler shaft cannot turn until the arm 24 overruns the end of the camming surface 16 on the upper jaw 14.
  • the mechanism 26 and the gears 27 and 2.8 will then cooperate to turn the tumbler shaft through 180 degrees so that the other arm 25 on the builder dog, which is axially displaced with respect to the arm 24, engages the cam surface 17 on the lower jaw 15.
  • This gear train known as the tension and taper gearing, comprises a worm gear 31 fixed to the tumbler shaft and spur gears 32, 33, 34, and 35.
  • the gear 32 in engagement with the worm 31 is fixed to a shaft which is common to the gear 33.
  • the latter gear engages the gear 34 which is fixed to a shaft common to the gear 35.
  • the gear 35 engages the teeth 36 on the underside of an elongated rack gear 37.
  • the rack gear is mounted on suitable guides so that it may be moved from side to side in FIG. 2.
  • a suitably mounted vertical shaft 38 carries the taper gear 40 and gear 41, the former of which engages the teeth 42 along the side of the rack gear 37 as seen in FIG. 2.
  • the other gear 41 engages a gear 43 fixed to the builder screw shaft 18.
  • the gear 43 and screw shaft 18 rotate together, but the screw shaft is of square crosssection and must be free to slide axially in a square axial aperture in the gear as the shaft oscillates with the bobbin rail 11.
  • a mechanism of this kind can only build packages having straight tapered ends, although the taper angle upward travel will continue until the arm 25 on the I builder dog overruns the lower end of the surface 17 on the lower jaw 15, whereupon the tumbler shaft will again be turned by the camming mechanism 26 and the gears 27 and 28.
  • the bobbin rail driving mechanism will be reversed and th bobbin rail will again be driven downwardly.
  • each successive layer of roving wound on the bobbin by a conventional roving frame is shortened by a predetermined and constant amount so that when the bobbin is fully wound the ends of the bobbin have a straight tapered shape.
  • this is accomplished by turning the builder shaft by a predetermined amount in the direction which causes the upper and lower jaws 14 and 15 to close upon each other, thus bringing the upper and lower ends of the carnming surfaces 16 and 17 closer together by successively equal amounts.
  • the upward and downward strokes of the bobbin rail are then shortened by a corresponding amount, for either the arm 24 will overrun the upper end of the surface 16 sooner than before or the arm 25 will overrun the lower end of the surface 17 sooner than before, thereby causing the direction of travel of the bobbin rail to be reversed.
  • the conventional way of turning the builder screw by the necessary amount is to drive the builder screw from the tumbler shaft through a gear train which causes the may be changed by changing the various gear ratios within the mechanism.
  • a cylindrical cam member 53 in the form of a sleeve adapted to fit over the central shaft 45 and of a length to be received between the upper and lower bearing blocks 46, 47 is fixed to the central shaft 45 for rotation therewith by any suitable means such as a pin or a set-screw 54.
  • This cylindrical cam member has two helical cams 55 and 56 machined into its outer surface. As best seen in FIG. 4, the helices 55 and 56 are oppositely directed, and the pitch of each helix varies in a definite pattern from turn to turn throughout its length from its outermost or initial end to its innermost or terminal end.
  • a pair of dog-arm camming members 57 and 58 are slidably mounted on the'bed plate 48so that theymay be reciprocally driven parallel to the axis of the cam 53.
  • the upper camming member 57 is located nearer the axis of the can member than is the lower camming member 58 so that the two members may pass side by side as they slide along their mounting grooves.
  • the lengths of these camming members 57, 58 are propertioned similarly to the lengths of the camming members 16 and 17 of a conventional builder apparatus such as that shown in PEG. 2 and their function is similarthat is, the upper arm of a builder dog bears on and slides along the surface of the upper camming member 57, and the lower arm of a builder dog slides along the camming surface of the lower camming member 58.
  • a single guide groove 60 is cut along the full length of the bed plate parallel to and to the left of the axis of the shaft 45 as seen in FIG. 3.
  • a guide member 61 having a groove-engaging portion along its lower edge, is fixed to and adapted to cooperate with the upper camming member 57 by means of a bridging portion 62 which is fixed between the upper edges of the guide member 61 and the camming member 57 adjacent their upper edges.
  • a guide member 63 is made to cooperate with lower camming n ember 58 by means of a bridging portion 64.
  • Each of the guide members 61 and 63 has a longitudinal groove-engaging portion along its lower edge.
  • cam followers may extend over the cam surface for a substantial distance more or less radially of the cam body, the cam followers should not contact the cam surface over any substantial distance in the direction along the length of the cam surface. if the cam follower is to track the cam accurately. Insome of the claims this condition is expressed as $11? gaging each of said camming surfaces along an element of substantially zero length along the length of said surface.
  • the pins are positively held in contact with the helical cams surfaces by means which permits ready removal of the pins when necessary.
  • These means comprise metal lic leaf springs 68 and 70, the former leaf spring being secured at one end to the guide member 61 by a screw 71 and the latter leaf spring being secured at one end to the guide member 63 by a screw '72.
  • Each of the pins 65 and 66 has a circumferential groove in a portion which protrudes beyond the bridging member.
  • the groove in pin 65 is shown at 73, and the groove in pin 66 is shown at 74.
  • the end of each leaf spring opposite the end fixed to the guide member is provided with a suitable slot into which the grooved portion of the pin may be received.
  • the spring 68 has a slot 75
  • the spring 76 has a slot 76.
  • the package end profile which the builder screw forms in this illustrative example of my invention is a mathe matically exact curve and is based on the following considerations.
  • the taper angle for a convex curve can be much larger than that for a straight-line profile or a concave profile at the beginning, or initial layers, of the wound package. There is a limit, however, to how large a taper angle can be successfully used, and this angle limits the selection of curves which will produce a convex ccntour and at the same time permit the building of a high-density package.
  • i-' 2 (length of first, layer minus length of last layer) B varies with the size of the bobbin and desired length of the last layer of roving.
  • the wooden bobbin of a 10" x 5" roving frame has 1.5 inch outside diameter. Accordingly,
  • Table H The values shown in Table H are used to generate a disc cam shown in FIG. 6. This is the controlling cam for the machine tool on which the helical builder screw is cut.
  • the base circle of this disc cam should be as large as possible, and for accurate results, it should have a base circle radius of not less than 3 inches.
  • the cam and its basic layout is shown in FIG. 6.
  • Table II includes only every tenth value of X and the corresponding values of x. It should be clearly understood, however, that the intermediate nine values between each of the values actually shown should be calculated and used in the layout of the cam. These values are accurately scribed on any suitable type of sheet metal, and the cam may be rought cut on a band saw.
  • the final shaping of the cam may be done by hand with a file, ribbon sander, or other type of fine cutting tool.
  • the disc or master cam just described is used in cutting the cylindrical helical groove in the builder screw.
  • I have used a conventional, high-precision ten-inch lathe to turn the cam body and a milling attachment to cut the grooves in the body.
  • the master cam is suitably mounted and rotated in coordination with the rotation of the cam body into which the helical grooves are out.
  • a small roller indicated at 75 in FIG. 6 is rigidly connected in any suitable way so that the motion of the cross-slide of the lathe in the direction parallel to the axis of the workpiece is accurately con trolled in accordance with the increase in diameter of the master cam.
  • the two grooves in the complete cam have identical variations in pitch from point to point along the axis of the cam, but they are of opposite hand and are oppositely directed along the axis of the cam body. Accordingly, the same disc cam may be used as a master to cut back grooves.
  • means for building packages of roving having convexly curved end profiles which means comprises a cylindrical builder cam body having in a first portion of the length thereof a first helical camming groove and hav- My invention ing in a second portion of the length thereof a second helical camming groove, the directions of said camming grooves being of opposite hand and each of said grooves having a major portion thereof which has continuously varying pitch, means for engaging the surface of each of said camming grooves along an element of substantially zero length along the length of said carnming groove, said engaging means being mounted for motion relativeto said cam body in a direction substantially parallel to the axis thereof, the builder screw driving mechanism of the frame being adapted to drive said builder cambody through equal successive increments and thereby displace said engaging means by successively different increments, and means responsive to the position of said engaging means along said camrning grooves for determining the lengths of sumessive layers wound on the

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  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Textile Engineering (AREA)
  • Spinning Or Twisting Of Yarns (AREA)
US850639A 1959-11-03 1959-11-03 Apparatus for winding packages of roving Expired - Lifetime US3021664A (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US850639A US3021664A (en) 1959-11-03 1959-11-03 Apparatus for winding packages of roving
GB33851/60A GB921375A (en) 1959-11-03 1960-10-03 Improvements in apparatus for winding packages of roving and the like
CH1193260A CH375637A (fr) 1959-11-03 1960-10-25 Cadre de mèche

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US850639A US3021664A (en) 1959-11-03 1959-11-03 Apparatus for winding packages of roving

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CH (1) CH375637A (fr)
GB (1) GB921375A (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3106056A (en) * 1960-04-29 1963-10-08 Deering Milliken Res Corp Method of forming a roving package
CN114348803A (zh) * 2022-02-21 2022-04-15 东莞市本末科技有限公司 一种电机理线、收线装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2003362A (en) * 1933-05-17 1935-06-04 Whitin Machine Works Roving frame builder motion
GB650921A (en) * 1948-11-26 1951-03-07 Arvid Janso Spinning regulators for textile ring spinning machines
US2652681A (en) * 1948-10-27 1953-09-22 Asea Ab Arrangement in spinning regulators
US2870597A (en) * 1957-05-09 1959-01-27 Saco Lowell Shops Roving frame builder mechanism

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2003362A (en) * 1933-05-17 1935-06-04 Whitin Machine Works Roving frame builder motion
US2652681A (en) * 1948-10-27 1953-09-22 Asea Ab Arrangement in spinning regulators
GB650921A (en) * 1948-11-26 1951-03-07 Arvid Janso Spinning regulators for textile ring spinning machines
US2870597A (en) * 1957-05-09 1959-01-27 Saco Lowell Shops Roving frame builder mechanism

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3106056A (en) * 1960-04-29 1963-10-08 Deering Milliken Res Corp Method of forming a roving package
CN114348803A (zh) * 2022-02-21 2022-04-15 东莞市本末科技有限公司 一种电机理线、收线装置

Also Published As

Publication number Publication date
GB921375A (en) 1963-03-20
CH375637A (fr) 1964-02-29

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