US3480218A - Yarn furnisher for winding machines - Google Patents

Description

Nov. 25, 1969 J. B. LAWSON 3,480,218

YARN FURNISHER FOR WINDING MACHINES 2 Sheets-Sheet 1 Filed Dec. 22. 1966 FIG.I

INVENTOR. JOHN B. LAWSON ATTORNEYS Nov. 25, 1969 Q LAWSON 3,480,218

YARN FURNISHER FOR WINDING MACHINES Filed Dec. 22, 1966 2 Sheets-Sheet 2 INVENTOR. JOHN B. LAWSON BY W4 ATTORNEYS United States Patent YARN FURNISHER FOR WINDING MACHINES John B. Lawson, Barrington, R.I., assignor to Robison Rayon Company, Inc., Providence, R.I., a corporation of Rhode Island Filed Dec. 22, 1966, Ser. No. 603,925 Int. Cl. B65h 59/06 US. Cl. 242-45 9 Claims ABSTRACT OF THE DISCLOSURE This invention relates to apparatus for furnishing yarn to winding machines and the like, wherein the tension on the yarn is selectively controlled as the yarn is taken up by a yarn package. The invention provides positive yarn feeding means and a differential control system whereby it is possible to deliver yarn continuously ti a winder at a pre-selected tension, regardless of tension changes which enter the system from external sources. Further, the invention provides means whereby a uniform tension may be maintained on the yarn throughout the build of the yarn package, or the tension may be programmed to increase or decrease, as desired, while the package builds.

Summary of the invention Yarn packages having yarn wound thereon under controlled tension, such as uniform tension throughout, are desired in various textile uses. As is well known, it is often important to have uniformly tensioned yarn packages in many weaving and knitting processes. Moreover, package dyeing particularly of synthetic yarns, is best accomplished when the yarn is wound on the package uniformly.

In conventional winding machines operating with constant spindle speeds, the tension on the yarn tends to increase as the yarn package builds, i.e. increases in size. This results in undesirable tension variations throughout the yarn package. Various furnishing devices have been proposed for supplying yarns to winding machines under controlled tensions, but they have proven to be unsatisfactory for a variety of reasons, such as lack of sensitivity, frequent breakdowns, limited utility, limited control ranges, lack of accuracy in programming, etc.

A primary object of the present invention is to provide an improved yarn furnisher, based on a new principle, that will feed yarn continuously to a winding mechanism under selectively and accurately controlled tension.

Another object is to provide a furnisher which may be programmed to maintain a selected uniform yarn tension throughout the build of the package or, if desired, will provide a selected variable tension during the package build, such tensions being repeatable for successive packages wound on the winder.

Another object is to provide a yarn furnisher wherein tension variations in the yarn as it is withdrawn from its source of supply are, for practical purposes, nullified so that the tension on the yarn as it is delivered is a function only of the tension imposed by the device.

Another object is to provide mechanism for furnishing yarn in accurately measured selected lengths under predetermined tension to a winder or the like.

A further object of this invention is to provide automatic yarn furnishe-r means for a winding machine which controls the rate at which the yarn is positively fed to the winder in response to an integrated signal combining signals originating from two separate differential sensing means; one means sensing the build up of the yarn package and the other means sensing the tension in the yarn as it is delivered from the positive yarn feeder to the yarn package on the winder.

3,480,218 Patented Nov. 25, 1969 Description of the drawings Other objects and advantages of this invention will be evident from the description which follows and from the drawings wherein:

FIGURE 1 is a fragmentary view in perspective of a yarn winding device equipped with a preferred yarn furnishing mechanism of this invention; and

FIGURE 2 is an enlarged fragmentary view, partly in section, of the variable speed drive and differential control system, with the sensing arm and impulse transmission linkages shown schematically.

Detailed description Referring to FIGURE 1, a yarn Y is drawn from a cone C or other suitable source of supply and is wrapped about spools 2 and 3 which are part of the positive yarn feeder 1. Spool 2 is freely rotatable and is driven by spool 3 through an elastic belt 4. The axis of spool 2 is set at a divergent angle to that of spool 3 so that the yarn will spiral about the spools, and not become entangled, as the furnisher operates. Spool 2 is known in the art as a Gaudet roll. Since the yarn Y is wound several times about the spool combine 2 and 3, the yarn is positively fed without slippage, and tension variations in the yarn as it comes from the supply C are nullified.

Upon leaving the spools 2 and 3, the yarn travels upwardly through a guide eye 5 at the distal end of a pivotable tension sensing arm 6. From guide eye 5, the yarn passes downwardly through the guide eye 11 of a reciprocatable traverse arm 12 and thence onto the spindle 13 about which the yarn package 14 is built. Arm 12 is mounted on the traverse frame T which is swingable about its axis 10. The spindle 13 and traverse frame T may be the components of any-well known yarn winder, such as a Leesona model No. 50, wherein the spindle is driven at a selected constant speed by the usual winding machine drive shaft (not shown).

As the size of package 14 increases, the traverse frame T gradually swings outward, about its axis 10, in harmony therewith. Meanwhile, the rate at which yarn is taken up by the package 14 gradually increases, due to the increase in the diameter of the package. This invention utilizes the outward movement of frame T to control continuously the speed at which yarn Y is delivered by spools 2 and 3 to the winder.

As best shown in FIGURE 2, the proximal end of sensing arm 6 is afiixed to a rock shaft 15 mounted within control housing 7. A spiral spring 16 has one end fixed to shaft 15 and its other end secured internally of an axially turnable annular housing 17. Spring 16 urges shaft 15 in a counterclockwise direction, as viewed in FIGURE 2, to cause arm 6 to pivot upward, away from spools 2 and 3. The degree of spring load on arm 6 may be varied by turning spring housing '17 relative to rock shaft 15. A spring loaded detent 20 is employed to lock housing 17 against unintentional angular displacement. Spring housing 17 and detent 20 are disposed externally of control :housing 7 for ready accessibility thereto. If desired, housing 17 may be provided with a calibrated scale to facilitate the setting of spring 16 to impose selected spring loads on sensing arm 6.

It will be seen that yarn Y, as it passes from spool 2 to eye 5 to eye 11, is formed into a loop, the size of which is determined by the position of the upwardly urged arm 6. The yarn passing through loop 2-5-11 is tensioned by arm 6, the magnitude of such tension being equal to one-half the torque load imposed by spring 16 on the arm. When the positive yarn feeding rate of spools 2 and 3 equals the yarn take up rate of package 14, arm 6 imposes a uniform, selected tension on the yarn passing through loop 2-5- 11.

Should any differential occur between the rate at which yarn is fed by spools 2 and 3 and the rate at which yarn is taken up by package 14, the size of this loop of yarn will change, causing or permitting a simultaneous and proportional change in the position of arm 6. If the rate at which yarn is taken up by package 14 should exceed the rate at which yarn is delivered positively by spools 2 and 3, the loop of yarn 2511 will decrease in size, pulling arm 6 downward. By means of mechanism to be explained, such downward movement of arm 6 will increase the positive yarn feeding rate of spools 2 and 3. However, should the rate at which yarn is taken up by package 14 fall below the rate at which yarn is delivered positively by spools 2 and 3, the loop of yarn 2-5-11 will increase in size, permitting arm 6 to move upward under the influence of spring 16. This upward movement will cause a decrease in the positive yarn feeding rate of spools 2 and 3, as will be explained.

Upward movement of arm 6, due to an increase in size of the yarn loop, will reduce the tension exerted by the arm on the yarn Y. Downward movement of arm 6, caused by a decrease in the size of the yarn loop, will increase tension on yarn Y.

The positive yarn feeder spool 3 is driven from the winding machine drive shaft (not shown) through pulley 21, affixed to said shaft, belt 22, pulley 23, shaft 24 and a variable speed drive comprising Reeves pulleys A and B and elastic belt 32 (FIG. 2). Pulley 23 is afiixed to the end of the rotatable shaft 24, which is suitably supported Within tubing 26 and control housing 7 by bearings. Within housing 7, Reeves pulley A, comprising interengaged pulley halves 27 and 28, is suitably connected to shaft 24 for rotation therewith. Pulley half 28 is slidably mounted on shaft 24 so that it may be moved axially toward or away from pulley half 27. A vertical arm 30 pivoted at 31 in housing 37 is equipped with bifurcated rounded ends which straddle shaft 24 and rest against pulley half 28. When arm is moved in a clockwise direction, as shown in FIGURE 2, it slides pulley half 28 toward pulley half 25, thereby increasing the driving diameter 29 of the pulley A. If arm 30 is moved counterclockwise, the force of elastic belt 32 will cause pulley half 28 to move to the right, axially along shaft 24, to decrease the driving diameter 29.

A rotatable shaft 33, mounted within htousing 7 above shaft 24, supports the Reeves pulley B, which comprises pulley halves 34 and 35. The diameter of pulley B is adjustable in similar fashion to that of pulley A. More particularly, pulley half 34 is slidably mounted on shaft 33, and a vertical arm 36, pivotally attached within housing 7 at 37, has rounded bifurcated ends 40 which straddle shaft 33 and bear against pulley half 34. When arm 36 is moved clockwise, as shown in FIGURE 2, pulley half 34 moves toward pulley half 35 to increase the diameter of pulley B. Conversely, if arm 36 is moved counterclockwise, elastic belt 32 will force pulley half 34 away from half 35 to decrease the diameter of the pulley.

Spool 3 is affixed to shaft 33, and thus is driven by shaft 24 through the variable speed Reeves drive.

A horizontal link 38, having one end pivotally attached to arm 30 and the other end pivotally attached to arm 36, coordinates the movement of the arms. Clockwise movement of arm 30 moves link 38 to the left of FIG- URE 2, and thereby causes arm 36 to move counterclockwise. Conversely, counterclockwise movement of arm 30 results in clockwise movement of arm 36.

Arm 36 is urged in counterclockwise direction, as seen in FIGURE 2, by a compression spring 39 which surrounds a guide rod 100. One end of rod 100 is pivotally connected to arm 36 by means of block 51, and its other end is slidably retained within aperture 52 in the wall of housing 7. Since link 38 connects arm 36 to arm 30, spring 39 serves also to bias arm 30 in a clockwise direction. Thus, in the absence of a counteracting force, spring 39, acting through arms 30 and 36, will cause pulley A to assume its maximum diameter, and will cause pulley B to assume its minimum diameter. In such condition, spool 3 will rotate at maximum speed.

A force to oppose and counteract spring 39 is provided by an air amplifier 41. The latter includes a circular cylinder cap 43 fitted over an aperture 42 in the side of housing 7 and a flexible diaphragm 44 clamped between the rim of cap 43 and the rim of aperture 41. The diaphragm 44, which may be of rubber or other flexible material, is fastened to the bottom of a piston 45 by a threaded plug 46. The space between the piston and the cylinder cap 43 provides a hermetically sealed pressure chamber 48.

Piston 45 has an axial bore 49, which is enlarged and threaded at its rearward end to receive plug 46. The forward end of bore 49 receives a piston rod 53 which, in turn, is pivotally connected to arm 30 by means of block 54. Piston 45 is provided at its forward end with an orifice 55, which communicates with piston bore 49 via passage in the piston. Bore 49, in turn, communicates with chamber 48 via axial bore 47 in plug 46.

Compressed air from a suitable source (not shown) is introduced into chamber 48 via pipe 57 and orifice 58 in cap 43. From chamber 48, compressed air passes to orifice via plug bore 47, piston bore 49 and piston passage 50. For purposes to be explained, the diameter of orifice 58 is smaller than that of orifice 55.

Orifice 55 may be closed or opened by a valve 60 pivotally attached at 61 to piston rod 53. Valve 60 is biased clockwise, as seen in FIGURE 2, about its pivot 61, by a compression spring 62 seated in an aperture 63 in piston 45. In the absence of a counteracting force, spring 62 pivots valve 60 to close orifice 55 to preclude the escape of compressed air therefrom.

When orifice 55 is closed, air pressure builds up behind piston 45 causing it to move to the right of FIG- URE 2. Movement of piston 45 to the right does not occur until the air pressure in chamber 48 overcomes the force of spring 39, which acts on piston 45 through arm 36, link 38, arm 30 and rod 53. Since piston rod 53 moves with the piston, it pivots arm 30 in a counterclockwise direction, permitting the diameter of pulley A to be reduced. Because of link 38, this movement of arm 30 causes clockwise movement of arms 36 to close pulley B and increase its diameter. The aforementioned change in diameter size of pulleys A and B causes a reduction in the speed of rotation of spool 3.

When valve 60 is moved about its pivot 61 away from orifice 55, the latter will be opened. If opened sufiiciently, the volume of compressed air escaping from orifice 55 will exceed that entering through orifice 58, since the latter is of smaller diameter, and the pressure behind the piston will drop. When the force exerted by the compressed air on the piston is reduced below the force exerted by spring 39, the spring acts to urge piston 45 to the left of FIGURE 2. Because spring 39 also moves arms 30 and 36 to the left, the diameter of pulley A will increase and that of pulley B will decrease, thereby increasing the rotational speed of spool 3.

Accordingly, air amplifier 41, under the control of valve 60, and acting in opposition to the force of spring 39, regulates arms 30 and 36 to adjust the size of Reeves pulleys A and B. The latter, in turn, govern the yarn feeding speed of spool 3. When spool 3 is rotating at the desired yarn feeding rate, free of external yarn tension influences, the system will be in equilibrium. In such condition, valve 60 will open orifice 55 sufficiently to maintain the force exerted by the compressed air on piston 45 equal to the force exerted by spring 39 on the piston. At this time the amount of compressed air escaping from orifice 55 will be in balance with the amount passing through orifice 58 into chamber 48.

Between its maximum speed position, to the far left in FIGURE 2, and its minimum speed position, to the far right in FIGURE 2 (when valve 60 is closed), piston 45 will have an infinite number of equilibrium positions. For each such equilibrium position there is a corresponding speed of rotation of spool 3, and hence a corresponding yarn feeding rate. As will be explained more fully hereinafter, the equilibrium position of piston 45 is adjustable automatically to maintain the yarn delivery rate of spools 2 and 3 in pre-selected relationship to the yarn take-up rate of yarn package 14.

Since valve 60 is mounted on piston rod 53, it moves as the piston moves. A horizontal flexible link 65 is connected to the upper end of valve 60 and, as more fully explained hereinafter, limits the extent of movement of the upper end of valve 60 when piston 45 is moved to the right, following closure of orifice 5 5-. As the piston 45 and valve 60 move to the right. Link 65 eventually is rendered taut. As a result, while piston 45 continues its movement, link 65 causes valve 60 to pivot counterclockwise, thereby opening orifice 55 and permitting compressed air to escape therefrom, causing the air pressure behind piston 45 to drop. When orifice 55 is opened sufiiciently to equalize the force exerted by the compressed air on the piston with the opposing force exerted thereon by spring 39, a new equilibrium position is reached by the piston, and it comes to rest.

If link 65 should be moved to the left, as seen in FIG- URE 2, valve 60 will be opened beyond its equilibrium position, thereby increasing the escape of compressed air from orifice 55. As a result, the force exerted by the compressed air on piston 45 is reduced, thereby permitting spring 39 to move the piston to the left in FIGURE 2. Such movement of piston 45 will continue until link 65 becomes slack, whereupon spring 63- causes valve 60 to pivot clockwise to close orifice 55 sufliciently to establish a new equilibrium position. When this occurs, the piston again comes to rest.

Thus, link 65 controls valve 60, and thereby determines the equilibrium position of piston 45, and hence the yarn delivery speed of spool 3.

Horizontal flexible link 65 connects the upper end of valve 60 to a vertical link 66 which serves as a differential control means. Link 65 may be in the form of a finely fashioned chain, or may comprise a cord of nylon or similar material. Differential control link 66 is pivotally attached at its lower end to a cam controlled link 68 supported within housing 7 by a horizontal pivot 69. The upper end of differential link 66 is formed with a rightangled extension 70 slidably engaged within a forked member 71 fastened to rock shaft 15. When the system is in equilibrium, arm 6, acting through shaft 15, fork 71 and differential link 66, tensions flexible link 65 sufficiently to urge valve 60 counterclockwise, about pivot 61, against spring 62. In such condition, flexible link 65 is tensioned sufliciently to open orifice 55 to the extent necessary to maintain the force exerted by the compressed air on the piston equal to the force exerted thereon by spring 39.

Movement of arm 6 in a downward direction, caused by the take-up speed of package 14 exceeding the delivery speed of spools 2 and 3, moves differential link 66 counterclockwise about its pivot 67. This motion pulls flexible link 65 to the left, as seen in FIGURE 2, pivoting valve 60 counterclockwise to open further orifice 55. When the force of the air pressure behind piston 45 becomes less than the force of spring 39, the piston moves to the left, as previously described. Accordingly, the diameter of pulley A is increased and that of pulley B is decreased, causing the rotational speed of shaft 33 and spool 3 to increase, until the yarn delivery speed again equals the yarn take-up speed of package 14.

As the piston 45 moves to the left, the tension exerted on flexible link 65 by differential link 66 is relaxed, permitting spring 62 to bias valve 60 in a clockwise direction, toward orifice 55. Piston 45 continues to move to the left until valve 60 closes orifice 55 sufliciently to permit the air pressure behind the piston to build up until the force exerted thereby again equals the counteracting force exerted by spring 39. After piston 45 has moved far enough to permit arms 30 and 36 to make, through the Reeves differential drive, the desired speed correction, spring 62 restores valve 60 to its equilibrium position. The piston now comes to rest, and remains in its new position until the next correction.

If arm '6 should move up, caused by the delivery speed of the spools 2 and 3 exceeding the take-up speed of package 14, differential link 66 will pivot clockwise, about its pivot 67, permitting flexible link 65 to relax. As a result, spring 62 urges valve 60 clockwise, about its pivot 61, to close orifice 55. When the force of the air pressure behind piston 45 exceeds the force of spring 39, the piston moves to the right, as seen in FIGURE 2. This movement reduces the diameter of pulley A and enlarges the diameter of pulley B, thereby reducing the speed of shaft 33 and spool 3, until the yarn delivery rate again equals the yarn take-up means.

As piston 45 moves to the right, flexible link 65 will be tensioned, causing valve '60 to begin to pivot counterclockwise to open orifice 55, permitting compressed air to escape again therefrom. Piston 45 continues to move to the right until valve 60 opens orifice sufliciently to permit the force of the air pressure behind the piston to be reduced until it is equal to the force exerted by spring 39. At this point, the piston again comes to rest, having moved far enough to permit arms 30 and 36 to make the necessary adjustment of the Reeves differential drive to provide the desired speed correction.

Thus, arm 6 senses any disparity between the positive yarn feeding rate of the spools 2 and 3 and the yarn takeup rate of the package 14, and transmits this difference via impulse transmission means comprising rock shaft 15 and fork 71 to differential link 66. The latter transmits the impulse to valve 60, permitting piston 45 to adjust the Reeves differential drive to correct the yarn delivery speed of roll 3. When the disparity between the yarn take-up speed and the yarn delivery speed is eliminated, arm 6 stops its movement. Like piston 45, it remains in its new position until the next speed correction is required.

If external influences which tend to vary the tension on yarn Y enter the system, the positive yarn feeding spools 2 and 3 will respond, either increasing or decreasing the yarn feeding rate. As a result, arm 6 will move to restore the balance between the yarn feeding rate of the spools and the yarn take-up rate of package 14. For example, if yarn tension is increased for any reason, thereby slowing down spools 2 and 3, arm 6 will be pulled down to speed up spools 2 and 3 to restore the speed balance. Should external influences cause a reduction of tension on the yarn, permitting spools 2 and 3 to speed up, arm

6 will rise to slow down the speed of the spools and restore the speed balance.

The movement of winding frame T in a clockwise direction about its axis 10, in response to the build up of the yarn package 14, is utilized to control the speed of the delivery spool 3. There is connected to the frame T a rigid link 74 to which an upstanding link 75 is attached. Link 75 is connected to one end of a pivotally mounted horizontal link76 (FIG. 1), the opposite end of which is connected to upstanding link 77. The latter is in two sections, which are connected by a turnbuckle 78. At its upper end, link 77 is connected to a lever 81 afiixed to a rock shaft 82 supported within housing 7. Also affixed to rock shaft 82 (FIG. 2), for angular movement therewith, is a cam 83 having a curved cam slot 84. A pin 85, which acts as a cam follower, is mounted on the lower end of link 68 and engages within cam slot 84.

As the traverse frame T and its link 74 move in a clockwise direction, during the buildup of package 14, link 75 is raised, causing link 77 to descend. The descent of link 77 causes link 81, shaft 82 and cam 83 to pivot counterclockwise, thus moving link 68 clockwise about its pivot 69. This motion of link 68 causes differential link 66 to pivot clockwise about fork 71, thereby pulling flexible link 65 to the left to open valve 60. As a result, the air pressure behind piston 45 is reduced and spring 39 causes the piston to move to the left of FIGURE 2. Through the motions already explained, this movement of piston 45 increases the diameter of pulley A and decreases the diameter of pulley B, whereby the delivery speed of spool 3 is increased.

Cam slot 84 is shaped so that, as yarn package 1 4 builds, the impulse transmission means comprising links 74, 75, 76, 77, lever 81, rock shaft 82, cam 83, pin 85 and link 68 actuates differential link 66 to produce the desired change in the speed of rotation of spool 3. Thus, cam 83 is designed so that each increment of movement of frame T produces a selected and corresponding increment of change in the speed of spool 3. The design of cam slot 84 may be such as to maintain the yarn delivery speed of rolls 2 and 3 equal to the yarn take-up speed of package 14, in which event a uniform tension will be maintained on the yarn being wound. In such case, as frame T moves outward, cam 83 will cause the proper adjustments to be made to the Reeves differential drive, through differential link 66, flexible link 65, air amplifier 41 and arms 30 and 36, to increase the speed of spool 3 to the extent required.

However, if it is desired to reduce the tension on the yarn slightly, as it is wound, cam slot 84 is designed to overcorrect the speed of spool 3. In such event, as frame T moves outward, cam 83 actuates the speed control system to increase the speed of spool 3 to an extent sufficient to overfeed the yarn. When this occurs, arm 6 rises to reduce the tension on the yarn. As arm 6 rises, it actuates the speed control system to decrease the speed of spool 3 to eliminate the disparity between the yarn delivery rate and the yarn take-up rate caused by cam 83. When the two rates are again equal, the upward movement of arm 6 ceases. Thus, arm 6, as it rises to its new position, eliminates the overcorrection caused by cam 83, restores the yarn delivery and take-up speed balance and reduces tension on the yarn. In the course of winding a complete package 14, under gradually reducing yarn tension, arm 6 gradually rises, through an angle of about 45, from start to finish.

It will be seen that arm 6 has three functions: (1) to apply a pre-selected uniform or pre-selected variable tension on the yarn, (2) to nullify the effect of tension variations which enter the yarn feeding system from external sources and (3) where a pre-selected variable tension is programmed to control speed overcorrections or undercorrections arising from the movement of frame T, so that the yarn feeding speed is maintained equal to the yarn take-up speed of package 14. In practice, because slight tension variations tend to arise continuously, from a variety of causes, arm 6 is constantly oscillating or vibrating as it carries out its functions. Where uniform tension is to be maintained on the yarn as the package builds, the arm will vibrate in a more or less fixed position. Because the arm 6 is constantly vibrating, it is constructed of light, but rigid, material.

The length of link 77 can be adjusted by turnbuckle 78. In this manner, the angular position of arm 6, when valve 60 is in equilibrium position, may be adjusted as desired. Thus, the length of link 77 can be changed so that arm 6 will activate valve 60 at different angular positions with respect to the positions of the traverse frame T.

In addition, the connection of link 75 to link 74 can be moved closer or further from the axis 10 of the traverse frame T. In this manner, the amount of speed change imparted to spool 3 can be adjusted to equal the change of take-up speed of the package 14 or to provide speed changes which are either greater or less than the requirement of the package 14. If, for example, link 75 is positioned further away from axis 10 of the traverse frame, the speed of spool 3 will be overcorrected as the package builds, and arm 6 will rise to correct for the over-feed. As the arm 6 rises, the force exerted by spring 16 on the arm will decrease, thus reducing the tension on the yarn Y. In this manner also, a reducing tension may be programmed.

It will be noted that arm 6 has an upward extension 88 (FIG. 2) disposed between the electrical contacts of an insulated clip 99. If the arm rises too high, as would occur if the yarn should break or run out, or if it drops too low, as might happen if the yarn fouls on spool 3, extension 88 will strike a contact and stop the winder. The clip 99 is connected to a stop motion system (not shown) for stopping the winder in a manner familiar in the art.

Means 89 are provided for measuring the amount of yarn wound on a package, and is connected by cable 90 to the stop motion system to stop a wind after a selected amount of yarn has been wound. Spool 3 has a fixed circumference, and it is thus possible to measure the yarn delivered per revolution of the spool. Counter 89 is mounted on the housing 7, and is connected to spool 3, to measure the revolutions thereof, through reduction gearing 91, 92, 93, 94 and 95. The counter 89 may be of a pre-set type, of well-known construction, capable of closing an electric contact after a selected count has been obtained. With such a counter, connected to the stop motion system of the winder, it is possible to regulate and select the amount of yarn to be wound on a given package, and to have the wind stop when the selected amount is reached.

Thus, this invention makes possible, for the first time, the provision of a yarn package wound with a pre-selected length of yarn, automatically and accurately, under a pre-selected, programmed tension, all of which is repeatable for successive packages wound on the machine.

It is to be clearly understood that the terms and expressions used herein are employed as terms of description, and not of limitation, and that there is no intention in using such terms and expressions to exclude any equivalents of the apparatus or method described. It is also to be clearly understood that what is specifically shown and described herein represents a preferred embodiment only of the invention, and that various changes and equivalents may be resorted to without departing from the principles of the invention or the scope of the claims hereof. Accordingly, it is intended to claim the present invention broadly, as well as specifically, as indicated in the appended claims.

What is claimed is:

1. A furnisher for feeding a strand of material to the wind package of a winding machine, comprising:

(a) ahousing,

(b) a first shaft rotatably supported by said housing,

(c) an adjustable diameter pulley and a strand feeding spool mounted upon said first shaft for rotation therewith,

(d) a second shaft rotatably supported by said housing,

(e) an adjustable diameter pulley mounted upon said second shaft,

(f) drive means for rotating said second shaft at a speed fixed in relation to the axial speed of said wind package,

(g) an elastic belt trained about said adjustable diameter pulleys whereby rotation of said second shaft is transmitted to rotate said first shaft and said strand feeding spool,

(h) hydraulic piston means operable to move and thereby to change the diameter of at least one of said pulleys so as to change the ratio of the peripherial speeds of said first and second shafts, and thus the ratio between the rotational speed of said spool and the axial speed of said wind package,

(i) control means for said hydraulic piston including a valve operable to adjust the hydraulic pressure 9 upon said piston to govern the movement of said piston, and

(j) a first and a second sensing means for operating said valve, said first means comprising a movable arm supported by said housing for forming said strand into a loop between said spool and said winding package and means connecting said arm to said valve so that a change in size of said loop causes movement of said valve; said second sensing means comprising means movable in response to a change in diameter of said wind package and connected to said valve so that said change in diameter moves said valve.

2. A yarn furnisher for a winding machine including:

(a) a yarn feeder for delivering y-arn to a winder;

(b) tension sensing means engaging said yarn as it passes from the yarn feeder to the yarn package being formed on said winder for producing a signal output in response to the tension in said yarn;

(c) a variable speed drive, drivingly connected to said yarn feeder;

(d) a second sensing means engaging said yarn package for producing a signal output in response to the build up of yarn thereon;

(e) impulse transmission means connected to said variable speed drive for regulating said drive in response input signals; and

(f) means connecting said tension sensing means and said second sensing means to each other and to said impulse transmission means for converting the output signals from said tension sensing means and said second sensing means into a single input signal to said impulse transmission means.

3. The invention of claim 2 wherein said impulse tranmission means comprises an air amplifier.

4. The invention of any one of claims 2 and 3, wherein means are connected to said yarn feeder for measuring the length of yarn delivered.

5. The invention of any one of claims 2 and 3 wherein said tension sensing means comprises an arm contacting said yarn and forming said yarn into a loop as it passes from the feeder to the yarn package and spring means biasing said arm to apply a predetermined tension to said yarn.

6. The invention of any one of claims 2 and 3 wherein said means for converting said output signals comprises a first lever pivotally connected at one end and having a free end thereof positioned to engage said second sensing means and pivot in response to the output signal therefrom, and a second lever pivotally connected at one end end to the free end of said first lever and having its other end positioned to engage said tension sensing means and pivot in response to the output signal therefrom, and input means connected to said second lever and said impulse transmission means movable to a plurality of positions in response to movement of said second lever for producing an input signal to said impulse transmission means.

'7. The invention of claim 3 wherein said air amplifier comprises continuously pressurize piston and cylinder means including a piston having passage means therethnough communicating with said continuously pressurized cylinder and terminating in valve means, said valve means being operatively connected to said means for converting said output signals to receive said input signal, said piston being operatively connected to said variable speed drive.

8. The invention of claim 6 wherein said input means comprises a flexible link connected at one end to said second lever, and linkage means connecting the other end of said flexible link to said impulse transmission means.

9. The invention of claim 7 wherein said means for converting the output signals from said tension sensing means and said second sensing means into a single input signal to said impulse transmission means comprises a first lever pivotally connected at one end and having a free end thereof positioned to engage said second sensing means and pivot in response to output signal therefrom, and a second lever pivotally connected at one end to the free end of said first lever and having its other end positioned to engage said tension sensing means and pivot in response to the output signal therefrom, and input means comprising a flexible link connected at one end to said second lever, and a lever pivotally mounted to said piston having one end forming a flapper for said valve means and the other end connected to said flexible link, said input means being movable to a plurality of positions in response to movement of said second lever for producing an input signal to said impulse transmiss1on means.

References Cited UNITED STATES PATENTS 2,401,676 6/1946 Weber 242-45 X 2,466,109 4/1949 Jencks 24218 2,915,254 12/1959 Weber et a1. 24245 2,938,365 5/1960 Lassiter 242--45 X 3,047,247 7/1962 Kotte 24245 3,371,879 3/1968 Hill 24245 NATHAN L. MINTZ, Primary Examiner

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