US3169362A

US3169362A - Roving package winding apparatus

Info

Publication number: US3169362A
Application number: US318476A
Authority: US
Inventors: Gaston G Fornes
Original assignee: INST OF TEXTILE TECHUOLOGY
Current assignee: INST OF TEXTILE TECHUOLOGY; INSTITUTE OF TEXTILE TECHUOLOGY
Priority date: 1961-04-25
Filing date: 1963-10-10
Publication date: 1965-02-16
Anticipated expiration: 1982-02-16
Also published as: GB973168A; CH396709A; CH417416A; GB973272A

Description

Feb. 16, 1965 s. G. FORNES ROVING PACKAGE WINDING APPARATUS 4 Sheets-$heet 1 Original Filed April 25. 1951 I u win FIG. 1

PRIOR ART FIG. 4

INVENTOR F a 6 4m n7 0 Feb. 16, 1965 e. e. FORNES ROVING PACKAGE WINDING APPARATUS 4 Sheets-Sheet 2 Original Filed April 25, 1961 m R Y r m gm 1 m A S Feb. 16, 1965 s. e. FORNES ROVING PACKAGE WINDING APFARATUS 4 Sheets-Sheet 3 Original Filed April 25, 1951 FIG Feb. 16, 1965 e. e. FORNES ROVING PACKAGE WINDING APPARATUS 4 Sheets-Sheet 4 7 Original Filed April 25, 1961 INVENTOR Gaston G. Fornes BY qzevs mdI United States Patent 0 3,159,362 RQVHNG PACKAGE WENDTNGAPPARATUS Gaston G. Fornes, (Iharlottesviile, Van, assignor to institute of Textile Technology, Cherlcttesville, Va, a corporation of Virginia @riginai application Apr. 25, 1961, Ser. No. iilSgiiii, now Patent No. 3,123,970, dated Mar. 10, 1964. Divided and this application (Itch R0, 1963, Ser. No. 318,476

5. laizns. (ill. 57-39) This application is a divisional of pending application Serial No. 105,401, filed April 25, 1961, now Patent No. 3,123,970, issued March l0, 1964, and assigned to the same assignee as the present application.

This invention relates to roving frames used in the production of textile yarns and, more particularly, to apparatus for winding packages of roving and the like to produce packages having greater density and stability.

Packages of textile roving are produced on roving frames. The packages are formed by winding roving on bobbins insuccessive, closely wound layers. The bobbins are made to reciprocate axially so that the coils of each layer are wound seriatim. The amplitude of reciprocation of the bobbins and, hence, the length of each layer of roving are decreased during winding to provide package stability. Thus, a completed package of roving is generally cylindrical with tapered ends so that the end coils of each roving layer are supported by underlying layers in the package. Without this support, i.e. taper, the end coils would unlay and tangle requiring that the package be unwound with difiiculty or even discarded.

As is well known, a conventional roving frame cornprises a plurality of drafting rolls for attenuating each of a large number of ends of silver so that the number of fibers in cross section is reduced. The ends of roving are then passed to another part of the frame called the fiyer 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 winding operations are both accomplished with diiferential rotation between the rotating bobbin and the flyer which rotates about the same axis as the bobbin.

In order that the coils be laid 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 flyer. As mentioned, for stability, a conventional roving frame is also provided with means which reduce by a fixed and constant amount the arnplitude of each successivereciprocation of the bobbin 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, motion of the so-called tension gearing.

Economic considerations dictate that as much roving yardage as is practical be wound on each bobbin. However, machines on which packages of roving are wound and later unwound are complex and expensive. Increasing package diameter is not practical for obtaining ingreases ice creased yardage per package because major modifications in these machines would be required.

In a copending application, Apparatus for Winding Packages of Roving and the Like, Serial No. 850,639, filed November 3, 1959, now Patent No. 3,021,664, I have discussed at length the mathematical relationships which must obtain between builder motion and the increasing diameter of roving layers being wound on the bobbins, to produce packages with tapered ends. For a detailed analysis, the reader is referred to that application.

Sufiice it to say, at this point, thatin the conventional roving frame, decreases in roving layer length are made directly proportional to increases in roving layer diameter. The result is, of course, production of packages of roving having straight-line or conically tapered ends.

Packages with conical tapered ends have been common for many years in the textile industry. However, recent studies have shown that packages with convexly curved end tapers have significant advantages. Details of these studies are also pointed out in the application referred to.

Experiments with the conical end type packages also indicate that mere increase in roving tension to provide packages of greater density and greater yardage per unit volume is not helpful. Aggravated end coil stability problems arise which necessitate decreasing the slope of the taper, thereby introducing an'offsetting reduction in total package volume.

But, wh'en the tapers are made convexly curved, packaged volume and hence package yardage are directly increased. Moreover, studies have shown that end'coil stability can be enhanced with convex end sections by increased roving tension during winding. As a result, packages can be producedwhich have greater density and stability as well as significantly increased yardage.

It follows that, to produce packages of roving with convexly curved end tapers, the increases in roving layer diameter must be related to increasingly disproportionate reduction in roving layer length. Mechanisms which provide this relation automatically in a roving frame have been recently devised. They work very well in producing roving packages with the advantageous convex end tapers. i

It is too early to know which type ofthese, mechanisms will become popular in the textile industry. However, it

stands to reason that any such mechanism which requires little time to produce and install; whichrequires small modification of existing frames; which is simple, has few moving parts, and for which maintenance and replacement do not requireextended roving frame stoppage will be preferred.

Satisfaction of all the above criteria in one machine probably represents a non attainable goal of perfection. However, I believe I have invented apparatus that will satisfy more of these criteria than have been satisfied by previous developments and which fall well within the practical limits of economics circumscribing the problem.

This invention provides apparatus which may be incorporate-d in existing roving frames to produce roving packages which have convex end tapers and increased 60 roving yardage. The apparatus provided can be readily incorporated in an otherwise conventional roving frame. Further, the mechanism provided comprises relatively simple components which can be easily fabricated and installed. Installation of the new apparatus requires only minor roving frame modifications.

, operator attention is required. 7 With this invention roving packages can be produced with significantly increased volume and yardage.

' of FIG. 3A;

According to the invention, a cam is used to relate the proportional increases in roving layer diameter to the required disproportionate reductions in roving layer length. The cam can be generally rounded or generally elongate. The important feature is that the cam provided has a camming dimension which changes in successively greater disproportionate amounts with respect to successive, equal increments, in a reference dimension.

Input means are provided for displacement of the cam in the direction or sense of the reference dimension upon completion of each layer of roving. This displacement is provided in successive, equal increments in proportion to successive increases in roving layer diameter. An output means is then arranged on the cam for actuation in response to corresponding increasingly disproportionate differences in the camming dimension. The latter changes are utilized directly for controlling the amplitude of the succeeding bobbin reciprocation.

The input and output means can be hydraulically or mechanically actuated. They can also be electrically actuated'in which case a cam as such is not used, but, an

arrangement similarly utilizing disproportionately related differences in dimensions is provided.

The apparatus of this invention is easily fabricated and installed. Only minor roving frame modifications are required, namely, those of substitution of parts. Apparatus embodying this invention may be provided for installation in most commercial'roving frames now in use. Frame operation is in the normal manner and no special Convexly-curved package ends can be provided with any desired curve or profile. They can be made sinusoidal,

V parabolic, cycloidal, etc., by simply substituting cams of different sizes and contours. Fine adjustments in package profile can beobtained by providing foraxial or off-set center adjustment of the cam, when installed in the roving frame. Furthermore, withthis invention in use, increased package density is attainable. Higher winding tensions can be used, which further increases package yardage, and the packages produced have improved stability.

These and other features of the invention will become evident upon reading the following, more detailed descriptions. For clarity, reference will be made'to the drawings in which:

FIG. 1 is a schematic illustration of the builder mechanism of a typical, conventional roving'frame;

FIG. 2 is an illustration of an embodiment'of the present invention, installed in the roving frame of FIG. 1, in which a flat shoe cam and'hydraulic means provide builder actuation;

FIG. 3 shows a second embodiment of the present invention in which a'flat shoe cam and mechanical means provide builder actuation; 1

FIG. 3A is an enlarged elevational view, partly broken away, of a part of the builder mechanism shown in FIG. 3; x

FIG. 3B is a sectional view taken along the line 3B3B FIG. 4 is an illustration of a third embodiment of my invention in which electro-mechanical means provide builder actuation; and

FIG S is an illustration of a fourth embodiment'of my invention in which a flat disc cam is installed to provide builder actuation. I

Inasmuch as the construction and operation of conthose skilled in the art to comprehend the details and features of a preferred embodiment of the apparatus I have invented.

In FIG. 1 there is shown at 11 a portion of the bobbin rail of a roving frame which, as is well known, carries the bobbins and the bobbin rotating mechanism. Also, as is well known, 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 flyers. The flyers rotate with respect to 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 consists of closely wound coils.

In order that the successive layers of roving wound on the bobbins are each shortened by a predetermined amount to form the appropriate tapered ends necessary for stability of the finished package of roving, a conventional mechanism known as a builder is used. To orient the reader and to facilitate understanding of the invention, and the manner in which embodiments of it are constructed and operated, there will first be given a description of part of a conventional roving frame.

A conventional builder mechanism. comprises a suitable bracket 12 mounted on the bobbin rail 11 which moves up and down. This bracket has a vertical portion 13 in which there are suitable tracks or other guiding means foran upper jaw 14 and a lower jaw 15. These jaws have substantially parallel, elongated vertical camming surfaces 16 and 17, respectively.

A shaft 18, called the builder screw, is provided with two oppositely threaded

portions

20 and 21. The upper jaw 14 is provided with internal threads which mate with the threaded portion 20 on the shaft 18 and the lower jaw 15 is provided with internal threads which mate with the threaded portion 21; Thus, because the threads on the portions '20 and 21 are oppositely directed, rotation of the shaft '18 in one direction or the other will either close or open the jaws upon each other to the extent permitted by the length of the threaded

portions

20 and 21.

Adjacent and parallel to the shaft 18 there is a tumbler shaft 22 suitably mounted for rotation about its axison a stationary part of the machine frame. A so-called from the bottom of FIG. 1, thereby insuring that one or I sectors.

ventional roving frames are well known it will not be necessary .to describe the entire machine to illustrate the operation of apparatus according to my invention. A typi- 'cal roving frame is fully described and illustrated in Hill:

Cotton Drawing, Combing and Fly Frame Processes, pub- Y lished by International Textbook Company of Scranton,

Pennsylvania. Accordingly, I will describehere only' so much of a typical roving frame .as isnecessary to enable the other of the arms on the builder dog will bear on the camming surfaces.

The tumbler shaft 22 is also positively, but intermittently, driven by the bevel gear 27 fixed to the upper end of the shaft 22 and the bevel gear 28 fixed to the main drive shaft 30 of the roving frame. As is well known 7 the gear 27 is 'a sector gear having teeth in two opposite sectors and' having no teeth in the other two opposite The gear 27 is so oriented on the tumbler shaft 22 that whenone or the other of the arms on the builder dog is rotated into position toengage the camming surfaces on thebuilder jaws, a toothless sector on the gear 27 is adjacent or under the gear 28 on the main drive shaft so that there is no driving torque transmitted to the tumbler shaft.

Now, as the bobbin rail 11 is driven upward or downward to the end of its stroke the arm of the builder dog in engagement with the cammingsurfaces 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 23 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. By this time, however, 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. Thus, to illustrate, if the bobbin rail is being driven downward while the arm 24 engages the camming surfaces, the tumbler shaft cannot turn until the arm 2 overruns the end of the camming surface 16 on the upper jaw 14. The mechanism 26 and the

gears

27 and 28 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.

Those who are acquainted with textile machinery know that the half revolutions of the tumbler shaft also actuate a mechanism which determines the direction in which the bobbin rail is driven. At the same time that the arm 24 overruns the end of the suriace i6 and the tumbler shaft 22 turns through a half revolution, the driving mechanism of the bobbin rail is reversed by conventional means so that the bobbin rail is then driven upward. The upward travel will continue until the arm 25 on the 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 2? and 28. The bobbin rail driving mechanism will be reversed and the bobbin rail will again be driven downwardly.

As is apparent, these changes in direction of the bobbin rail travel result in the bobbins on all the spindles of the roving frame being driven up and down with respect to their respective fiyers which are axially stationary. With each reversal of direction of travel of the bobbin rail a new layer of roving is wound on each of the bobbins.

As has been previously described 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. In con ventional roving frames this is accomplished by turning the builder shaft by a predetermined amount in the direction which causes the upper and lower jaws 1 and to close upon each other, thus bringing the upper and lower ends of the camming surfaces 16 and 17 closer together. Obviously, 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 and cause 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 builder screw to rotate through an angle which is in fixed and direct proportion to the angle through which the tumbler shaft rotates. This gear train, known collectively as the tension and taper gearing, comprises in order a worm gear 3i 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. This 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. 1.

Merely to orient the reader it is well to state here that this rack gear is also the driving element of a belt shipper mechanism for an endless belt which runs between the two cones or conical pulleys in the power train of the roving frame. The purposes of this power train are not directly relevant to this invention and need not be described in detail. However, the rack itself is also an element in the train of gears between the tumbler shaft and the builder screw.

A suitably mounted vertical shaft 33 carries the gears 49 and ii, the former of which engages the teeth 42 along the side of the rack 3'7 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 cross-section and free to slide axially in an aperture in gear 43 as the shaft oscillates with the bobbin rail 11.

A mechanism of this kind can build bobbins having only straight tapered ends. While the taper angle may be changed by changing the various gear ratios within the mechanism the machine is incapable of making other than straight tapers.

According to one embodiment of the present invention, the

builder members

12, 13, 14, 15, and 18 are removed and replaced by a new combination of elements shown in FIG. 2. Taper gear elements 33, d9, 41 and 43 may. also be removed as they are not required.

In FIG. 2, hydraulic and mechanical means are used in conjunction with a flat, shoe cam 44. This cam is elongate with camming surfaces 45 and 4-6 at its longitudinal edges. The cam is mounted in the roving frame with its longitudinal axis parallel to the rack 37 which drives the belt shipper. The cam is rigidly attached by any strong supporting means to, a roving frame structural member.

The camming surfaces on opposite edges of cam 44 are symmetrical with respect to the longitudinal cam axis. It is sufiicient, therefore, to describe one of the edge surfaces since the other is a mirror image of the first.

The upper camming surface .45 .is best related to a system of Cartesian coordinates. In this system, with the horizontal axis parallel to the cam longitudinal axis, a reference dimension will be defined as the length of the cam. The total length is, for this embodiment, approximately equivalent to the length of the belt-shipper cones. A cumming dimension will be defined as the width of the cam.

With the origin of the coordinate system at the left end of the cam, the direction of increasing length will be to the right, along the horizontal axis. Now, for a conical taper on the roving package ends, the function relating ordinates and abscissas of the camming surface would be linear. i.e., the function would define a straight line with a positive slope. But, for the convexly curved tapered ends, this function is not linear.

For the latter case, the camming dimension, the cam width, increases in successively increasing increments as the reference dimension increases in successively, equal increments. Specifically, in the reference coordinates, the slope of the camming surface is positive and is progressively increasing.

The builder jaws 49 and S0 of this embodiment are mounted for relative motion on the member 11 of the frame which reciprocates in synchronism with the bobbin spindles. They are supported on the bobbin rail Ill by a T bracket 51. Two compression springs 52 and '53 are also mounted on bracket 51 with their axes coincident and parallel to the direction of reciprocation. The builder jaws have flange portions positioned against the outer ends of these springs. The springs, being in compression, provide a biasing force exerted against the flanges which tends to move the jaws away from each other. These jaws also have elongate surfaces 16 and 17 similar to those in the conventional type of builder.

A hydraulic system is provided to drive the builder jaws together against the direction of the biasing forceof the 7 springs. The hydraulic system comprises cam follower pistons 54 and cylinders 55, and similar drive pistons 56 and cylinders 57. Interconnected between the several cylinders is a network of tubing 58. Some of the tubes I 59 in the network are, of course, flexible to allow for movement of follower cylinders 55 as well as reciprocation of the drive cylinders. Also, the tubes and cylinders are filled with an incompressible fluid such as, for exam ple, oil which is commonly used in such systems.

The cam follower cylinders 55 are rigidly mounted on a bracket 47 connected to rack 37 for simultaneous movement therewith. The following pistons 54 are arranged to project against the camming surfaces 45 and 46 of the shoe cam with their axes co-linear. The drive cylinders and pistons are mounted on the reciprocating frame member 11 on opposite sides of the builder jaws. The drive pistons 56 project against the jaw flanges for moving the jaws together.

Operation of the system depends upon relative motion between the cam surfaces and the followers. At the start the rack is moved to the left and the followers bear against the narrow part of the cam. As the rack 37 moves in successive equal steps to the right, the follower pistons 54 are driven apart in directions transverse the direction of the longitudinal axis of the cam. This action increases the pressure exerted on the fluid in the system which in turn causes the fluid to exert an increased force on the drive pistons 56. Thus, the flanges and builder jaws are driven together against the biasing forces of the spring.

The biasing force is also important in the reverse direction through the system. With this biasing force exerted through the flanges on the drive pistons, the follower pistons are held, at all times, against the camming surfaces of the shoe cam.

Since thefollower pistons are moved relative to their cylinders only in response to the successive changes in the width of the cam, as described above, the driving force exerted on the jaws 49and 50 provides for closing movement of the jaws upon each other by amounts which are in direct proportion to the increasing changes in cam width.

The remainder of the roving frame is of standard construction. The usual builder dog rotates 180 upon one arm thereof overrunning a camming surface on one of the jaws, which causes the direction of reciprocation of the bobbin spindles to be reversed.

The package end profile which the builder jaws cause to be formed in this invention is a mathematically exact curve based on considerations analogous to that which I havedescribed in the referenced application at pages 17 et seq.

The sine wave, ellipse, parabola, cycloid, involute and circle all have convex contours. The study of the properties of these curves to date indicates that the sine curve permits the use'of a reasonable angle at the beginning of the innermost layers, and it requires only a moderate changes in the slope as the package isbuilt. I will indicate herein, how my invention is adapted to produce an end taper fashioned after the sine curve to produce pack ages of roving with improved volume, density, stability and yardage.

adapted, by providing cams of different profiles, for production of convex end tapers after the fashion of the most advantageous geometric curve determined for particular roving packages. How this can be done will be readily apparent to those skilled in the art, after reading how it can be done for the sine curve case:

Along a mid-line of a suitable work piece, measure a distance equivalent to the total length of rack movement.

number of n equal increments.

For the 10" x 5" Saco-Lowell ES. 2 roving frame this distance can be thirty inches. The reference coordinate system is now defined with the x-axis along the measured mid-line with the origin at the left end of the measured distance. Thus x will vary between x =0 and x inches.

Next divide the distance (x x into a convenient For illustration I will use 11:10 but for accuracy in actual fabrication a higher number such as n: 100 should be used. Arbitrarily assigning unity value to x =x tabulate normalized values of x from x to x 1. Thus x fl, x =.1, x =.2, x =.3, and so on to x =l.

Then tabulate corresponding angular values y from y to 3 from the relation of y=arc sin x. Thus y;,'=0, y '=5.7, y =ll.5, y =17.4, and so forth to y =90.

A convenient minimum cam width must next be selected. In the 10." x 5" conventional frame of the example in the copending application referred to, it is seen that the difference in lengths of the inside and outside roving layers is about 3.5 inches. This means that the builder jaws will mo ve together by this amount or, one builder jaw will move 1.75 inches, along the builder screw.

Therefore a minimum cam width of 2 inches is a convenient value with which the maximum width will be around 5 /2 inches.

One can 'now calculate ordinate or y values from y to y for the camming surface of the present example from the relation where a= /2 of the minimum cam width or 1 inch, and b y =1.224", y =1.340", and so forth to y =2.750".

These values can be readily checked by slide rule. But,

again, for actual fabrication, accuracy requires that many more ordinates be calculated. Also, the calculations should be done by logarithms so that ordinate values can be computed to the nearest ten thousandth of an inch.

Now the ordinate values can be plotted on the work piece, by standard techniques, so that a' series of points (x, y) are located'from (x y to (x y For the cam of the embodiment shown in FIG. 2, the lower camrning surface 46 is laid out with the same ordinate values. But for this surface, the ordinate values are plotted in the negative y direction, Le, a series of points .(x, y) are P t from (x0 y0) t n yn)- A smooth curve is next scribed through each set of points so that the camming surfaces can be cut and fin- 60. Continuing study indicates to me that for winding difv ferent sizes of bobbns with different roving materials, and

ished by standard machine shop practices. Actually, the cam will. be cut a' few inches longer than the length (x -x so that therewill be sufiicient material at each end for mounting purposes and for adjustment. The shape of the. cam, edges over such added end portions is not critical but there should be no abrupt changes in dimen sions or curvature as the cutting operation is completed beyondthe camming surfaces.

The calculations outlined abovewill produce an exact V sine curve profile on the cam edges. For practical application, modifications, may be required before the cam is cut. As was discussed in the copending application previously referred to (at page 19), one modification relates to provision of a straight line taper at the ends of the final roving layers because of the rapidly decreasing radius of curvature of the sine curve as it approaches This can be providedin the present embodiment by 9 scribing on the work piece the straight lines which are tangent to the sine curves at the points These lines are then followed in cutting, from the points of tangency to the end of the cam, resulting in a slightly reduced value for y max. or y Illustrated mathematically for upper camming surface 45, ordinate values beyond the point where The value of y at y:60, which is 2.165, is then substituted in the equation to evaluate constant c. Whence y ==c+(d) (x =)=2.l65=c+(2)(.866), and the constant c is found to equal .433 inch.

Therefore, for the terminal points of the camming surface where x =l.0 (normalized), y =.433-l2(x )=2.433 inches The tangent line can then be drawn directly between the tan 32 /z=.766

Thus the equation of this line is y=l.0+.766(x) If, for example, this taper angle is to be maintained for /5 of the roving package layers, the terminal point of this line is (x =.2, y =l.l53).

Appropriate adjustments can be made in subsequent calculations of the ordinate values because now if the sine curve is to be followed from x to x,,, the net change in y or (y y )=l.597 inches as compared to 1.526

inches previously. This can be done rigorously by fol-- lowing mathematical reasoning similar to that previously discussed. But I have found that as a practical measure it is sufi'icient if the two curves, i.e., the sine curve and the initial straight line, are joined in the vicinity of the ordinates at x by a smooth curve. The error introduced will be less than 7%, which is inconsequential, and may be as little as half of that amount it the curve is scribed by a skilled draftsman.

Of course the system of FIG. 2 is equally useful if the follower cylinders are rigidly mounted on a structural member of the roving frame with the cam supported for simultaneous movement with the rack. In this case the cam 44 is simply reversed end for end from the position shown in FIG. 2.

The arrangements discussed would be for a hydraulic system with a mechanical advantage of unity. The areas of the cylinders and pistons can be provided so that the (y max.-y min.) value could be doubled, for example, the same. Also, a cam with only one carnmingsurface could be provided in whichcase onefollower piston would It was indicated at page 18 of the copending ap l be arranged connected so as to actuate both drive pistons. How to construct apparatus for alternative arrangements such as these will be apparent to those skilled in the art.

Table I below is a compilation of the values computed for the sine curve illustration.

*Refcrence point.

Another embodiment of my invention in which a flat shoe cam 69, similar to the shoe cam 44 described above, operates a simple mechanical drive for closing the builder jaws is shown in FIG. 3. The shoe cam 69 is mounted to be traversed back and forth in the direction of its longitudinal axis by the reciprocating motion of the rack 37. It is also mounted for up and down motion with the rail 11.

To provide the back and forth motion and to permit the up and down motion a pair of vertically extending

rods

64 and 55 are fixed at their upper ends to the rack 37 or an extension thereof. Angled braces as and 67 are fixed at their upper ends to the rack 37 and at their lower ends to the rods 64- and $55, for example by brackets 68 and as, to brace the rods securely in their intended positions relative to each other. The shoe cam is equipped at its opposite ends with bracnets 6t and 62. Each of these brackets has two spaced, coaxial sleeve bearings 63. The rod 64 is received iri the bearings 63 on the bracket 61 and the rod 65 is received in the bearings 63 on the bracket 62. Thus as the rack moves left and right the rods which are rigidly fixed to it carry the shoe cam with the rack. As best seen in FIGS. 3A and 3B, a mounting frame '70, having a horizontal support plate '71, is fixed to the rail ll. A guide and actuating rod '72; passes through a vertical aperture in the support plate 71 and extends in both directions from the plate. Al: is upper end the rod has fixed thereto an upper cam follower '73 in which is mounted a cam follower roller 74 in a position to engage the upper edge of the shoe cam. A lower builder jaw '75 is fixed to the lower end of the rod '72 and is provided with a camming surface '76 which extends parallel to the rod '72 and is generally similar in construction and purpose to the camming surface 17 on the builder jaw 15 previously described. In this arrangement the upper cam follower bracket 7 3, the rod 72 and the lower building jaw 75 thus move as a unit.

In this embodiment I also provide a combined lower cam follower bracket and upper builder jaw illustrated at 77. A lower cam follower roller '78 is mounted in me bracket part of the member 71 in a position where it contacts the lower edgeof the shoe cam 65). The member '77 is also provided on its builder jaw portion with a carnming surface '7) which extends parallel to the surface 7e and is generally similar in construction and function to the cam surface 16 on the builder jaw 14, previously described. The member 77 has an aperture through which the rod 72 extends but the rod and the member are free to move relative to each other; that is, the rod simply serves as a guide for the member T7.

An upper compression spring 3% is interposed between the support plate 71 and the member 77 and acts to urge the member upwardly. Similarly, a lower compression springlll is inserted between the support plate 71 7 ing of the stop pins.

and the lower builder jaw 75 and acts to urge the lower builder jaw 75, the rod '72, and the upper cam follower bracket 73 downwardly.

The

cam follower rollers

74 and 78 engage the upper and lower edges of -the shoe cam as previously stated the up and down motion of the builder mechanism as it reciprocates with the rail 11.

law closure is provided in successively greater increments as the cam followers are forced apart by relative, longitudinal cam movement. The novel mechanism just described cooperates with the builder dog 23 and the train of

gears

31, 32, 33, 34 and 35 and the rack 36 in a conventional manner.

In athird embodiment of my invention shown in FIG. 4, electromechanical actuation of the builder drive is used. In this embodiment, the referencedimension, as defined in the discussion above, is the angle of rotation which is always the same, through which the builder dog 23 rotates upon completion of each successive layer of roving.

' A conventional builder jaw mechanism is used for control of the builder dog. The builder dog performs in the usual manner, rotating through successive, equal 180 angles upon one arm thereof overrunning a camming surface on one of the builder jaws.

According to this embodiment, a pair of switches 91 and 2 are provided for alternate actuation by the builder dog arms. A rack 1th and pinion gear W7 are mounted in the frame for rotation of a builder screw shaft to close the jaws. A template 93 on which a plurality of stop pins 94 are arranged is atfixed to the rack. The camming dimension, again, as defined in the previous discussion, of this embodiment relates to'the longitudinal spac- The longitudinal spacing is'provided in amounts which have successively greater differences from one end of the template tothe other.

A relatively simple electrical arrangement results when the pins are. aligned as shown in two rows on the template. Solenoids 95 and 96 are then-mounted on opposite sides of the template with solenoid shafts projecting therefrom for engaging the rows of stop pins. In this situation, the pins of each row are longitudinally staggered. Thesolenoidsare connected electrically to the switches at the builder dog. A tension linkage connected between one end of the rack and a stationary part of the frame completes the arrangement.

"and last'stop pins will be equal to'the distance moved by the belt-shipper rack during winding on the conventional roving frame. As previously stated, for a 10 x 5" frame this distance is thirty tothirty-three inches. The template piece 93 is provided slightly longer than this distance for convenience in mounting and adjust- Longitudinal location of. the pins can be established several ways, based on the mathematical reasoning described previously. A very convenient method is available for this example when the taper gears 97, 98 and 99 provided have a conventional ratio so that the builder shaft rotates through a conventional total number of turns.

Lay off the total distance above, thirty to thirty-three inches, along the template center line. Then divide this distance into 10 equal increments. Then, starting with 3 :0 at the right, and using the 10 increments as a scale, where the last mark, y equals 1.00, the ordinate ratios from Table I, can be plotted directly along the center line or reference axis. Thus y =0, y =.063, y =.l28, y =.194 etc., to y -=l.00 at the left. Then two straight lines are scribed parallel to and above and below the center line. They can be conveniently scribed two inches apart, each being an inch away from the center line. V

'The y values are then projectedperpendicularly from the center line or reference axis to the outer lines with y values for odd values of n being projected to one line and those for even values of n, to the other. The template is then drilled at the intersection of the projec- I tions and the outer lines so the stop pins can be mounted When the builder dog 23 rotates, one of the switches is 7 noid when the builder dog again rotates, and so on. 1 Each time the rack is advanced in successively greater amounts, as determined by the successively greaterlongitudinal spacing between stop pins. As a result, of course, the builder jaws are moved together in successively increasing increments which is the action required for producing roving packages with convex curved ends.

I I will describe how a template with stop pins is fabricated so that the illustrative sine curve profile can be produced at the bobbins. For simplicity, rack 1% is made similar to rack 37 of PEG. 1. Then the total distance, between the first in staggered array along the template. can be welded at the points indicated.)

Again, this is illustrative and many more than 10 pins will be required. Actually if n=tl1e number of layers or roving, n+1 pins are necessary. But the above discussion will be adequate to show how these pins are positioned. V I

Also, the twomodifications described which provide for straight-line initial and final package taper can be readily incorporated in the stop-pin arrangement.

For the initial taper angle argument, taper gears 97 and 9 are selected so. that subsequent, equal step-move ments of rack 100 willresult in builder jaw closure to provide the taper angle desired. This is within the skill of the present art. Then the first fifth of the template from y to y (assuming this initial angle will be previously,v the pins are mounted inthe' alternate positions indicated.

For the straight line taper argument near the end of winding, say beyond y=.60 (specifically, for the last 30 of the sine curve or beyond y=.666 on the template), thexremaining length on the template is divided int'o,,r1'1' .equal increments where m the remaining number ofroving layers to be wound. These increments are then alternately'projectedto the stop-pin lines and the pins are mounted accordingly.

Another important embodiment of my invention, shown in FIG. '5, utilizes the relation of the previously defined ,reference andcammingdimensions'in a system ofp-olar coordinates. A rotatable cam is used in this embodi- Qment in connection witha chain. drive for turning a conventional builder screw shaft 18 through successive,

ly greater a'rcsupon completion of each successive layerf of roving.

r In this "embodiment a flat cam 105 and a wheel gear 106'are rotatably mounted on a common shaft. The shaft and wheel gear are mounted in the roving frame so that the .wheelJgear engagesthe belt shipper rack (Or, the pins 7 5.3 37. As shown, an extension 107 on the rack can be provided to simplify location problems in the frame.

The periphery 108 of the cam 165 is of a prescribed contour. This contour is readily explained with reference to a system of polar coordinates in which the pole coincides with the geometric axis of the cam and in which the polar axis or initial line is positioned coincident with the shortest radius of the cam. The reference dimension in this case is the angle measured from the initial line (counterclockwise). The carnming dimension, as l have defined it herein, is the length of any given radius from the pole or center of rotation 113 to the camming surface 1&8.

Thus, in this cam, successive radii are of increasing length. Moreover, for any series of successive, equal angular displacements from the polar axis (or initial line), corresponding successive pairs of radii'have successively greater difierences in length. In other words, for successive, equal changes in the value of the angle from the initial line, the corresponding dififerences in values of the lengths of radii (from the center of rotation to the camming surface) are successively greater.

The camming surface contour 1% is advantageously formed as a smooth curve. This means that succes sive arcs of the contour, which are subtend equal angles at the center of rotation, are of successively greater length. Therefore it the cam is rotated (clockwise in the polar coordinates defined) through successive, equiangular displacements past a reference line, corresponding successive arcs which cross that line have lengths whic differ by amounts which are increasingly disproportionate to the equal angular displacements.

For appli ation of the changing camming dimension principle in this embodiment, the cam follower comprises a cable 199 which is wound on the camming surface. It follows that, as the cam is rotated through successive, equi-angular displacements by the rack 37 and gear wheel 1%, successively increasing amounts of cable will be wound on the cam. The outer end of the cable is connected to a chain 119 which drives a sprocket 111 'through successively increasing angular displacements upon completion of each successive layer of roving. The taper gear train 41 and 43, driven by the rotating sprocket shaft, then operates to turn a standard builder screw shaft 18 for closing the builder jaws.

A tension linkage 112 attached to the other end of the chain, for'keeping the chain taut and for resetting the mechanism between dolls, completes the arrangement.

Fabrication or" a cam for this embodiment will be illustrat d, again, for the Saw-Lowell RS. '2, 10" x 5 roving frame.

First a base circle is selected for the cam. I have used a base circle with a radius ol 8 inches. A semi-circle of this radius is then laid out on a pattern or directly on a work piece. For the reference system of polar coordinates, the center or the circle becomes the pole and, with the semicircle convex upwards, the initial line, r =8 inches, lies horizontally to the right.

The semi-circle is then divided into 11 equal arc segments. Again, for illustration, 1 will use'n=l0 although the greater the value of 11 selected, the more closely the cam surface will approach the desired contour.

Thus, radii are drawn on the pattern at successive equal increments in the value of an angle 0 (measured counterclockwise from r around the pole). These increments in 6 are equal to rr/ 10 radians. Substituting 6/- for x in Table I, we thus have a series of normalized values fromt /1r=0, 9 1r=0.l and so forth to 0 /1r -l.0O.

Next a series of radius ratios, r'/r' are computed from the relation id The values of these ratios from r' to r are the same as those shown in column 3 in Table I. Then a series of values for r from r =0 to r=r can be obtained from the relation and so on to These values of r are marked along the successive corresponding radii and a smooth curve is scribed through the ends of the radii so the cam can be cut from the Work piece. Actually, the camming surface curve should be continued for a vertical distance of about two inches at each end so that more than the actual camis cut from the work piece. This providessuil'icient material for convenience'in mounting and adjusting the cam inthe frame.

Of course the carnming surface can be provided in-other shapes and with various modifications for particular bobbin profiles. The modifications previously described for initial and final taper angles can be provided. To do so on the cam illustrated, the mathematical reasoning previously discussed is applicable excepting that the same must be adapted for the polar coordinate situation.

After the cam is cut, the total length of the cumming surface is measured, as with a tape so that a proper chain sprocket-and taper gear ratio can be selected. This selection is within the present skills of the art and will not be explained further at this point.

A more rigorous analysis for developing the camrning surface is also possible if one first selects the taper gear ratio andsprocket pitch diameter. Then, knowing the total number of turns required for the builder shaftduring winding, the total camming surface length is determined from the relation S=f21r (pitch radius of the sprocket) (N) where N is the-number of sprocket revolutions.

The'base circle radius is selected and the semi-circle is divided as before. Then a series of increasing arc lengths can be computed from the relation In polar coordinates, arc length is the relation: ds =dr (n10)? Subsequent values for r from r=r to r can be de veloped using the two equations expressed. This analysis can be carried forward by those skilled in the mathealso expressed from matics and will notbc developed here.

- Concerning the electroemechanical embodiment of my invention which I have'described, other-very advantageous forms can be. provided. One of these alternate forms requires negligible roving frame .modification.

Moreover,---with this alternate form, the long-standard builder jaw-mechanism can be eliminated. The. builder screw means.

7 .Two limit switches are actuation by the limit pins.

gizing.

ber of the frame which reciprocates in synchronism with the bobbin spindles. The axis of the shaft is disposed parallel to the direction of reciprocation. If necessary, an extension can be provided on the shaft to simplify location problems in the frame. The builder shaft herein is connected by the standard gear arrangements to the belt shipper rack for rotation. But, it does not have the usual builder jaws connected at its lower end. Rather, a series of limit pins are provided projecting in the radial directions from the shaft. p

The principles of reference and camming dimensions as I have hereinabove defined are again applied. In this alternate embodiment, the reference dimension relates to the angular spacing between successive limit pins. The limit pins are positioned along radii of successively equal angular displacement around the builder shaft.

The camming dimension relates to the longitudinal spacing between successive limit pins. The longitudinal spacing is provided in amounts which have successively greater differences from the first pin to the last. In other words, for illustration, the pins can be set perpendicular to the axis of the shaft, along a line on the surface of the shaft which defines a helix of continuously increasing pitch. 7

In this embodiment, two sets of these pins are located on the shaft spaced from each other in opposite longitudinal orientation. The pins of each set on the shaft are staggered by an angular amount equivalent to one shaft 1 angular displacement.

A collar can be provided in which the pins are mounted. Such a collar provides increased circumferential distances for equal angular spacings between pins so that no two pins on one collar will be aligned parallel to the shaft The collar can then he slipped on the shaft and held in pla'cefor movement therewith by ordinary key or set- The switches are electrically connected to the builder dog solenoidsfor altennate ener- As the builder shaft moves upward a limit-pin will close -the lower limit switch at the desired limit of upward travel of the bobbin spindle-s. Closing this switch energizes one of the builder dog solenoids. The corresponding solenoid shaft is thereby withdravm from engagement with one of the builder dog arms. The builder dog and tumbler shaft are thus freed to rotate through the normal180 arc, until the other builder dog arm engages the second gsolenoidshaft. As has been explained, this 180 revolution of the tumbler shaft causes the direction of the bobbin spindles to bere'versed. 7

The builder shaft is rotated as in the normal roving frame, through successive equal arcs upon each builder then arranged in the frame for According to this embodiment, a template with two rows of stop pins, longitudinally staggered as before but with successively equal longitudinal spacing, is provided on a rack adapted for longitudinal movement by a tension linkage. Solenoid shafts are also arranged engaging the row of stop pins for limiting rack movement. Limit pins are arranged on the builder shaft as descnibed above. Limit switches are again positioned for actuation by the limit pins.

In this embodiment, a selsyn generator is mounted on the tumbler shaft, with its rotor rigidly affixed to the shaft. successively greater decrements in the amplitude of reciprocation are controlled as before, with the limit switches each being electrically connected to a rack solenoid and to a builder dog solenoid; Each time a limit switch is closed, therefore, the builder dog rotates 180 and the rack advances, moving the builder shaft through successive equal angular displacements.

A selsyn motor, electrically connected to the genenator, is used in this embodiment for advancing the be'lt'shipper through successive, equal displacements in response to the successive 180 displacements of the selsyn generator rotor on the tumbler shaft.

Still another arrangement is possible,-by using a second selsyn motor geared to the builder shaft, which permits elimination of the above rack and template and stop pin solenoids. In this arrangement, the limit pins and limit switches are mounted as before for limiting the amplitude of reciprocation of the bobbin spindles. Solenoids, energized upon closure of the limit switches, are again used for control of builder dog rotation,

' Operation is as before with the added feature of the one'sel'syn-generator being used to drive two selsyn motors One selsyn'm-otor is used to rotate the builder shaft and the other, to advance the belt shipper as described.

. The selsyn evolutions required are, as is evident from my previous discussion, all of successively equal amounts.

Hencethe generator rotor on the tumbler shaft can be used, electrically, to drive thetwo motors which, through appropriate gearing arrangements, displacev the belt-shipper and builder shaft, by successive, equal, prescribed amounts.

Concerning the disc cam embodiment of FIG. 5, one

important additional feature should be described. By,

providing an adjustable mounting apparatus at the shaft on which the cam 105 and wheel gear 1% are sup-ported,

the axial position of the cam'can be changed. This means that an operator, skilled in the-use of these cams, can set a the cam geometric axis to 'a predetermined positioned-set dog' and tumbler shaft evolution. The builder shaft revolution then places the next limit pin in line for succeeding V actuation of the next limit switch.

. 'The nextli-mit switch is in turn closed when the suc ceedingrecip-rocation is at its zenith. The next solenoid is energized and'the builder dog again rotates 180 to reverse the .reciprocatory motion, and so on. Each time the builder shaft is turned (by successively equal angular amounts) the amplitude of the succeeding reciprocation is reduced. T he differences in relative longitudinal spacing of the limit pins are increasingly disproportionate to "the successive equal displacements of the'builder shaft.

Hence, theamplitude is continuously reduced in successively increasing increments, which is the action required for production ends. a

of roving pack-ages having convexly curved Still another electro-mechanical embodiment within: the

the directionof reciprocation of the bobbin spindles. Tension gearing andthe belt shipper rack are also eliminated;

from the axisof rotation. With such a degreeof mechanical freedom, fine roving package profile modifications can be obtained which furtherincreases theutility of this embodiment. V r V I have described my invention indetail. Several embodiments discussed above are illustrative of what "can be accomplished within the scopeof my invention.

lclaimzf" 1. In a roving frame having shaft and builder dog, for reversing the direction of said reciprocatory movement, and a builder mechanism, in

'cluding a builder shaft, mounted on said member to control the actuationlof said reversing means, said builder dog having a pair ofoppositely extending arms adapted for alternate engagement with said builder mechanism,the improvement which comprises a 'rack mounted in said template mounted on said rack, a plurality of stop pins mounted on said template'and projecting therefrom, said pins being successively spaced longitudinally of said template, soienoid means mounted adjacent said template for periodic engagement of said pins, and switch means electribobbins mounted on a member of the frame for reciprocatory movement with ,respectto flyers,'means, including a rotatable tumbler cally connected to said solenoid means for actuating the same, said switch means being mounted in said frame, the position of said builder mechanism being adapted to determine the position of actuaton of said switch means, and said tension linkage biasing said rack for longitudinal movement when ever said solenoid means are out of engagement with said pins.

2. The roving frame combination of claim 1 in which said stop pins are aligned in two longitudinal rows on said template, longitudinally successive pins being laterally staggered in said rows, and one said solenoid means is mounted adjacent each of said rows, each of said solenoid means having a retractable shaft for engaging said pins.

3. The roving frame combination of claim 2 in which said successive stop pins are spaced at increasingly greater longitudinal increments.

4. The roving frame combination of claim 1 in which said gear means comprises a gear train one member of which is disposed engaging said rack and another member of which has a passage at its center in which said builder i8 shaft is slidably arranged for rotation, said builder shaft and train being rotated by said rack when the same is moved by said tension linkage.

5. The roving frame combination of claim 3 in which one said switch means is mounted adjacent said builder dog for actuation by one of said arms and .a second said switch means is mounted adjacent said builder dog for actuation by the second of said arms, said one switch means being electrically connected to one said solenoid means, said second switch means being electrically connected to the other said solenoid means.

References Cited by the Examiner UNITED STATES PATENTS 2,870,597 1/59 Hill 5799 X 2,982,487 5 61 Newton 242-461 3,019,588 2/62 Sanders et al. 5799 3,049,859 8/62 Wise 5799 3,108,429 10/63 Heiberg S7-99 MERVIN STEIN, Primary Examiner.

Claims

1. IN A ROVING FRAME BOBBINS MOUNTED ON A MEMBER OF THE FREAME FOR RECIPROCATORY MOVEMENT WITH RESPECT TO FLYERS, MEANS, INCLUDING A ROTATABLE TUMBLER SHAFT AND BUILDER DOG, FOR REVERSING THE DIRECTION OF SAID RECIPROCATORY MOVEMENT, AND A BUILDER MECHANISM, INCLUDING A BUILDER SHAFT, MOUNTED ON SAID MEMBER TO CONTROL THE ACTUATION OF SAID REVERSING MEANS, SAID BUILDER DOG HAVING A PAIR OF OPPOSITELY EXTENDING ARMS ADAPTED FOR ALTERNATIVE ENGAGEMENT WITH SAID BUILDER MECHANISM, THE IMPROVEMENT WHICH COMPRISES A RACK MOUNTED IN SAID FRAME FOR LONGITUDINAL MOVEMENT, A TENSION LINKAGE MOUNTED IN SAID FRAME AND CONNECTED TO SAID RACK, GEAR MEANS CONNECTING SAID RACK TO SAID BUILDING MECHANISM, A TEMPLATE MOUNTED ON SAID RACK, A PLURALITY OF STOP PINS MOUNTED ON SAID TEMPLATE AND PROJECTING THEREFROM, SAID PINS BEING SUCCESSIVELY SPACED LONGITUDINALLY OF SAID TEMPLATE, SOLENOID MEANS MOUNTED ADJACENT SAID TEMPLATE FOR PERIODIC ENGAGEMENT OF SAID PINS, AND SWITCH MEANS ELECTRICALLY CONNECTED TO SAID SOLENOID MEANS FOR ACTUATING THE SAME, SAID SWITCH MEANS BEING MOUNTED IN SAID FRAME, THE POSITION OF SAID BUILDER MECHANISM BEING ADAPTED TO DETERMINE THE POSITION OF ACTUATION OF SAID SWITCH MEANS, AND SAID TENSION LINKAGE BIASING SAID RACK FOR LONGITUDINAL MOVEMENT WHEN EVER SAID SOLENOID MEANS ARE NOT OF ENGAGEMENT WITH SAID PINS.