US3203163A - Traverse and tension control for winding machines - Google Patents

Description

Aug. 31, 1965 JQ R. LONG 3,203,163

TRAVERSE AND TENSION CONTROL FOR WINDING MACHINES Filed May 31, 1963 I 7 Sheets-Sheet 1 J. R. LONG TRAVERSE AND TENSION CONTROL FOR WINDING MACHINES Filed May 31, 1963 7 Sheets-Sheet 2 J. R. LONG Aug. 31, 1965 TRAVERSE AND TENSION CONTROL FOR WINDING MACHINES Filed May 31, 1963 7 Sheets-Sheet 5 5 4 A i R "I m. r i l: x I \b x f L[|- J O 2 I 9 Z 5 b 4 w u 5 Z 2 mm 9 a 4 mm a Z Z 2 A Z Z n.- .7 mm g; 22% V K 5 "r "I W W-H l 7 7 5 7 0 w. L l W J. R. LONG Aug. 31, 1965 TRAVERSE AND TENSION CONTROL FOR WINDING MACHINES Filed May 51, 1963 7 Sheets-Sheet 4 J. R. LONG Aug. 31, 1965 TRAVERSE AND TENSION CONTROL FOR WINDING MACHINES Filed May 51, 1963 7 Sheets-Sheet 5 8 8 E%'i 2 mm\ II M u a w m u I m .l Eo I. 7 it 5 W. HHHHUZ m; Z Z Qw u z w m a m w 2 m 5 m m m N m 0 3 m M ill 2 E W 42! w Q 1. m 0 v. u a a w @m 0 INVENTOR. JoHM R. Loma ATTOEA/EVS Aug. 31, 1965 J. R. LONG 3,203,163

TRAVERSE AND TENSION CONTROL FOR WINDING MACHINES Fil ed May 31, 1963 '7 Sheets-Sheet 6 20\ 10 I85 280 240 165 370 am, 2 $2 292 2 Z\ JOHN 2. LONG} INVENTOR.

J. R. LONG Aug. 31, I965 TRAVERSE AND TENSION CONTROL FOR WINDING MACHINES 7 Sheets-Sheet 7 Filed May 51, 1963 United States Patent 3,203,163 TRAVERSE AND TENSION CONTROL FOR WINDING MACHINES John R. Lo-ng, Hickory, N.C., assignor to Shuford Mills, Inc., Hickory, N.C., a corporation of North Carolina Filed May 31, 1963, Ser. No. 284,647 19 Claims. (Cl. 57-98) This invention relates to textile strand winding machinery, such as fly frames and the like, and is particularly directed to a novel apparatus for controlling the length of relative strokes effected between strand traversing means and bobbins and for controlling relative rotationa1 speeds thereof.

Although the present invention is adaptable to other types of winding machines, the advantages and efficiency thereof may be more readily realized when explained in conjunction with a fly frame. Accordingly, the invention will be described hereinafter as applied to a fly frame.

As is well known, strands of roving are directed from drafting rolls to rotating bobbins of a fly frame by means of flyers which generally rotate at a constant speed throughout the build or winding cycle, and the bobbins rotate at gradually decreasing speeds as the diameter of the packages being formed on the bobbins increases. Heretofore, conventional fly frames have included a large number of elements for imparting the vertical reciprocatory traversing motion to the bobbin carriage relative to the flyers while effecting necessary changes in the rotational speed of the bobbins relative to the flyers.

For example, the bobbin speed has been controlled by large top and bottom oppositely tapered cones engaged by an endless belt which was shifted, in a stepwise manner, by an elongate rack. The rack was connected to a tumbler shaft of a builder motion through a train of tension gears and a worm fixed on the usual tumbler shaft. The builder motion varied the traversing strokes of the bobbins by means of builder blocks threaded on a builder shaft rotated by the aforementioned rack through another gear train. The builder blocks were raised and lowered with the bobbin carriage and relative to arms on a tumbler fixed on the tumbler shaft. Whenever the builder blocks were raised or lowered beyond corresponding arms on the tumbler, the teeth of a partially mutilated gear would engage a gear on the top cone shaft to impart about one-half a revolution to the tumbler shaft which would, in turn, impart movement to a set of twin gears, through the medium of a complicated shifting mehcanism, to thereby reverse the direction of traversing movement of the bobbins at the end of each stroke thereof.

It is apparent that the large number of elements set forth in the above example have many points of wear; there is necessarily considerable lost motion between the rack and the various gears of the gear trains so the shifting of the belt along the cones has not been uniform at all times; and certain of the tension gears had to be replaced with tension gears of other sizes whenever the size of roving being drafted was changed. Also, the taper of the cones frequently has not been uniform or, at least, has not been such as to effect the desired extent of speed variation to the bobbins and to the bobbin carriage throughout the build.

It is therefore an important object of this invention to provide a compact apparatus for controlling the building of packages of strand material, which apparatus includes relatively few parts and permits the elimination of nearly all the elements described above, and which is readily adjustable, and easily maintained, and is much more accurate and efficient in its operation than prior apparatuses used for this purpose, and particularly, apparatuses of the type heretofore described in conjunction with a fly frame.

3,203,163 Patented Aug. 31, 1965 ice Some of the objects of the invention having been stated, other objects will appear as the description proceeds, when taken in connection with the accompanying drawings, in which FIGURE 1 is a rear elevation of a portion .of a fly frame, with parts thereof omitted for purposes of clarity, and showing a preferred embodiment of the control apparatus of the present invention in association therewith;

FIGURE 2 is an enlarged plan View, partially in section, taken substantially along line 22 in FIGURE 1;

FIGURE 3 is an enlarged side elevation, partially in section, taken substantially along line 33 in FIGURE 1, and being on the same scale as the structure shown in FIGURE 2;

FIGURE 4 is an enlarged elevation, partially in section and with portions broken away, being taken substantially along line 4-4 in FIGURE 2 and looking at the opposite side of the control apparatus from that shown in the lower left-hand portion of FIGURE 3;

FIGURE 5 is an enlarged vertical sectional view through the control apparatus taken substantially along line 5-5 in FIGURE 2 and showing the means for advancing the builder control elements and the speed control member of the apparatus;

FIGURE 6 is an enlarged fragmentary perspective view of the structure shown in the upper central portion of FIGURE 4 and wherein the traverse simulating tumbler occupies an intermediate position spaced between the builder control switches or elements;

FIGURE 7 is a fragmentary elevation similar to the upper portion of FIGURE 4 and showing the tumbler in solid lines occupying an over-running position, and also showing the tumbler in broken lines occupying a normal traverse reversing position;

FIGURE 8 is an enlarged partially exploded perspective view looking in the general direction of the arrow indicated at 8 in FIGURE 3 and showing a preferred means for connecting the link which controls the output speed variator or variable speed transmission to the control member or lever thereof;

FIGURE 9 is an enlarged front elevation of the control apparatus of the present invention, partially broken away, and looking substantially along line 9-9 in FIG- URE 3;

FIGURE 10 is a fragmentary elevation, partially in section, looking substantially along line 1010 in FIGURE 9 showing a preferred means for stopping the machine at the end of each winding cycle thereof and for determining the position at which various movable elements of the novel control apparatus come to rest at the end of a manual resetting or winding back operation following each winding cycle of the machine;

FIGURE 11 is a fragmentary vertical sectional view taken substantially along line 1111 in FIGURE 9 showing a concentrically mounted indexing collar or drum which is intrumental in imparting uniform stepwise movements to the builder control elements;

FIGURE 12 is an elevation of a typical package of textile strand material showing the shape thereof when the stepwise movement of the builder control elements is effected by the concentrically mounted drum of FIG- URE 11;

FIGURE 13 is a view similar to FIGURE 11, but wherein an eccentrically mounted indexing drum or cam is instrumental in effecting the stepwise movement of the builder control elements;

FIGURE 14 is an elevation of a typical package of textile strand material having rounded ends such as may be formed utilizing the indexing cam of FIGURE 13;

FIGURE 15 is a schematic diagram of the driving mechanism of the fly frame and the control apparatus of the present invention and also showing the electrical and fluid pressure circuitry in association therewith.

Generally, the present invention comprises an apparatus for controlling the building of strand packages on a winding machine of the character described. In the preferred embodiment of the invention, a tumbler reciprocates in timed relation to, or in synchronism with, a traversing mechanism which effects relative traversing movements between bobbins and strand guiding means. The tumbler reciprocates between a pair of spaced builder control elements preferably in the form of electric switches. Means are provided, in response to engagement of either builder control element, for (a) reversing the direction of movement of said traversing mechanism and said tumbler; (b) imparting a step in movement to at least one of the builder control elements a predetermined distance toward a point midway of the path of travel of said tumbler; and (c) for effecting a predetermined change in the relative speed between the bobbins and the strand guiding means whereby the length and/ or range of strokes of the traversing means and the relative speed between the bobbins and the strand guiding means are changed progressively throughout the winding cycle.

Referring more specifically to the drawings, with particular reference to FIGURES 1, 2 and 3, the numeral 20 broadly designates the main frame of a winding machine which is shown in the form of a roving frame or fly frame in this instance. Frame 20 includes a plurality of upright frame members or samsons, only three of which are shown indicated at 21, 22, 23 in FIGURE 1. Samsons 21, 22, 23 support a main horizontally disposed upper frame member or beam 24 on which the usual drafting rolls D are mounted in a well-known manner, said drafting rolls D being shown schematically in FIGURE 3.

Referring to FIGURE 15, the numeral 30 indicates the main drive shaft of the fly frame which has a pulley 31 thereon driven by an electric motor 32 through the medium of an endless belt 33 and a pulley 34 fixed on the shaft of motor 32. Drive shaft 30 has a gear 35 fixed thereon which is connected, by a diagrammatically illustrated gear train 36, to a gear 37 fixed on one of a pair of spindle shafts 40 (FIGURES 3 and 15) which are interconnected so as to be driven at the same speed and in the same direction by means not shown in the present drawings but being Well known in the art.

Each spindle shaft 40 drives a plurality of conventional spindles 41 on each of which is mounted a strand traverse guiding means embodied in a flyer 42. Only one of the spindles 41 and flyers 42 are shown in FIGURE 15, although several of the spindles 41 are shown in FIGURES 2 and 3 and two of the flyers 42 are shown in FIGURE 3.

Each spindle shaft 40 imparts rotation to each spindle 41 by means of bevel gears 43, 44. Roving or a similar strand of textile material R is fed to each flyer from the drafting rolls D (FIGURE 3). Each strand R passes through an opening 45 in the upper end of the corresponding flyer 42, then passes partially around said upper end of the flyer and through one of its arms 46, which is hollow, as is usual. The strand R then passes out of the lower end of the corresponding hollow arm 46 and passes around a conventional presser finger 47 and through the usual opening in the presser foot thereof to be Wound in the form of coils around an axially reciprocable carrier or bobbin 51 to form a package P of textile strand material.

As is usual, each bobbin or carrier 51 is positioned on a bolster or other support 52 having a gear 53 on its lower end which rests upon a bracket 54 (FIGURE 3) carried by a conventional bolster rail 55. The bolster rail I well-known manner so that they rotate at the same speed and in the same direction at all times.

One of the bobbin shafts 57 is connected to the variable output element or outer sleeve s of a conventional differential compound, broadlly designated at 60, by means of gears 61, 62 and an intervening gear train 63. Differential compound 60 is mounted on main drive shaft 30. Main drive shaft 30 is driven at a constant speed and its end opposite from drive pulley 31 has a direct drive connection to an auxiliary drive shaft 70 which replaces the usual top cone shaft of a fly frame, although the top cone shaft may be used in this instance. For purposes of clarity hereinafter, auxiliary drive shaft 70 will be termed as a top cone shaft, even though the usual top cone may be omitted therefrom.

Top cone shaft 70 is journaled in the upper portions of samsons 21, 22 of frame 20 (FIGURES 1 and 3) and is driven by main drive shaft 30 through the medium of a conventional gear train broadly designated at 71 and including gears '72, 73, 74, 75. Gears 72, 73, 74 are generally known as twist change gears. The direct drive is also transmitted from main drive shaft 30 to the shaft of the front bottom drafting roll D (FIGURE 3) by means of an endless sprocket chain 76 and sprocket wheels 77, 78 shown in phantom lines (schematically) in FIGURE 3, the sprocket wheels 77, 78 being mounted on top cone shaft 70 and on one end of the bottom foremost drafting roll of the group of drafting rolls D.

In conventional fly frames, top cone shaft 70 transmits roation directly to a bottom cone shaft 81 through the medium of elongate tapered cones provided on each of the shafts and which are engaged by a shiftable endless belt. However, the control apparatus of the present invention, to be later described, is interposed between shafts 70, 81 and, in the present instance, the usual cones and the interconnecting endless belt are omitted or, at least, they are not required. Accordingly, even though the bottom cone shaft 81 does not have a cone thereon, the shaft 81 is termed as a traverse drive shaft or bottom cone shaft, since its position and function correspond substantially to the position and function of the cone shafts of conventional fly frames.

Bottom cone shaft 81 is journaled in samson 21 and i a bearing 82 mounted on a gear box 83 suitably secured to samson 22. The end of shaft 81 disposed within gear box 83 (FIGURES 2 and 15) has a bevel gear 86 fixed thereon which is alternately engaged by a pair of spaced twin bevel gears 87, 88. Gears 87, 88 are fixed on a common sleeve 90 keyed for axial movement on an auxiliary traverse drive shaft 91 journale-d in gear box 83.

Auxiliary traverse drive shaft 91 has a bevel gear 92 fixed thereon which meshes with a bevel gear 93 fixed on a jack shaft 94. Jack shaft 94 also has a spur gear 95 fixed thereon which meshes with a gear 96 fixed on a lay shaft 97. Lay shaft 97 has a lay change gear 100 fixed thereon which meshes with one of a lay train of gears generally designated at 102. Lay train 102 also includes a gear 103 which is fixed on a conventional lifter shaft 104 journ-aled in the lower front portions of samsons 21, 22, 23 and other parts of the frame 20, not shown (FIG- URES 2, 3 and l5).

Lifter shaft 104 has one or more pinions 105 fixed thereon, each of which meshes with an arcuate lift rack 106 formed integral with a bobbin lifter arm 107 (FIGURES 1, 3 and 15). One of the lifter arms 107 is shown pivotally connected to samson 23 in the left-hand portions of FIGURES 1 and 3. Each lifter arm 107 imparts vertical reciprocation to bolster rail 55 through the medium of a roller 110 carried by bolster rail 55, as shown in the right-hand central portion of FIGURE 3.

As is well known, twin gears 87, 88 are alternately shifted into engagement with bevel gear 86 by means of a reversing or shifting lever 111. On conventional fly frames, the equivalent of shifting lever 111 is shifted to and fro by a complicated cam-operated shifting mecha nism. However, in the present invention, novel and improved means are provided for shifting lever 111 to and fro, as will be later described. In the present instance, shifting lever 111 is shown in FIGURES 2 and in the form of a bell crank and is pivotally mounted, as at 112, on a substantially horizontally disposed bracket 113 suitably secured to frame member or samson 22.

Bottom cone shaft 81, which may also be termed as a main traverse drive shaft, imparts rotation to bolsters 52 and the bobbins 51 thereon through the medium of the differential compound 60 (FIGURE 15), in a well-known manner. Accordingly, it will be observed in the righthand central portion of FIGURE 15 that the end of bottom cone shaft 81 opposite from twin gears 87, 88 has a gear 120 fixed thereon which is connected to a gear 121 by means of a gear train generally designated at 122. Gear 121 is fixed on the outer portion of an inner sleeve s1 of :the differential compound 60.

As heretofore stated, differential compound 60, in the upper right-hand portion of FIGURE 15, includes outer sleeve s (variable speed output element) on which gear 61 is fixedly mounted and also includes inner s eeve s-1 (variable speed input element) on the outer end of which gear 121 is fixedly mounted. As is usual, the two sleeves s, s-1 are connected through conventional planetary gearing (not shown) to a housing H fixed on main shaft 30 and serving as a constant speed input element.

Since the differential compound 60 is not peculiar to the present invention, a further more detailed description thereof is deemed unnecessary. Generally, the compound performs an addition of a variable r.p.m. component derived from the bottom cone shaft 81 and a constant r.p.-m. component coming directly from the main drive shaft 30, making the sum of the two components available for the drive of the bobbins. The ratios of the gears in the housing H are usually selected so that the variable rpm. component provides the winding rpm, and the constant r.p.m. component provides a component of the bobbin r.p.m. equal to the flyer r.p.m. In other words, housing H rotates at a constant speed while bottom cone shaft 81 imparts rotation to the inner sleeve s-l at a variable speed, and the sum of the constant speed of housing H and the variable speed of inner sleeve s1 determines the rotational speed of outer sleeve s and gear 61 thereon, thus determining the variable speed at which the bobbins 51 are rotated. Of course, the variations in speed of the inner sleeve s-1 are effected by the variations in speed imparted to bottom cone shaft 81 through the medium of the controlling apparatus of the present invention so that, in effect, the present apparatus determines the rotational speed of the bobbins 51 relative to the rotational speed of the flyers 42.

The parts heretofore described are conventional parts of a fly frame or roving frame and it is with such parts or the equivalent of such parts associated with fly frames and the like that the present invention is adapted to be associated.

As heretofore stated, the apparatus of the present invention obviates the necessity of providing a very large number of parts for effecting the required variable speed to the bobbins 51 and bolsters 52, along with the required rate of ascent and descent thereof, and the present invention also controls the build of the packages P on the bobbins 51 by determining the length of each successive upward and downward stroke of the bobbin carriage during reciprocatory traversing movement thereof. It will become apparent, as the description proceeds, that the principles of the present invention are also applicable to machines other than fly frames, or types of fly frames other than that disclosed herein, in which the bobbins remain in a fixed position and the flyers are strand guiding means reciprocate longitudinally of the bobbins. It will also become apparent. that the principles of the present invention are applicable to fly frames of the type whose bobbins are rotated at a constant speed throughout the build or winding cycle and whose flyers are rotated at progressively increasing speed to maintain the desired winding tension in the textile strands passing from the strand guide means embodied in the presser feet of the flyers 42 to the bobbins 51. The control apparatus of the present invention will now be described in detail.

DETAILED DESCRIPTION OF TRAVERSE AND TENSION CONTROL APPARATUS The apparatus of the present invention is in the form of a compact combination builder control mechanism and bobbin speed control mechanism and comprises a variable speed transmission unit or speed variator positioned above and adjacent to bottom cone shaft 81 (FIGURES 1-5, 9 and 15). Speed variator 135 may be of any well-known type suitable for the purpose, provided that it will effect the desired variation in output speed and may be .accurately controlled. For example, speed variator 135 may be of a type manufactured by the Zeromax Company, 2845 Harriet Avenue South, Minneapolis 8, Minnesota and as is disclosed in their Catolog No. ZM-562, to which reference is made for a more detailed description thereof.

The speed variator 135 is provided with a constant speed input shaft 136 and a variable speed output shaft 137 which is driven through intervening connections with input shaft 136. The output speed of shaft 137 is controlled by a speed control arm or lever 140 fixed on a speed control shaft 141 projecting from the housing of speed variator 135.

In practice, a speed variator corresponding to speed variator 135 was used having an output speed at shaft 137 of from zero to 80 revolutions per minute while the input shaft 136 was driven at a constant speed of approximately 1800 revolutions per minute. In other words, if speed control lever 140 was moved to the limit of its forward movement or to the right in FIGURE 3, shaft 137 would remain at a standstill and, if speed control lever 140 was moved to the limit of its rearward movement or to the right in FIGURE 3 with the input shaft 136 rotating at 1800 revolutions per minute, the output shaft 137 would rotate at 80 revolutions per minute. However, the speed control lever 140 is never moved to the zero output speed position and is never moved to its maximum output speed position during a winding cycle of the fly frame.

The top cone shaft 70 transmits continuous constant speed rotation to input shaft 136 of speed variator 135 during operation of the fly frame by means of a pair of sprocket wheels 145, 146 fixed on shafts 70, 136 and engaged by an endless sprocket chain 147 (FIGURES 1, 2, 3, 5, 9 and 15). Output shaft 137 of speed variator 135 transmits rotation to bottom cone shaft 81 by means of an endless sprocket chain 150 mounted on a pair of sprocket wheels 151, 152 fixed on the respective shafts 137, 81. The housing of speed variator 135 is suitably secured to a support or platform 155 overlying bottom cone shaft 81 and supported upon suitable front and rear corner posts or legs 156, 157 suit-ably secured to the floor F upon which the machine rests.

The speed control lever 140 of speed variator 135 is moved forwardly from a predetermined maximum speed position such as that shown in FIGURES to a predetermined minimum speed position in a stepwise manner and in substantially equal increments of predetermined length by means under control of the builder control mechanism of the present invention, the latter means being illustrated in the form of a ratchet mechanism in FIG- URES 2, 4 and 5, for example. To this end, one end of a pliable link cable or sprocket chain 160 (FIGURES 2 and 3) is pivotally and adjustably connected to a medial portion of speed control lever 140. The other end of link 160 is suitably secured to a collar or sleeve 161 adjustably secured on a transverse pilot shaft 162, as by means of a set screw a.

Collar 161 is preferably mounted on pilot shaft 162 in eccentric relation thereto so that it will impart uniform steps in movement to speed control lever 140 as uniform steps in movement are imparted to pilot shaft 162 by the ratchet mechanism. In the present embodiment, pilot shaft 162 is rotated approximately one-third of a revolution during each winding cycle and, since the point at which link 160 is connected to speed control lever 148 moves in an arcuate path generated about control shaft 141, instead of a straight linear path, if collar 161 was concentric with pilot shaft 162 the control lever 140 would be moved progressively decreasing distances during successive equal length steps in angular movement or rotation of pilot shaft 162 so that successive relative changes in the rotational speed of bottom cone shaft 81 and the bobbins 51 would not be uniform.

' Speed control lever 140 is yieldably urged toward its predetermined high speed starting position as by means of a tension spring 164, one end of which is connected to a spring anchor block 165 mounted for longitudinal adjustment along the upper portion of speed control lever 140 by means of a pair of set screws b (FIGURE 3). The rear end of spring 164 is connected to a suitable angle bracket 166 which extends downwardly in FIG- URES l and 3 and is suitably secured to platform 155.

As heretofore stated, the rear end of link 160 is pivotally and adjustably secured to a medial portion of speed control lever 140. To this end, it will be observed in FIGURE 8 that the rear end of link 160 has a threaded member or screw 170 connected thereto which loosely penetrates a clevis 171 pivotally mounted on a shoulder screw 172 whose reduced threaded portion is threaded into a block or slide 173. Slide 173 is mounted for longitudinal sliding movement on speed control lever 140 and is adjustably secured thereto by means of a pair of set screws 175. The free end of screw 170 has a lock nut 176 threaded thereon against which clevis 171 is urged by tension spring 164.

It follows, therefore, that the starting position or maximum speed position of speed control lever 140 may be accurately determined by adjusting lock nut 176 along screw 170 to correspondingly increase or decrease the effective length of link 160. Further, the extent to which the speeds of bottom cone shaft 81 and bobbins 51 are changed with each angular movement of pilot shaft 162 may also be accurately determined by adjusting slide 173 along control lever 140.

It is apparent that each increment in movement of speed control lever 140 may be increased by adjusting slide 173 toward speed control shaft 141 of speed variator 135, thereby increasing the relative changes in output speed imparted to the output shaft 137. Conversely, by adjusting slide 173 outwardly away from control shaft 141, the increments in angular movement imparted to lever 140 by the uniform angular movements of pilot shaft 162 are reduced to thereby reduce the extent of relative changes in the speed of output shaft 137, thus obviating the necessity of utilizing the conventional types of tension gears used heretofore for effecting changes in relative speeds of the bobbins of the extent required whenever a change in the size or character of the strand material being run is contemplated. Thus, adjustment of slide 173 along lever 140 determines the winding tension in the strands R in their movement from the presser feet 4'7 to the bobbins 51 (FIGURE 3).

Pilot'shaft'162 is journaled in a pair of bearing blocks 180, 181 (FIGURES 2 and 9) fixed on a pair of standards 182, 183 suitably secured to the corresponding front legs 156. Amedial portion of pilot shaft 162, to one side of speed variator 135, has a ratchet wheel 185 fixed thereon which is engaged by a feed pawl 186 and a hold-back pawl 187 (FIGURES). Feed pawl 186 is pivotally mounted, as at 190, on the lower end of a swing arm 191 pivotally mounted on tpilot shaft 162 adjacent ratchet wheel 185.

The free end of feed pawl 186 is normally urged into engagement with the teeth of ratchet wheel 185 by means of a tension spring 192, the lower end of which is mounted on a pin 193 carried by a medial portion of pawl 186. Spring 192 extends upwardly and its end opposite from pawl 186 is connected to a medial portion of swing arm 191.

Hold-back pawl 187 is pivotally connected, as at 195, to an upper portion of a pawl support bracket 196 which extends downwardly and then inwardly and is suitably secured to the lower surface of platform 155. A medial portion of pawl 187 also has a pin 197 projecting outwardly therefrom on which the upper end of a tension spring 200 is mounted. Tension spring 200 extends downwardly and is connected to a medial portion of support bracket 196, thus normally urging hold-back pawl 187 into engagement with the teeth of ratchet wheel 185.

In order that ratchet wheel 185 may be rotated in a reverse direction during the resetting of the control apparatus, by means to be hereinafter described, corresponding ends of cables or pliable elements 201, 202 (FIGURE 5) are connected to the pins 193, 197 projecting from the respective pawls 186, 187. Cables 201, 202 extend in generally radial directions away from ratchet wheel 185 and beneath and partially around respective grooved pulleys 203, 204 suitably journaled on pawl support bracket 196.

Cable 201 extends upwardly from pulley 203, engages pulley 204 and is connected to a medial portion of cable 202, as at 205 (FIGURES 5 and 9). Referring to FIG- URE 3, it will be observed that cable 205 extends upwardly, loosely penetrates a pawl release arm 208 and has an abutment 209 fixed on the upper end thereof and bearing against the upper surface of pawl release arm 208. Pawl release arm 208 is pivotally mounted, as at 210, on beam 24 of frame 20 and has an upwardly projecting handle portion 211 thereon, as shown in the upper portion of FIGURE 3. It is apparent that an operator may move downwardly handle portion 211 of pawl release arm 208 to thus move pawls 186, 187 out of engagement with ratchet wheel 185.

It is apparent that ratchet wheel 185 is advanced in a stepwise manner by means, to be later described, operatively associated with feed pawl 186 (FIGURE 5). Accordingly, manually operable means is provided for returning ratchet wheel 185, pilot shaft 152, cam or collar 161, speed control lever and builder control elements, to be later described, to the starting position upon pawls 186, 187 being released from engagement with ratchet wheel in the manner heretofore described. To this end, it will be observed in FIGURES 1, 2, 3 and 9 that pilot shaft 162 has a sprocket wheel 215 fixed thereon which is engaged by an endless sprocket chain 216. Sprocket chain 216 extends upwardly and engages a sprocket wheel 317 (FIGURES 1 and 3) fixed on a shaft 220 journaled in a bearing block 221. Bearing block 221 is fixed to beam 24. Shaft 220 has a hand wheel 222 fixed thereon which may be manually rotated in a clockwise direction in FIGURE 3, after pawls 186, 187 have been released from engagement with ratchet wheel 185, for returning ratchet wheel 135 to starting position at the end of each winding cycle.

In order to insure that the elements operatively connected to pilot shaft 162 are returned to a predetermined position which they should occupy at the start of each winding cycle, pilot shaft 162 has a collar 223 adjustably secured thereon as by means of a set screw 224 (FIGURE 10). Collar 223 has a radially extending limiting abutment 225 thereon which is adapted to engage a stop bracket 226 suitably secured to and projecting upwardly from platform 155.

During each winding cycle, it isapparent that abutment 225 moves away from stop bracket 226. In order to stop the fly frame at the end of each winding cycle, limiting abutment 225 moves to the knock-off position shown in broken lines in FIGURE 10 and engages and deacti- 9 vates or opens a normally active or closed knock-off switch 227 which then interrupts the flow of current to motor 32 through intervening electrical connections therewith to be later described (FIGURE 15).

The housing of knock-off switch 227 i adjustably secured to an arcuate switch support 230 (FIGURES 2, 3, 9 and 10), which overlies pilot shaft 162 and collar 223, and whose inner surface is generated substantially about the axis of pilot shaft 162. Switch support 230 has a longitudinally extending slot 231 therein which is loosely penetrated by a bolt 232 on switch 227 to facilitate angularly adjusting switch 227 relative to pilot shaft 162. Switch support 230 extends rearwardly and is suitably secured to the upper surface of the housing of speed variator 135.

A traverse simulator, broadly designated at 240 (FIG- URES 1-4, 6, 7, 9 and 15), to be later described, actuates the feed pawl 186 (FIGURE 5) through an electrically controlled fluid-pressure-operated means comprising a fluid pressure cylinder 241 which is suitably secured in substantially horizontal position on the platform 155 as by means of a screw 242 penetrating the head end of cylinder 241. Cylinder 241 is shown in FIGURE 5 as being of a single-acting type and has a piston 243 therein which is normally urged to retracted position against the base or bottom of cylinder 241 by means of a compression spring 244.

One end of compression spring 244 bears against the head of cylinder 241 and the other end of spring 244 bears against piston 243. Piston 243 has a connecting rod 245 extending therefrom and which is pivotally connected to the lower portion of swing arm 191 (FIGURE 5) by means of a connecting link 245'. The lengths of active and inactive strokes of piston rod 245 and pawl 186 are determined by a pair of spaced stroke-limiting abutments or collars 246, 247 .adjustably secured on the exposed portion of .piston rod 245 by respective set screws d, e. The abutments 246, 247 are adapted to alternately engage a stop block or angle clip 250 disposed therebetween and being suitably secured to platform 155.

As heretofore stated, slide 173 (FIGURES 3 and 8) may be adjusted longitudinally of speed control lever 140 for varying the extent to which the speed of output shaft 137 is decreased with each step in rotation imparted to ratchet wheel 185, shaft 162 and collar or cam 161. It will become apparent, as the description proceeds, that the relative displacement between the collars or abutments 246, 247 of FIGURE 5 also determines the extent to which speed control lever 140 is moved at the end of the corresponding traversing strokes of the bobbins 51 and carriage 55, since the displacement between abutments 246, 247 determines the amount of angular movement imparted to ratchet wheel 185, shaft 162 and collar 161 as each active stroke is imparted to feed pawl 186.

The base of fluid pressure cylinder 241 has one end of a conduit 251 connected thereto for communication with the interior of cylinder 241. The other end of conduit 251 (FIGURES 5 and 15) is connected to one side of an electromagnetically operated four-way valve or solenoid valve 252, the housing of which is suitably secured to platform 155. Although the fluid pressure circuit of FIGURE 15 is arranged for compressed air, it is apparent that it may be readily arranged for use with hydraulic pressure.

In the present instance, valve 252 has a pair of exhaust ports g. While coil 253 of valve 252 is deenergized, the movable core of valve 252 normally maintains communication between conduit 251 and exhaust port 1. While the core of valve 251 occupies the latter position, a conduit 254 connected to valve 252 is maintained in communication with exhaust port g. The end of conduit 254 opposite from valve 252 is connected to a conduit 255 leading from a suitable source of fluid pressure or comregulator valve 257 may be provided in conduit 255 between the compressed air source 256 and conduit 254.

When the core of valve 252 is rotated, by energization of coil 253 in a manner to be later described, communication is established between conduits 251, 254 so that fluid pressure then enters the base end of cylinder 241 and imparts an active stroke to piston 243, piston rod 245 and pawl 186, thus imparting a step in rotation to ratchet wheel 185, the length of which is determined by the distance abutment 246 moves with piston rod 245 before abutment 246 engages stop block 250. Upon the core of valve 252 returning to the open position, it is apparent that air is then exhausted from the base end of cylinder 241, thus permitting spring 244 to move piston 243, piston rod 245 and feed pawl 186 to the retracted position.

TRAVERSE SIMULATOR AND BUILDER CONTROL MECHANISM As heretofore stated, the active strokes of feed pawl 186 (FIGURES 5 and 15) are controlled by the traverse simulator 240. The traverse simulator 240 comprises a reciprocating tumbler 260 which reciprocates in timed relation to or in synchronism with vertical reciprocation of bobbin carriage 55 and between a pair of spaced builder control elements or switches 261, 262 (FIGURES 4, 6, 7 and 15) carried by suitable bifurcated builder blocks 263, 264 which are supported upon and guided for relative movement upon an elongate traverse plate 265 extending substantially parallel to, but being spaced from, the path of travel of tumbler 260. In this instance, it will be observed in FIGURE 6 that plate 265 is provided with a pair of opposed longitudinally extending slots 266, 267 therein in which inverted substantially T-shaped portions 270, 271 of the respective blocks 263, 264 are fitted for sliding movement.

During operation of the fly frame, at least one of the builder control elements 261 or 262 is moved toward a point substantially midway of the path of travel of tumbler 260 upon tumbler 260 moving into operative relationship with one or the other of the builder control elements or switches 261, 262. Although the switches 261, 262 are shown as being carried by the respective blocks 263, 264, it is apparent that the switches 261, 262 may be mounted on the tumbler 260, without departing from the spirit of the present invention. The means for imparting stepwise movement to the builder control elements 261, 262 will be later described.

The tumbler 260 has an elongate rigid upper portion 274 thereon which is connected to a medial portion of the upper run of an endless pliable element 275, as by a pair of screws 276. Endless pliable element 275 is pref erably in the form of a sprocket chain, as shown in FIG- URES 4, 6 and 7 and is mounted on a plurality of sprocket wheels 280-284. Sprocket wheels 280-283 are idlers and sprocket wheel 284 is fixed in axial relation to a relatively larger driven sprocket wheel 286. Sprocket wheel 286 has an endless sprocket chain 287 mounted thereon which also engages a sprocket wheel 290 fixed on lifter shaft 104 (FIGURES 3 and 9).

Sprocket wheels 284, 286 are fixed on or formed integral with a common hub h (FIGURE 9) journaled on a shoulder bolt or stub shaft 291 fixed to an intermediate upright frame member 293 extending between and being suitably secured to elongate plate 265 and platform (FIGURES 4 and 9), thus supporting traverse plate 265 in spaced relation above pilot shaft 162.

The front end of traverse plate 265 has a standard 292 suitably secured thereto (FIGURES 4 and 9), on the upper portion of which sprocket wheel 280 is suitably journaled. The rear end of traverse plate 265 has the medial portion of a standard 294 suitably secured thereto on which respective upper and lower sprocket wheels 281, 282 are suitably journaled. Sprocket wheel 283 is journaled on a shaft or shoulder screw 295 (FIGURE 4), one reduced end portion of which loosely penetrates a 1 1 slot 296 provided in the upright frame member 293 (FIG- URE 4). The reduced end of shaft 215 has a nut 297 threaded thereon for locking shaft 295 in the desired adjusted position along slot 296 for maintaining the desired amount of tension in sprocket chain 275.

In the illustrated embodiment of the invention, means are provided for simultaneously moving both of the builder control elements or switches 261, 262 toward each other, or toward midway of the path of travel of tumbler 260, each time tumbler 260 engages either of the switches 261, 262 during normal operation of the fly frame. To this end, it will best be observed in FIGURE 7 that the inverted substantially T-shaped portions 270, 271 of builder control blocks 263, 264 have corresponding ends of respective pliable elements or sprocket chains 300, 301, suitably connected thereto and extending toward and past each other where they pass over respective rollers 302 (only one of which is shown in FIGURE 7) journaied on a common shaft 303 suitably secured to upright frame member 293 of traverse simulator 240.

Sprocket chain 300 extends substantially halfway around the corresponding roller 302 and both sprocket chains 300, 301 extend forwardly and beneath a wheel or drum 305 (FIGURES 7 and 11) fixed on pilot shaft 162 as by means of a set screw i. Corresponding ends of the sprocket chains 300, 301 are suitably secured to the periphery of drum 305, as at i. Drum 305 is shown as being circular and concentric with respect to pilot shaft 162 in FIGURES 7 and 11 so that uniform movement is imparted to the two builder control elements 261, 262 in proportion to each uniform step imparted to ratchet wheel 185 by feed pawl 186 (FIGURE 5).

It is apparent that, since pilot shaft 162 is rotated in successive steps of equal length determined by the length of the successive active strokes of feed pawl 186 (FIG- URE 5), the drum 305 (FIGURES 7 and 11) imparts successive steps of equal length to the builder control elements 261, 262. Thus, since the relative positions of the builder control elements 261, 262 determines the range and length of the strokes of the bobbin carriage 55 and both of the builder control elements 261, 262 move toward each other with each successive step imparted thereto, the resulting packages of textile strand material have substantially straight tapered ends thereon such as are indicated at T, T on the package P shown in FIGURE 12. In FIGURE 14, a strand package P-1 is shown which is similar to the strand package P of FIGURE 12, but wherein it is provided with rounded ends T-1, T-l'.

In order to produce the package P1, it is apparent that successive strokes of the bobbin carriage 55 must be shortened, with respect to preceding strokes, progressively increasing amounts rather than being shortened uniform amounts in the course of successive reciprocations of bobbin carriage 55. Accordingly, in order to produce the package P-1, shaft 162 is shown in FIG- URE 13 provided with a drum 305' which may be circular or may be irregularly shaped and which is shown positioned in eccentric relation to pilot shaft 162.

Since pilot shaft 162 is rotated in steps of equal length, when the drum 305 of FIGURE 11 is replaced by the eccentric drum or cam 305 of FIGURE 13, the eccentric drum 305' imparts stepwise movement to sprocket chains 300, 301 and builder control elements 261, 262 in steps of gradually increasing length. Since the builder control elements 261, 262 control the reversing of the direction of movement of bobbin carriage 55 at the end of each stroke thereof in each direction, by mean to be later described, it follows that the strokes .of the bobbin carriage 55 are also gradually reduced in length in successively increasing amounts for forming the package P-l of FIGURE 14.

In order to increase or decrease the included angularity of the tapered portions T, T of packages P of FIGURE 12 relative to the axes thereof as they are being wound, the displacement between the limiting abutments 246, 247

or, at least, the displacement between limiting abutment 246 and stop block 250 (FIGURE 5) may be correspondingly decreased or increased. While adjustment of the limiting abutments 246, 247 along piston rod 245 is the most convenient method of predetermining the angularity of tapered ends T, T of the package P of FIGURE 12 during the build, it is apparent that drum 305 may be replaced by a drum of larger or smaller diameter to also respectively increase or decrease the angularity of the tapered ends of packages P with respect to their axes.

It should be noted that, whenever the displacement between abutment 246 and stop block 250 is increased or decreased, the slide 173 (FIGURES 3 and 8) should be adjusted outwardly or inwardly along speed control lever to insure that the relative speeds between the fiyers and the rotating bobbins are so maintained as to maintain the desired amount of winding tension in the strands passing from the flyers to .the bobbins.

In order to maintain taut the pliable elements or sprocket chains 300, 301 (FIGURE 7) during each winding cycle and to also cause the builder control elements 261, 262 to return to a predetermined starting position following each winding cycle as the operator rotates the pilot shaft 162 in the reverse direction in the manner heretofore described, the lower portions 270, 271 of the builder control blocks 263, 264 have the proximal ends of respective tension springs 310, 311 suitably connected thereto. Springs 310, 311 extend outwardly and are connected to spring anchors or pins 312, 313 (FIGURES 6 and 7) extending across the ends of the slots 266, 267 and being suitably secured to the traverse plate 265.

Since lifter shaft 104 is operatively connected to both the tumbler 260 and the bobbin carriage 55, it follows that tumbler 260 serves to reverse the direction of traverse of bobbin carriage 55. In this regard, it should be noted that each time tumbler 260 engages each of the builder control elements or switches 261, 262, it motivates an inactive and then an active stroke of feed pawl 186 and also motivates the shifting of one of the twin gears 87, 88 (FIGURE 2) into engagement with gear 86 while shifting the other of the twin gears out of engagement with gear 86 to reverse the direction of rotation of shafts 91, 97, 104 and the direction of movement of bobbin carriage 55.

It will be observed in the lower right-hand portion of FIGURE 15 that the builder control switches 261, 262 normally close a series circuit to the coil 253 of solenoid valve 252, the switch 261 being so arranged as to normally maintain contact between a pair of conductors 315 and k while the switch 262 normally maintains contact between conductor k and a conductor 316 leading to one side of the coil 253 of solenoid valve 252. The other side of coil 253 has a lead conductor 317 leading therefrom. The conductors 315, 317 are connected to a suitable source of electrical energy embodied in a plug 320. Thus, builder control switches 261, 262 normally maintain the coil 253 energized so the core of valve 252 maintain scommunication between conduits 251, 254 to thus maintain tre piston rod 245 (FIGURES 5 and 15) and pawl 186 in extended position.

However, whenever either of the switches 261, 262 is engaged by tumbler 260, it breaks contact between conductors 315, k or conductors k and 316 to de-energize the coil 253 and permit the core of valve 252 to move so as to interrupt the flow of compressed air into cylinder 241 while permitting compressed air to be exhausted from cylinder 241 through conduit 251, valve 252 and discharge port 7. Spring 244 then retracts piston rod 245 and pawl 186 so that, upon subsequent movement of tumbler 260 out of engagement with the corresponding builder control switch 261 or 262, coil 253 is energized to effect an active stroke to the feed pawl 186 and impart an inward step to each of the builder control elements or switches 261, 262 toward a point midway of the path of travel of tumbler 260, It should be noted that the latter arrangement insures that each step in movement imparted to the switches 261, 262 occurs following the movement of tumbler 260 out of engagement with the corresponding switch in each instance, although the operation of the feed pawl 186 is responsive to engagement of tumbler 260 with either of the builder control switches 261, 262.

In order to reverse the direction of movement of bobbin carriage 55 and tumbler 260 each time tumbler 260 engages one of the switches 261 or 262, means are pro-' vided for energizing the coils 325, 326 of respective electromagnetically operated valves or solenoid valves 327, 328 to alternately introduce fluid pressure or compressed air into opposite ends of a builder shifting, double-acting, fluid pressure cylinder 331 operatively connected to the shifting lever 111 to thus reverse the position of twin gears 87, 88 each time either of the switches 261, 262 is engaged and actuated by tumbler 260. To this end, it will be observed that, when switch 261 is engaged and actuated by tumbler 260, this not only breaks contact between conductors 315, k, but establishes contact between conductor 315 and a conductor 333 leading to one end of the coil 325. The other end of coil 325 has a conductor 334 leading therefrom to a medial portion of lead conductor 317, thus completing the circuit to coil 325 whenever switch 261 is actuated by tumbler 260.

Whenever switch 262 is actuated by tumbler 260, this interrupts contact between conductors k, 316 and establishes contact between a pair of conductors 335, 336. Conductor 336 leads from builder control switch 262 to lead conductor 317, and conductor 335 leads from builder control switch 262 to one side of the coil 326 of solenoid valve 328. The other side of coil 326 has a conductor 337 leading therefrom to a medial portion of lead conductor 315. It is thus seen that the coil 326 of solenoid valve 328 is energized each time tumbler 260 engages and actuates switch 262.

The elements 327, 328 are shown in the form of fourway valves provided with respective pairs of exhaust ports m, n and p, q (FIGURE 15). Valve 327 has conduits 340, 341 connected to opposite sides thereof. One side of valve 328 has conduit 255 connected thereto, and the other side of valve 328 has a conduit 342 connected thereto. Conduit 340 is connected to conduit 255, Cor responding-ends of conduits 341, 342 are communicatively connected to respective head and base ends of the double-acting cylinder 331 for communication therewith.

As best shown in FIGURE 2, cylinder 331 is suitably pivotally secured to the bracket 113, as by means of an angle bracket 343. Cylinder 331 has a piston 343 mounted for longitudinal movement therein and to which the inner end of.a piston rod 344 is fixedly connected. Piston rod 344 slidably penetrates the head of cylinder 331 and is pivotally connected to one arm of bell crank 111, as at 345. Whenever the coils 325, 326 of valves 327, 328 are energized, they establish communication between the respective pairs of conduits 340, 341 and 255, 342. However, when the tumbler 260 moves out of engagement with the respective switches 261, 262, the cores of valves 327, 328 return to inoperative position in which communication is established between the exhaust ports in, n of valves 327, 328 and the respective conduits 341, 342.

It is thus seen, that each time tumbler 260 engages and actuates builder control switch 261 (FIGURES 5, 6, 7 and 15), spring 244 (FIGURE retracts piston rod 245 and feed pawl 186, and the core of valve 327 is rotated, through energization of coil 325, to establish communication between conduits 340, 341 and introduce compressed air or fluid pressure into the head end of cylinder 331 so the twin gears 87, 88 then occupy the position shown in FIGURES 2 and relative to gear 86.. As heretofore stated, this reverses the direction of movement of lifter shaft 104, bobbin carriage 55 and tumbler 260 so that tumbler 260 moves out of engagement wth builder control switch 261 and thus causes compressed air to enter the base end of cylinder 241 to impart an active stroke to feed pawl 186. At the same time, since the contact between conductors 333, 357 is then broken, the core of valve 327 returns to its normal inactive or closed position in which it permits air to subsequently be exhausted from the head end of cylinder 331 through exhaust port 111. Thus, the direction of rotation of shaft 104 is reversed and the direction of movement of bobbin carriage 55 and tumbler 261 is reversed.

As tumbler 260 then moves from left to right in FIG- URE 15, it moves out of engagement with switch 261 and an active stroke is then imparted to pawl 186 in the manner heretofore described to move the builder control elements or switches 261, 262 inwardly toward each other a predetermined distance. When tumbler 260 subsequently engages and actuates switch 262, feed pawl 186 is momentarily retracted in the manner here tofore described as the coil 326 of solenoid valve 328 is energized and causes the core of valve 328 to move from the inactive position to the position in which it is shown in FIGURE 15, thus introducing compressed air into the base end of cylinder 331 (FIGURES 2 and 15). It is apparent that this causes bell crank 111 to move in a counterclockwise direction in FIGURES 2 and 15 as air is exhausted from the head end of cylinder 331 to thus shift the twin gears 87, 88 so that gear 88 engages gear 86 and gear 87 moves out of engagement with gear 86, thus completing a cycle in the operation of the builder control elements 261, 262. It is apparent that many cycles of the builder control elements 261, 262 are repeated during each complete winding cycle.

As heretofore stated, upon the completion of each winding cycle, in which all the packages P are filled with strand material, limiting abutment 225 (FIGURE 10) moves into engagement with and opens normally closed knock-off switch 227. Referring to the upper portion of FIGURE 15, it will be observed that knock-off switch 227 normally maintains contact between a pair of conductors 350, 351. Conductor 351 extends from switch 227 to one end of the coil of a main electromagnetic relay 352, to the same end of which a conductor 353 is also connected. The other end of the coil of relay 352 has a conductor 354 leading therefrom.

The end of conductor 353 remote from relay 352 is connected to one side of a normally open, manually operable push-button switch 356, from the other side of which a conductor 357 extends. Corresponding ends of conductors 354, 357 are connected to a suitable source of electrical energy embodied in a plug 360. Conductor 354 has a conductor 361 leading therefrom to one side of electric motor 32. The other side of motor 32 has a conductor 362 leading therefrom to one side of a normally open switch 363 of relay 352. The other side of switch 363 has a conductor 364 leading therefrom to a medial portion of conductor 357. Relay 352 also includes a normally open switch 365 which, when closed, establishes contact between a pair of conductors 366, 367. The end of conductor 366 opposite from switch 365 is connected to conductor 364, and the end of conductor 367 opposite from switch 365 is connected to one side of a normally closed safety switch 370 which is in series with a second normally closed safety switch 371. Switches 370, 371 are interconnected by a conductor 372 and the side of switch 371 remote from switch 370 is connected to the end of conductor 356) remote from knock-off switch 227.

When starting the fly frame, manually operable push button switch 356 is closed by an operator so that current flows from the source 360 through conductor 357, switch 356, conductor 353, the coil of relay 352, and conductor 354 back to the source of electrical energy 360, thus energizing the coil of relay 352. Thereupon, switches 363, 365 move to closed position to energize electric motor 32 as current flows from lead conductor 357 through con- 1 5 ductor 364, switch 363, conductor 362, electric motor 32 and conductor 361 to lead conductor 354.

Although the operator releases switch 356 after motor 32 is energized, current normally continues to flow through the coil of relay 352, owing to the fact that current flows from lead conductor 357 through conductors 364, 366, switch 365, conductor 367, switch 370, conductor 372, switch 371, conductor 350, knock-off switch 227, conductor 351, the coil of relay 352 and conductor 354. It follows therefore that, upon any one or more of the three switches 370, 371, 227 being opened, the flow of current through the coil of relay 352 is interruped, thus permitting switch 363 to open to stop electric motor 32 and thereby stop the fly frame.

It has already been stated that knock-off switch 227 is opened at the end of each winding cycle by engagement of limiting abutment 225 therewith. Referring to FIGURES 6 and 7, it will be observed that the housings of safety switches 370, 371 are suitably secured to the respective builder control blocks 263, 264, with their actuating buttons or push buttons being disposed on substantially higher planes than the push buttons of the respective builder control switches 261, 262. In other words, the push buttons or plungers of switches 370, 371 are positioned more closely adjacent the upper run of sprocket chain 275 than are the plungers or push buttons of the builder control switches 261, 262. Thus, in the event of a malfunction of the reversing mechanism in the left-hand portion of FIGURE 2 or a malfunction of any other operating part of the fly frame which might tend to cause the bobbin carriage 55 to over-run the desired range and/ or length of stroke thereof in either direction, it is apparent that this will also tend to cause the tumbler 260 to move beyond the limits permitted by engagement thereof with the builder control switches 261, 262.

By way of comparison, it will be observed in the righthand portion of FIGURE 7 that tumbler 260 is shown in phantom or broken lines in the normal position that it would occupy at the end of a stroke in movement thereof from left to right. It should be noted that the broken line illustration of the tumbler 260 in the right-hand portion of FIGURE 7 shows the tumbler in engagement with the plunger of push button of the right-hand builder control switch 262.

On the other hand, the tumbler 260 is shown in solid lines in the left-hand portion of FIGURE 7 in that position to which it may be moved in the event that engagement of the plunger of builder control switch 261 thereby does not cause bobbin carriage 55 to reverse its direction of movement. Owing to the fact that at least the upper run of sprocket chain 275 is pliable, it will be noted that when there is a tendency for the tumbler 260 to continue movement from left to right in FIGURE 7 after its lower portion has engaged the plunger of switch 261, the plunger 260 then pivots against the plunger of builder control switch 261 and its upper portion is tilted toward the direction of movement of sprocket chain 275 and thus engages the plunger of safety switch 270, thus breaking the circuit to the coil of relay 352 (FIGURE 15) and thereby interrupting the flow of current to electric motor 32 to stop the fly frame.

It is apparent that the tumbler 260 will also tilt in the direction of movement of the upper run of sprocket chain 275 with movement thereof from left to right in FIGURE 7 in the event of failure of the shifting mechanism to respond to reverse the direction of movement of tumbler 260 through some malfunction of the fly frame so that tumbler 260 would then tilt to the right after its lower portion has engaged the plunger of the right-hand or rear builder control element or switch 262 in FIGURES 4, 6 and 7 so that, here again, tumbler 260 will then engage the plunger'of safety switch 371 to interrupt the flow of current through electric motor 32 and thereby stop the fly frame.

It is thus seen that I have provided a simple compact and efiicient apparatus, including a traverse simulator having a tumbler thereon movable between a pair of spaced control elements which accurately control the relative traversing movements and the relative rotational speeds between the bobbins and flyers or other textile strand guiding means of a winding machine, and which eliminates many of the conventional cooperating parts used heretofore for these purposes to thereby avoid the accumulations of lost motion inherent in the conventional cooperating parts and to reduce the cost and time involved in maintenance thereof as well as obviating the necessity of replacing tension gears when different sizes or types of strands are to be wound on the machine, since the present apparatus obviates the need for such tension gears.

It is seen further that the present apparatus is readily adjusted to vary the angle or shape of the tapered ends formed on the strand packages, simply by adjusting the abutments 246, 247 on piston rod 245 (FIGURE 5) relative to stop member 258- and ratchet wheel 185, or by varying the size or shape of the drum to which chains 3%, 301 are connected (FIGURE 4), and wherein the length and diameter of the strand packages being wound may be varied simply by adjusting the angular positions of limiting abutment 225 and knock-off switch 227, respectively (FIGURES 9 and 10), aboutpilot shaft 162 and relative to stop bracket 226.

In the d-raWings and specification there has been set forth a preferred embodiment of the invention and, although specific terms are employed, they are used in a generic and descriptive sense only and not for purposes of limitation, the scope of the invention being defined in the claims.

I claim:

1. Apparatus for controlling the building of packages of strand material on a winding machine having rotating bobbins for receiving thereon the strand material, strand guide means adjacent each bobbin, a reciprocable traverse mechanism for imparting relative axial movement between said guide means and said bobbins, and means shiftable between first and second positions for reversing said traverse mechanism at the ends of strokes thereof in respective first and second directions; said apparatus comprising (a) a frame,

(b) first and second spaced switches movably mounted on said frame,

(c) a tumbler movable between and adapted to engage and actuate said switches in alternation,

((1) means operatively associated with said traverse mechanism for reciprocating said tumbler in synchronism therewith,

(e) first and second electrically operable means for shifting said shiftable means to the respective first and second positions and being electrically connected in parallel to the respective first and second switches whereby the direction of movement of said traverse mechanism is reversed each time said tumbler engages and actuates each of said switches, and

(f) means responsive to each engagement of said tumbler with at least one of said switches for imparting a step in movement to at least one of said switches toward said tumbler thereby to vary correspondingly the rangeof movement of said traverse mechanism and said tumbler relative to said frame.

2. In a winding machine for winding strand material onto bobbins and including a continuously driven shaft, a strand traversing means, means for producing relative traversing movement between said bobbins and said traversing means and including a reciprocating element reciprocating in timed relation to said relative traversing movement between said bobbins and said traversing means, and shiftable means for reversing the direction of movement of said means producing relative traversing movement at the end of each stroke thereof in each direction; the combination therewith of (a) a speed variator interposed between and operatively interconnecting said shaft and said bobbins for imparting rotation thereto,

(1) a movable speed control member operatively connected to said variator for varying the output speed thereof,

(b) a tumbler operatively connected to and being reciprocated by said reciprocating element,

(c) a pair of first and second spaced builder control elements straddling said tumbler and being independently engageable in alternation by said tumbler,

(d) means responsive to engagement of one of said builder control elements by said tumbler for shifting said shiftable means in one direction,

(e) means responsive to engagement of the other of said builder control elements by said tumbler for shifting said shiftable means in the opposite direction,

(f) means operable automatically for moving at least one of said control elements in at least one direction in response to engagement of at least one of said builder control elements by said tumbler, and

(g) means operatively connecting said last-named means (f) to said speed control member for imparting movement thereto upon moving said one of said control elements to change correspondingly the speed of the bobbins.

3. In a Winding machine for winding strand material onto bobbins and including a continuously driven shaft, a strand traversing means, means for producing relative traversing movement between said bobbins and said traversing means and including a reciprocating element reciprocating in timed relation to said relative traversing movement between said bobbins and said traversing means, and shiftable means for reversing the direction of movement of said means producing relative traversing movement at the end of each stroke thereof in each direction; the combination therewith of (a) a speed variator interposed between and operatively interconnecting said shaft and said bobbins for imparting rotation thereto,

(1) a movable speed control member operatively connected to said variator for varying the output speed thereof,

(b) a tumbler operatively connected to and being reciprocated by said reciprocating element,

(c) a pair of first and second spaced builder control elements straddling said tumbler and being independently engageable in alternation by said tumbler,

(d) means responsive to engagement of one of said builder control elements by said tumbler for shifting said shiftable means in one direction,

(e) means responsive to engagement of the other of said builder control elements by said tumbler for shifting said shiftable means in the opposite direction,

(f) means operatable automatically for moving at least one of said control elements in at least one direction in response to engagement of at least one of said builder control elements by said tumbler, and

(g) means responsive to engagement of at least one of said builder control elements by said tumbler for imparting a relatively small step in movement to said speed control member to reduce correspondingly the speed of said bobbins.

4. A control apparatus adapted to be positioned between the top and bottom cone shafts of a fly frame in lieu of the conventional cones and connecting belt thereof and to replace the conventional builder motion thereof, said fly frame having a reciprocating bobbin carriage lifter shaft and shiftable reversing means connecting the bottom cone shaft with said lifter shaft; said control apparatus comprising (a) a variable speed transmission having an input shaft adapted to be driven by said top cone shaft,

18 an output shaft adapted to drive said bottom cone shaft, and a movable control lever for varying the speed of said output shaft relative to said input shaft,

(b) a pilot shaft,

(c) a pliable link connected to and adapted to be coiled about said pilot shaft,

(d) means pivotally and adjustably connecting said link to said lever,

(e) a pair of spaced movable control elements,

(f) a tumbler adapted to be operatively connected to said lifter shaft for reciprocable movement between said control elements,

(g) means responsive to movement of said tumbler into engagement with each of said control elements for imparting a step in rotation to said pilot shaft to thereby impart a step in movement to said control lever,

(h) means responsive to movement of said tumbler into engagement with each of said control elements adapted for shifting said reversing means to reverse the direction of movement of said lifter shaft and said tumbler, and

(i) means operatively connecting said control elements to said pilot shaft for imparting predetermined stepwise movement to said control elements relative to said tumbler with successive steps in rotation of said pilot shaft.

5. A structure according to claim 4, in which said means (g) comprises (1) a ratchet wheel fixed on said pilot shaft (2) a pawl engaging said ratchet wheel (3) electrically operable means for imparting active and inactive strokes to said pawl, and

(4) switch means electrically connected to said electrically operable means and being actuable by engagement of said tumbler with each control element for actuating said electrically operable means.

6. In a winding machine having bobbin carriage means for supporting rotating bobbins thereon, strand guide means for directing strands to said bobbins, mechanism including a lifter shaft for reciprocating one of said means relative to the other of said means, a constant speed drive shaft, an auxiliary shaft operatively connected to one of said means for rotating the same, a variable speed transmission interposed between and operatively connected to said drive shaft and said auxiliary shaft, and shiftable reversing means operatively connecting said auxiliary shaft to said lifter shaft; means for controlling said shiftable, reversing means comprising (a) a traverse simulator including (1) an endless pliable element,

(2) means supporting and guiding at least a portion of said pliable element in a substantially straight path,

(3) means drivingly connecting said lifter shaft to said pliable element,

(4) a tumbler carried by said portion of said pliable element,

(b) a pair of first and second spaced builder control elements positioned astraddle said tumbler,

(c) means responsive to engagement of said tumbler with said first control element for shifting said shiftable reversing means in one direction and being responsive to engagement of said tumbler with said second control element for shifting said shiftable reversing means in the opposite direction whereby the direction of rotation of said lifter shaft and the direction of movement of said tumbler is reversed each time said tumbler engages each control ele ment, and

(d) means responsive to engagement of said tumbler with each control element for imparting a step in movement to each of said control elements toward said tumbler to correspondingly reduce the lengths 12% of successive movements of said tumbler and said lifter shaft.

7. A structure according to claim 6, wherein said machine is provided with means for driving said drive shaft, and

(e) means responsive to any tendency for movement of said tumbler beyond either of said control elements upon engaging the same for interrupting said last-named driving means and stopping said drive shaft.

8. A structure according to claim 6, in which said responsive means ((1) comprises (1') a support plate spaced from and extending substantially parallel to said portion of said pliable element and on Which said control elements are movably mounted,

(2) means yieldably urging said control elements away from each other,

(3) roller means positioned in fixed relation to said support plate at a point spaced between said control elements,

(4) first and second pliable members fixedly connected to said control elements and extending inwardly in engagement with said roller means,

(5) a pilot shaft adjacent one of said control elements,

(6) a drum on said pilot shaft to which corresponding ends of said pliable members extend from said roller means and to which said pliable members are secured,

(7) a ratchet mechanism for imparting stepwise angular movement to said pilot shaft, and

(8) means responsive to engagement of each control element by said tumbler for actuating said ratchet mechanism.

9. A structure according to claim 8, in which said drum is in the form of a cam eccentrically mounted on said pilot shaft.

10. A structure according to claim 8, in which said ratchet mechanism (7 comprises (a) a ratchet wheel fixed on said pilot shaft,

(b) an axially movable bar adjacent said ratchet wheel,

(') a pawl movable with said bar and yieldably engaging said ratchet wheel,

(d) means adjustably limiting the extent of each active stroke of said bar and said pawl relative to said pilot shaft to thereby determine the length of each successive step in angular movement of said pilot shaft and to thereby determine the extent of each movement imparted to said control elements by said pliable members, and said responsive means (8) comprising means for successively imparting an inactive stroke and then an active stroke to said bar and said pawl in response to engagement of each control element by said tumbler.

11. A structure according to claim 10, including manually operable means remote from said pilot shaft and operatively connected thereto for turning back said pilot shaft and said ratchet wheel to a predetermined starting position upon completion of each winding cycle in the operation of the machine, and manually operable means, adjacent said first-named manually operable means, for moving and maintaining said pawl out of engagement with said ratchet wheel while the same is being turned back.

12. A structure according to claim 8, in which said variable speed transmission includes a movable speed control arm for varying the speed of said auxiliary shaft relative to said constant speed drive shaft,

(e) a collar fixed on said pilot shaft adjacent said arm,

(f) a second pliable element fixed to the periphery of said collar and extending therefrom to said speed control arm, and

(g) means connecting said second pliable element to said speed control arm whereby said control arm is moved in a stepwise manner with stepwise angular movement of said pilot shaft. 13. A structure according to claim 12, in which said speed control arm consists of a pivoted lever, and said means (g) comprises (1) a slide block adjustably secured on said lever for adjustment toward and away from the pivot point of said lever,

(2) a clevis on said slide block,

(3) means on said second pliable element loosely penetrating said clevis, and

(4) means for adjustably varying the effective length of said second pliable element between said lever and said collar whereby the rate of successive relative changes in the speed of said auxiliary shaft may be determined by adjusting said slide block relative to said lever.

14. In a machine for winding textile strands onto rotating bobbins and including strand guide means, and a 20 reversible traverse mechanism effecting relative axial movement between said guide means and said bobbins, apparatus for controlling said mechanism comprising (a) a pair of spaced first and second control elements,

(b) a tumbler operatively connected to said traverse mechanism and being reciprocatorily movable thereby into alternating operative relation with said first and second control elements,

(0) electrically operable means responsive to movement of said tumbler into operative relation with each of said control elements for reversing the direction of relative movement between said guide means and said bobbins, and

(d) said first and second control elements comprising respective first and second normally inactive electric switches.

15. In a machine for winding textile strands onto rotating bobbins and including strand guide means, a driven constant speed shaft, and a reversible traverse mechanism effecting relative axial movement between 0 said guide means and said bobbins, apparatus for controlling said mechanism comprising (a) a tumbler movable in a predetermined path in proportionally fixed relation with the relative movement of said guide means and said bobbins,

(b) a pair of spaced first and second control elements defining opposite ends of the path of travel of said tumbler,

(c) means responsive to movement of said tumbler into operative relation with each of said control elements for reversing the direction of movement of said tumbler and the direction of relative movement between said guide means and said bobbins,

((1) means responsive to each movement of said tumbler away from at least one of said control elements for imparting a predetermined amount of movement to said control elements relative to said tumbler in which at least one of said control elements moves toward said tumbler to thereby vary successive relative movements between said guide means and said bobbins while varying successive movements of said tumbler along said path,

(e) said reversible traverse mechanism including a shifting element shiftable between first and second positions for reversing the direction of relative axial movement effected between said guide means and said bobbins,

said responsive means (c) comprising 1) a fiuid-pressure-operated cylinder operatively connected to said shifting element for shifting the same between said first and second positions,

(2) first and second electrically operable means for admitting fluid pressure into respective first and second ends of said cylinder in alternation,

(3) normally inoperative first and second switches 5 on said respective first and second control elements and being actuated each time said tumbler moves into operative relation with the respective control elements, and

(4) means electrically connecting said first and second switches to the respective first and second electrically operable means for activating the same upon said tumbler moving into operative relation with the respective first and second control elements whereby said cylinder shifts said shifting element to and fro with successive movements of said tumbler into operative relation to said control elements.

16. In a machine for winding textile strands onto rotating bobbins and including strand guide means, and a reversible traverse mechanism elfecting relative axial movement between said guide means and said bobbins, said machine including a driven constant speed shaft; apparatus for controlling said mechanism comprising (a) a tumbler movable in a predetermined path in proportionally fixed relation with the relative movement of said guide means and said bobbins,

(b) a pair of spaced first and second control elements defining opposite ends of the path of travel of said tumbler,

() means responsive to movement of said tumbler into operative relation with each of said control elements for reversing the direction of movement of said tumbler and the direction of relative movement between said guide means and said bobbins,

(d) means responsive to each movement of said tumbler away from at least one of said control elements for imparting a predetermined amount of movement to said control elements relative to said tumbler in which at least one of said control elements moves toward said tumbler to thereby vary successive relative movements between said guide means and said bobbins while varying successive movements of said tumbler along said path,

(e) a variable speed transmission having an input shaft connected to said constant speed shaft and a variable speed output shaft operatively connected to said bobbins for driving the same,

(if) a movable speed control arm connected to said transmission for varying the speed of said output shaft,

said responsive means (d) comprising (1) a pilot shaft,

(2) a ratchet wheel on said pilot shaft,

(3) means operatively connecting said control elements to said pilot shaft,

(4) a pawl engageable with said ratchet wheel,

(5) means responsive to movement of said tumbler into operative relation with said one of said control elements for imparting an inactive stroke to said pawl, and

(6) means responsive to subsequent movement of said tumbler away from said one of said control elements for imparting an active stroke to said pawl to impart a step in rotation to said ratchet wheel and thereby to move said control ele ments.

17. In a machine for winding textile strands onto rotating bobbins and including strand guide means, and a reversible traverse mechanism effecting relative axial movement between said guide means and said bobbins, apparatus for controlling said mechanism comprising (a) a tumbler movable in a predetermined path in proportionally fixed relation with the relative movement of said guide means and said bobbins,

(b) a pilot shaft,

(c) normally inoperative means for imparting stepwise rotational movement to said pilot shaft in one direction.

((1) a pair of spaced first and second control elements defining opposite ends of the path of travel of said tumbler and being operatively connected to said pilot shaft for imparting a linear step in movement to said control elements relative to said tumbler each time a step in rotation is imparted to said pilot shaft and wherein at least one of said control elements moves toward said tumbler.

(e) means responsive to movement of said tumbler into operative relation with each of said control elements for reversing the direction of movement of said tumbler and the direction of relative movement between said guide means and said bobbins,

(f) means responsive to each movement of said tumbler into operative relation with at least one of said control elements for momentarily actuating said normally inoperative means to impart a step in movement to said control elements to thereby vary successive relative movements between said guide means and said bobbins while varying successive movements of said tumbler along said path,

(g) a limiting abutment carried by said pilot shaft and rotatable therewith, and

(h) means engageable by said abutment upon predetermined angular movement thereof and completion of a winding cycle for stopping the machine.

18. A structure according to claim 17, including manusually operable means for winding said pilot shaft in a reverse direction upon completion of each winding cycle to return said control elements toward a starting position, and stop means engageable by said limiting abutment for stopping further movement of said pilot shaft upon rotation thereof a predetermined angular distance in the reverse direction.

19. A structure according to claim 18, including means adjustably securing said limiting abutment on said pilot shaft for angular adjustment whereby the starting position of said pilot shaft and the consequent starting position of said control elements may be accurately predetermined, and means for angularly adjusting said firstnamed engageable means relative to said pilot shaft and said stop means whereby the instant at which the machine stops may be accurately predetermined.

References Cited by the Examiner UNITED STATES PATENTS 1,816,738 7/37 Netherland et a1. 5778 2,381,68'4 8/45 Overbey 5779 2,732,683 1/56 Hoifmann 5795 2,764,363 9/56 Stammwitz 24226.2 2,901,882 9/59 Granberry 5798 3,112,602 12/63 Ozaki 57-99 3,130,930 4/64 Miller 5798 X MERVIN STEIN, Examiner.

Claims (1)

1. APPARATUS FOR CONTROLLING THE BUILDING OF PACKAGES OF STRAND MATERIAL ON A WINDING MACHINE HAVING ROTATING BOBBINS FOR RECEIVING THEREON THE STRAND MATERIAL, STRAND GUIDE MEANS ADJACENT EACH BOBBIN, A RECIPROCABLE TRAVESE MECHANISM FOR IMPARTING RELATIVE AXIAL MOVEMENT BETWEEN SAID GUIDE MENS AND SAID BOBBINS, AND MEANS SHIFTABLE BETWEEN FIRST AND SECOND POSITIONS FOR REVERSING SAID TRAVERSE MECHANISM AT THE ENDS OF STROKES THEREOF IN RESPECTIVE FIRST AND SECOND DIRECTIONS; SAID APPARATUS COMPRISING (A) A FRAME, (B) FIRST AND SECOND SPACED SWITCHES MOVABLY MOUNTED ON SAID FRAME, (C) A TUMBLER MOVABLE BETWEEN AND ADAPTED TO ENGAGE AND ACTUATE SAID SWITCHES IN ALTERNATION, (D) MEANS OPERATIVELY ASSOCIATED WITH SAID TRAVERSE MECHANISM FOR RECIPROCATING SAID TUMBLER IN SYNCHRONISM THEREWITH, (E) FIRST AND SECOND ELECTRIALLY OPERABLE MEANS FOR SHIFTING SAID SHIFTABLE MEANS TO THE RESPECTIVE FIRST AND SECOND POSITIONS AND BEING ELECTRICALLY CONNECTED IN PARALLEL TO THE RESPECTIVE FIRST AND SECOND SWITCHES WHEREBY THE DIRECTION OF MOVEMENT OF SAID TRAVESE MECHANISM IS REVERSED EACH TIME SAID TUMBLER ENGAGES AND ACTUATES EACH OF SAID SWITCHES, AND (F) MEANS RESPONSIVE TO EACH ENGAGEMENT OF SAID TUMBLER WITH AT LEAST ONE OF SAID SWITCHES FOR IMPARTING A STEP IN MOVEMENT TO AT LEAST ONE OF SAID SWITCHES TOWARD SAID TUMBLER THEREBY TO VARY CORRESPONDINGLY THE RANGE OF MOVEMENT OF SAID TRAVERSE MECHANISM AND SAID TUMBLER RELATIVE TO SAID FRAME.

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