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June 28, 1938. ~ ’ > ~' A. J. EN'GEL '- ' MANUFACTURE OF ARTIFICIAL SILK Filed Dec. 6, 1955 v ,. I 2,122,092‘ I 2 Sheets-Sheét 1 $9.41‘ SKIMMW _June28,1938. A__,_ENGE._ . ' 2,122,092 MANUFACTURE OF ARTIFICIAL SILK Filed Dec. 6, 1955 , 2 Sheets-Sheet 2 1/115 Qwucmkon ' Shame/x5 Patented June 28, 1938 2,122,092 ' or Anemia s Antonie Jacobus Engel, Arnhem, Netherlands, Corporation, assignor to American N. 0., a corporation of Delaware Erika, Application December 6, 1935, Serial No. 53,254 In the Netherlands December 8, 1934 . (501 242-43) 8 C a: 1 Ms having a frusto-conical shape. However, the This invention relates to traverse mechanism of the type generally used in the production of form of the spool or bobbin ends does not de pend upon‘ the number of rotations of the auxil- , bobbins and more particularly to means for iary movement but exclusively upon the speed forming the tapered winding on the end of the v bobbin spools. 5 . pattern of the auxiliary movement. ‘Therefore, an object of this invention is the provision of mechanism whereby thread can be wound upon bobbins to form a package having end edges thick enough for‘ proper washing, dye - When winding textile materials, particularly arti?cial silk, as is known, a traverse varying device is employed by means of which the ma terial obtained from the spinning process is guided so as to be deposited on bobbin spools in ing, or drying. a predetermined form. Traverse mechanisms whereby a spool or package of thread is formed which will‘ be free from noticeable ridges. winding on the end of the spool a conical shape, but these have not proved to be satisfactory be cause of the difference in density between'the end edges of the winding and the main body. This invention further contemplates the pro-' vision of a mechanism whereby a number of the 15 above described movements may be combined to give the desired type of winding. Spools or bobbins formed in Other objects, advantages and characteristic this manner cannot be washed, dyed, or dried features of the invention will become apparent evenly. as the description of the disclosed embodiment _ progresses, reference being had to the annexed ' When winding bobbins with freshly spun rayon the traverse movements most generally drawings in which: Figs. 1, 2 and 3 are diagrammatic representa tions of fragmentary‘longitudinal sections of cy lindrical windings showing the different eiiects 25 produced in forming the winding with different arrangement of traverse mechanism; ./ used are almost always made up of one main movement combined with one or two auxiliary movements. The main movement being that ob tained by allowing the roller of the thread guide 25 arm to roll around the periphery of a cam of predetermined shape. The auxiliary movements I employed are, ?rst, the simple stroke displace-- ‘ ment and the regular stroke shortening move 10’ This invention also contemplates, apparatus have been employed heretofore which give the portion thereof. r Fig. 4 is a diagrammatic illustration of ‘the " traverse guide as taught by this invention show 30 ment that takes place during the spinning pe ing the position of the cams while eifecting 30 maximum displacement of the thread guide to riod, and secondly, the “Pilgrim Step”. These , right; movements are distinguished one from the other theFig. 5 is similar to Fig. 4 but showing the by the ratio between the number of rot'ations'of the auxiliary movements and the rotations of the main movement. When using the ‘stroke short ening movement as referred to above, then dur ing‘ the entire‘ winding on period‘ the auxiliary movement moves only once causing the ampli tude of traverse to change from a maximum in starting the winding on period to a minimum on 40 the completion of the winding on period. Then when the “Pilgrim Step” is employed the auxil iary movement may make twenty times as many rotations as the main movement thereby caus ing the guide to oscillate backward and forward 45 in its path across the spool or bobbin a corre-v sponding number of times. Using the stroke dis placement movement the auxiliary movement may turn as much as one twentieth the speed of the main movement thereby causing the am 50 plitude of traverse to decrease to a minimum and build up to a maximum during 20 cycles of the , guide. In winding yarn into packages the effect of 55 the auxiliary movement is to form packages thread guide at its maximum displacement to the left; ' ‘ . v ‘Fig. 6 is a front detail elevation of the traverse _ mechanism} Fig. '7 is a detail vertical longitudinal section along the line 'l-,-'l of Fig. 6 showing the gear train employed in driving the auxiliary cam; Fig. 8 is a vertical section of a modi?cation of the gear train shown in Fig. '1, showing the use of a different gear ratio; I Fig. 9 is a vertical section of a second modi?ca 45 tion of the auxiliary cam driving mechanism. Referring‘to the drawings, particularly Figs. 6 and "l, the mechanism is driven by a main drive shaft III that is connected to a suitable source of power not shown. A hub I l is ?tted on the oppo site end of shaft I0 and adapted to turn with 50 the shaft to drive the main eccentric or cam I2. Eccentric I2 is substantially heart-shaped in‘ ' form and the periphery thereof serves as a track on which the roller \end of a bell crank, which ‘serves as the thread guide arm, is adapted to 2 ' move. ‘ " 2,122,092 The eccentric I2 is secured to a guidev member l3 which is adapted to move in a line which is at right angles. to the shaft. Provisions for such movement are made by slotting member l3 as shown at M and IE to receive the driving crank pine l6 and the hub II respectively. The‘ crank pin 16 is secured to a crank arm I‘! vwhich is made integral with hub H, by means of a bolt l8. Such'an arrangement 10 is provided to permit the .main cam I2 to ‘move and may only be altered by changing the con tours of v‘cam 22. Heart-shaped camsmountedand adapted to turn on eccentric bushings have been usedhere tofore on traverse mechanisms. In operation the cam is driven at a constant speed while the eccen tric bushing is rotated at any desired speed de pending upon the form-‘of movement that is to ‘ be employed in forming the winding. First let along its center line i. e., its line of symmetry, _ us suppose that the bushing turns very slow as 10 with respect to the main drive shaft l0. Springs compared to the main cam, for example, no more I 9 are connected to hub I I and the cam I2 and thereby normally tend to force the point of cam 15 I 2 toward the main shaft In. This movement, however, is limited by roller 22 that is mounted upon the guide member l3 by means ‘of bolt 2|. A second or auxiliary cam or eccentric member 22, the periphery of which forms the path for 20 roller 20, governs the movement of the main cam with respect to the shaft. Thus it can be read ily seen that although the main cam I2 is adapted to slide on the shaft along its center line, it is also caused to rotate by the shaft... Cam‘ 22 is 25 keyed to and adapted to be driven by bushing,23. Bushing 23 is driven by means of gears 24, 25, 26 and-21 from the main shaft l0. These gears obviously may be given any desired ratio to obtain varying relative speeds between cam 22 and cam As shown in Fig. 8 a gear ratio may be se lected which will cause the cam 22 to be driven 30 I 2. at a relatively higher speed than cam l2, while on the other hand should it be desirable to drive cam 22 at a somewhat lower speed than cam I2, 35 an arrangement of gears'such as is shown in Fig. 9 may be employed. The gears 24-21 must have then e. g. 34, 34, 29 and 39 teeth respectively. The form that the winding will take on the spool is directly dependent upon the speed pat 40 tern of cam 22. Therefore, the shape of ,cam 22 must be of such contours as will give the desired form to the winding. In operation if it is desired to employ the “Pilgrim Step" movement in wind— ling a thread on a spool or bobbin the cam 22 must, of'necessity, be driven at a higher speed than cam. I2. This will effect an oscillatory movement of the thread guide arm which will cause the thread to move forward and backward a number of times corresponding to'the ratio of the speeds of the respective cams during each traverse of the spool or bobbin. It is to be un derstood that cam 22-will have the desired con tours to effect a proper shape of winding. The than ‘180° per “wind on”. Then, the cam will move with respect to the driving shaft in such a way that during the winding on period the stroke of the cam decreases regularly. The eccentric bushing thus determines the speed at which the stroke will decrease and if it is as sumed that the relative rotation of the eccentric bushing as compared to the cam is of a uniform speed, then it follows that the displacement of 20 the cam during the beginning of the winding on period takes place very slowly. However, during the winding on period it will increase, then to ward the middle of this period, the speed of dis placement will reach a maximum. Thereafter 25 thevspeed of displacement will decrease and to ward the end of the winding on period will ap proach zero as a limit. Thus it can be seen that the speed pattern of displacement will assume the form of a sine curve.‘ 'In this case the frusto conical ends of the spool package will appear as indicated in Fig. 1 by the heavy line. Alterations in the relative speed of the cam and bushing will not change the theoretical form of the spool end. When the eccentric bushing is 35 turned 360° instead of 180° relative to the cam ‘during one winding on period the stroke is as indicated above throughout the ?rst part of the period, but twice as fast. The package thus formed up to this point will only,have one-half the thickness of that discussed above. However, 40 during the movement of the eccentric bushing through the remaining 180° of the winding on period the stroke will increase again and the movements will be exactly opposite to the ones in the first half. I The changes of the stroke are 45 equal, but opposite, consequently the package is built up exactly as in the ?rst instance. In either case the package retains the same form regardless of whether the eccentric bushing makes one revolution or many relative to the cam. So 50 Fig. 1 illustrates ,also the form of the spool or “Pilgrim Step” movement may be accomplished package formed by the simple stroke displace- ' 55 by utilizing a gear trainv such as that disclosed ment or “Pilgrim Step” traverse produced by the auxiliary movement derived from‘ the eccentric in Fig. 8, the gears 2t-_21 having for example I bushing 55 in the cam. , respectively 45, 23, 45 and 23 teeth. If it is desired to wind the bobbins by the stroke , shortening movement, then, of necessity, cam 22 80 must be driven at a much slower speed than cam l2. A gear train such as shown in Fig. 7 ‘may be employed to effect this movement, the number of teeth of gears 26-2'I being respectively 151, 150, 149 and 150. Driving cam 22 slower than cam i2 will cause'the thread guide arm to move through a path traversing the spool from maxi mum amplitude or the longest stroke to an am plitude which approaches zero as a limit or the minimum stroke in the first 180° movement of 70 cam 22. As cam 22 completes one revolution or the second 180° the amplitude of traverse of the thread guide will increase to a maximum. Re gardless of the number of revolutions made by the cam 22 relative to the cam l2 the shape of M the winding on the ‘spool will remain the same Due to the fact that the thread lags on making the return stroke relative to the thread guide, one does not get the theoretical form ofspool end. The lagging of the thread relative to the guide 60 on returns will result in an extra turn of yarn being deposited on all points of the return and with a given number of returns these surplus turns will amount to a substantial quantity of yarn. It can readily be seen that whenever the change in the length of stroke is small there will 65 be a greater number of reverses that will come together and the amount of yarn built up as a result of the lag will increase accordingly. In Fig. v1 a dotted line illustrates how the shape of 70 the end of the spool is changed by this phenom enon and further explains how ridges in the wind ing originate. Another auxiliary movement that has been. pro posed for reducing the stroke is one which effects ' 2,122,002 a constant speed displacement of a main cam along a line at right angles to the axis of rota ' . ' 3 driven in the same direction at uniformly differ ent speeds by reason of the gears 24, 25, 26 and 21 which transmit power from the shaft II), with tion. A spool produced when utilizing this move which the main cam is operatively connected, ment is of the form, theoretically, as illustrated to the bushing 23, to which latter the auxiliary by the fulllines in Fig. 2. The lagging, of the cam is keyed. The main cam i2 is thus free'to Ur thread, however, will cause the shape of the spool move me line corresponding to its line of sym to assume a form such as is indicated by dotted metrys-that is, in a line which bisects the cam line in this same ?gure. Although the ridges are into two symmetrical parts-and is held by' much smaller than those illustrated in Fig. l springs IS in, contact with the auxiliary cam‘ 22. 10 in dotted line,'they are, nevertheless, of substan Therefore, the displacement of the roller riding tial size and, of course, are objectionable. Other upon the periphery of the main cam and control difficulties encountered in using such a move ling the traverse mechanism will be the result ment are, that the winding on the end‘ of the ant of two different movements of the main cam, spool'is too thin and introduces difficulties when namely, the displacement imparted to the roller 15 subjected to suction or pressure wash due to the by the throw of the main cam rotating about the fact that the permeability of the end of the wind axis of drive shaft Ill, and the displacement re ing is so much greater than’that of the mid sulting from shifting of the main cam along its line of symmetry .under'the in?uence of the‘ section. ' . ' 20 A spool or package of thread formed by utilizing , auxiliary cam. , The main cam being heart-shaped, the shape 20 the mechanism and method set out herein may . have a form such as is illustrated by‘ Fig. 3 i. e. of the auxiliary cam is preferably so selected that the sectional contour of the end ‘of the winding the main cam moves smoothly along its line of can be of a form corresponding to a logarithmic symmetry between its two extremes of travel curve. This form has the‘ advantage, that it gives with a speed of movement that increases with a 25 an even permeability in pressure- or suction decrease in the distance between the highest point washing and that it is free of ‘ridges. This is of the main cam and its axis of rotation,‘ and vice possible because the thread lags when it reverses versa. Also the auxiliary cam is so formed that and a crossing different from that in the cylin the cam throws of successive points of its pe drical part results, thereby effecting a lesser de riphery vary in accordance with a logarithmic 30 30 gree of permeability per unit thickness of pack age, which provides the necessary equalizing fac tor. The varying of the thickness after a loga rithmic curve'is obtained by making the speed of the'auxiliary motion for stroke reduction in crease regularly from the beginning to the end of the wind on period. The constructions here to known. can not give such a form, as they have '40 not the characteristic of my invention, that the two traverse movements are combined in such a way that the auxiliary movement is employed only to move the main cam or eccentric member in its position relative to the shaft, while in each position this main ‘cam alone determines the length of the stroke. So the form of the auxiliary cam can be chosen freely, as at any moment only .one point of.it is working. The shape of the extreme ends of the spool is only a?ected by the change in shape of the aux iliary cam in the ‘vicinity of the point which has the greatest radius, and that portion of the spool 50 end de?ned by the extreme outer end of the spool and the cylindrical portion thereof is dependent . for its shape on the shape of the auxiliary cam curve. ‘ - _ r - In this way the thread guide carried by the traverse mechanism travels back and forth along the spool or bobbin with the speed of the auxiliary motion imparted by the auxiliary cam regularly - increasing during the period of the shortening of the stroke of the thread guide. 1 This results in a package having the general form indicated in Fig. 3 in which the‘end edges are substantially free from ridges and are of a suitable density for 40 proper washing, dyeing and drying. While the invention in-its preferred form contemplates the employment of an auxiliary cam of the logarith mic character described above, it will‘ be apparent that in its broadest aspect the invention is not 45 limited to any particular shape of auxiliary cam, and that the shape of ‘such cam may be suitably selected according to. the desired form vof the package to be wound. , , Although for purpose of illustration and ex no planation this invention has been described in connection with a thread guide that is fastened to ' the end of a swinging lever of the bell crank type, the invention is equally applicable to the recipro in‘ the vicinity of its smallest radius. Therefore, eating form of guide member. In fact, it would as ' it is obvious that regardless of the movement ?nd application to substantially all forms of tra 55 employed any desired shape of winding can be verse mechanisms employed in the spinning art. obtained by the selection of an auxiliary cam "Permeability" as used herein is de?ned as having the desired contours. that quantity of water which will flow through The position of the thread guide has been dia one square centimeter of the surface of the pack grammatically indicated in Figs. 4 and 5 for age at a given pressure in a, given interval of‘ 60 maximum strokes. Its position is de?nable in time, while "wind‘ on” or “winding on" period, I one extreme position by the dimension “A” of as used herein, refers to a period in which the the main cam plus dimension "a” of the auxiliary cam and in the other extreme, position by “28" ’ spool or package is completely wound. minus “11". Therefore, the total stroke is (“A” I What I claim is: _ 1. In an apparatus for winding spools or bob plus “a.") minus (“3” minus "113’) and is equal to a traverse actuating mechanism comprising “A” minus “3” plus 2 “a”. Minimum stroke may bins, a main cam of symmetrical shape and adapted to be obtained by rotating the auxiliary cam 180° guide arm of the traverse (see Figures 4 and.5). In this case the roller is control the thread then closer to the shaft and the stroke is "A" mechanism, an auxiliary cam located adjacent the main cam and independently rotatable with minus “13” plus 2 “b”. ‘ The operation of the apparatus will be readily respect thereto, means supporting the main cam apparent from the foregoing description. Dur 75 ing rotation of the drive shaft in, the main heart shaped cam l2 and the aumliar'y cam 22 will be _ 65 , 70 for displacement along its line of symmetry, means extending between the main cam and aux iliary cam whereby relative rotation between the 75, 4 2,122,092 cams causes displacement of the main cam along its line of symmetry and means for rotating the ‘cams at relatively different speeds. 2. In an apparatus for winding spools or bob bins, a traverse actuating mechanism comprising a main cam of symmetrical shape and adapted to control the thread guide arm of the traverse mechanism, an auxiliary cam located adjacent '10 the main cam and independently rotatable with respect thereto, a roller supported by the auxiliary cam, means yieldingly retaining the roller in en gagement with the periphery of the auxiliary cam whereby relative rotation between the cams causes displacement of the main cam along its line 15 of symmetry and means for rotating the cams at relatively di?erent speeds. 3. In an apparatus for winding spools or bob bins, a traverse actuating mechanism comprising a rotary drive shaft, a main cam‘ operatively con 20 nected for rotation to the drive shaft, said main cam being of symmetrical shape and adapted to ‘control the thread guide arm of the traverse mechanism, an auxiliary cam located in closely spaced parallel relation to the main cam and independently rotatable with respect thereto, means supporting the main cam for displacement along its line of symmetry, means extending be tween the main cam and auxiliary cam whereby relative rotation between the cams causes dis 30 placement of the main cam along its line of sym metry and means for rotating the drive shaft and auxiliary cam. ' 4. In an apparatus for winding spools or bob bins, a traverse actuating mechanism comprising 35, ,a rotary drive' shaft, a main cam operatively con nected for rotation to the drive shaft, said main "cam being of symmetrical shape and adapted to control the thread guide arm of the traverse mechanism, an auxiliary cam‘ located in closely 40 spaced parallel relation to the main cam and in dependently rotatable with respect thereto about cam and independently rotatable with respect thereto, means supporting the main cam for dis placement along its line of symmetry, means ex tending between the main cam and auxiliary cam whereby relative rotation between the cams causes displacement o'f the main cam along its line of nected to the drive shaft for rotating the auxiliary cam at a diiferent speed relative to the drive shaft. I 6. In an apparatus for winding spools or bob bins, a traverse actuating mechanism compris ing a main cam of symmetrical shape and adapted to control the thread guide arm of the traverse mechanism, an auxiliary cam located adjacent the main cam and independently rotat able with respect thereto, means supporting the ' main cam for displacement along its line of symmetry, means extending between the main 20 cam and auxiliary cam whereby relative rota tion between the cams causes displacement of the main cam along its- line of symmetry, said auxili ary cam being so shaped thatthe cam throws of successive points upon its periphery vary in ac-' cordance with a logarithmic curve, and means for rotating the cams at relatively different speeds. _ 7. In an apparatus for winding spools or bob bins, a traverse actuating mechanism compris- . ing a rotary drive shaft, a hub ?xed to the drive shaft and having a crank arm‘ extending radially therefrom, a main cam of symmetrical shape loosely associated with the hub, and adapted to control the thread guide of the traverse mecha 35 nism, a guide member rigidly ?xed to the main cam and having an elongated slot therein dis posed parallel to the line of symmetry of the main cam, a pin extending laterally from the crank arm and receivable in the slot for imparting rota 40' an axis corresponding to the axis of said drive' tion to the guide member and main cam, a bush shaft, means supporting the main cam fordis placement along its line of symme'try,>means ex tending from the main cam‘ and yieldingly main_ tained in engagement with the periphery of the auxiliary cam whereby relative rotation between the cams causes displacement of the main cam along its line of symmetry and means for rotat 50 ing the drive shaft and auxiliary cam at relatively different speeds. > . 5. In an apparatus for winding spools or bob ' , - bins, a traverse actuating mechanism‘ comprising a rotary drive shaft, a main cam operatively 55 connected for rotation to the drive shaft, said CH symmetry, means for rotating the drive shaft and speed change mechanism operatively con ing surrounding the drive shaft and independ ently rotatable with respect thereto, an auxiliary cam ?xed"to said bushing and located adjacent the guide member, a roller' carried by said guide member, spring means yieldingly urging said roller into engagement with the periphery of the auxiliary cam whereby relative rotation between ‘the'cams causes displacement of the main cam along its line of symmetry, and means for rotat ing the drive shaft and bushing at different 50 speeds. 8. A traverse actuating mechanism as set forth in claim 7 in which the auxiliary cam is so main cam being of symmetrical shape and' shaped'that the cam‘ throws of successivelpoints 55 upon its periphery vary in accordance with a adapted to control the thread guide arm of the logarithmic curve. . , traverse‘ mechanism, an auxiliary cam located in closely spaced parallel relation to the main ANTONIE JACOBUS ENGEL.