US3739603A

US3739603A - Apparatus and method for feeding strands, and elements thereof

Info

Publication number: US3739603A
Application number: US00137430A
Authority: US
Inventors: M Philip
Original assignee: Individual
Current assignee: Individual
Priority date: 1971-04-26
Filing date: 1971-04-26
Publication date: 1973-06-19
Anticipated expiration: 1990-06-19
Also published as: DE2220556A1; FR2144223A5; IT952790B

Abstract

The apparatus comprises rotatable tension equalizing cylinder, guides directing strands from a strand supply about and in contact with at least a portion of the cylinder so that the cylinder acts as a windlass to substantially equalize the tension in the strands, an assembly of feed rollers having axially spaced apart strand feeding sections and strand non-feeding sections, a movable bar parallel to the axis of the feed rollers, a plurality of guides pivotally mounted on and along the length of the movable bar, a cam for oscillating the movable bar along its length part of the distance through which it is movable, a lever for adjusting the position of the movable bar in a normal position where the cam can oscillate the movable bar and the guides direct the strands to the feeding sections of the rollers, or in an adjusting position where the guides can be individually pivoted to be aligned with either a feeding section or a nonfeeding section, or in a non-feeding position where all the guides are aligned with non-feeding sections, the strands being guided from the feed rollers to the knitting stations of a multifeed knitting machine, and drive means for rotating the cylinder and rollers, the cylinder being rotated at a lineal rate greater than that of the feed rollers.

Description

United States Patent Philip APPARATUS AND METHOD FOR FEEDING STRANDS, AND ELEMENTS THEREOF [7 6] Inve ntor: Morris 'l liilip, 2519 Grand Avenue,

Bronx, N.Y.

[22] Filed: Apr. 26, 19 71 [21] Appl. No.: 137,430

Primary Examiner-Ronald Feldbaum Attarney--Tashof & Osheroff June 19, 1973 [57] ABSTRACT The apparatus comprises rotatable tension equalizing cylinder, guides directing strands from a strand supply about and in contact with at least a portion of the cylinder so that the cylinder acts as a Windlass to substantially equalize the tension in the strands, an assembly of feed rollers having axially spaced apart strand feeding sections and strand non-feeding sections, a movable bar parallel to the axis of the feed rollers, a plurality of guides pivotally mounted on and along the length of the movable bar, a cam for oscillating the movable bar along its length part of the distance through which it is movable, a lever for adjusting the position of the movable bar in a normal position where the cam can oscillate the movable bar and the guides direct the strands to the feeding sections of the rollers, or in an adjusting position where the guides can be individually pivoted to be aligned with either a feeding section or a nonfeeding section, or in a non-feeding position where all the guides are aligned with non-feeding sections, the strands being guided from the feed rollers to the knitting stations of a multifeed knitting machine, and drive means for rotating the cylinder and rollers, the cylinder being rotated at a lineal rate greater than that of the feed rollers.

.30 Claims, 8 Drawing, Figures APPARATUS AND METHOD FOR FEEDING STRANDS, AND ELEMENTS THEREOF This invention is directed to an apparatus and method for feeding strands from a strand supply to a knitting machine or other machine or device which utilizes such strands. More particularly, the invention is directed to a method and apparatussas well as parts thereof, for reducing and substantially equalizing the tension in a plurality of strands and subsequently positively feeding the strands at a predetermined measured rate to the machine which utilizes the strands.

This invention is particularly concerned with feeding strands to multifeed knitting machines, although it can be used for other machines which desirably use a plurality of strands being fed at a predetermined measured rate. As is well known, multifeed knitting machines are provided with a plurality of knitting stations which knit a fabric from strands being delivered from a strand sup ply. The strand supply comprises a plurality of cones, or spools, of individual strands and each strand to be knit is guided from a cone to a separate knitting station on the machine. The knitting station is also frequently called a feeding station, although, in fact, at such stations the strand or yarn is not fed", that is positively moved, into the needles but is rather guided by a yarn guide into a position where the needles can draw it during the knitting operation.

Because of the elasticity of the yarn, the nature of the yarn, and the manner in which it is wound on the cone, when the yarn is removed from the cone the tension of the yarn varies during the unwinding process. In addition, frequently the yarn does not freely unwind from the cone but sticks and in order to free the yarn it is necessary to apply more tension. In addition to the variations in the tension in each yarn as it is unwound from its core, the tension also varies between the plurality of yarns as they are being unwound from their respective cones. If the yarns are guided directly from the spools to the feeding stations on the machine, the tension in each yarn, as well as among the yarns, varies as they are being drawn by the needles during the knitting operation. This results in needles drawing different lengths of yarn at different tensions, thereby producing an unevenly knitted fabric.

Attempts have been made to overcome these problems by providing devices which positively feed measured lengths of yarn to the feeding stations, but these devices do not feed and measure the yarns at the same tension. Therefore, since corresponding lengths of yarn during the measuring are under varying degrees of tension, such lengths of yarn, in their relaxed state, as in the finished fabric, would not be of uniform length. This causes uneven knitting.- On the other hand, merely equalizing the tension in all the yarns as they come from the strand supply and guiding the yarns to the knitting stations without positive measured feeding does not solve the problem because inherent variations and irregularities in the knitting machine still cause uneven knitting.

According to the present invention these difficulties are avoided by reducing and substantially equalizing the tension in the yarns and then positively feeding the yarns at a predetermined measured rate. Since the tension in all the yarns is substantially constant and equal when the yarns are positiyely measured and fed, all the feeding stations continue to receive, throughout the knitting operation, the precise amount of yarn required for the knitting operation, with the yarn being at about the same tension so that there is produced a uniform fabric. In addition, the invention provides a system for temporarily disengaging some or all of the yarns from the positive feeding device so that adjustments can be made on the machine. The invention also provides specific means for substantially equalizing the tension in the yarns and for positively feeding the yarns.

According to one aspect of the invention there is provided an apparatus for positively feeding a plurality of strands from a strand supply at substantially the same tension and rate of feeding, comprising tension equalizing means for reducing and substantially equalizing the tension simultaneously in a plurality of strands from a strand supply, guide means, and feeding means for positively feeding said strands at a predetermined measured lineal rate, said guide means guiding said strands from said tension equalizing means to said feeding means, said feeding means positively feeding said strands at substantially the same tension it received them from said guide means.

According to another aspect of the invention the tension equalizing means comprises a tension equalizing cylinder, means supporting said cylinder for rotation about its axis, drive means for rotating said cylinder about its axis, and means for directing said strands from said strand supply about, and in contact with, at least a portion of the surface of said cylinder, so that tension in said strands causes the surface of said cylinder to frictionally engage said strands and deliver them from said strand supply to said guide means and so that increased tension in any strand will increase the rate of delivery of that strand and decreased tension in any strand will decrease the rate of delivery of that strand, whereby the tension in all of said strands is substantially equalized.

According to another aspect of the invention the feeding means comprises a transversely extending main feed roller, at least one auxiliary feed roller opposed thereto, means supporting each of said feed rollers for rotation about its axis, and drive means for rotating each of said rollers about its axis, at least a portion of the surface of said main feed roller mating with at least a portion of the opposed surface of each said auxiliary feed roller so that rotation of said rollers will cause said mating portions to positively feed any strands therebetween.

According to another aspect of the invention the surfaces of said feed rollers are provided with opposed axially spaced apart portions which mate to define strand feeding sections and wherein said feed rollers are provided with other opposed axially spaced apart portions which do not mate to define strand non-feeding sections, said feeding sections and non-feeding sections alternating axially of said rollers, and wherein there are provided means for selectively guiding strands to feed ing or non-feeding sections.

According to another aspect of the invention there is provided a method of positively feeding a plurality of strands at substantially the same tension and rate of feeding comprising the steps of reducing and substantially equalizing the tension simultaneously in a plurality of strands from a strand supply and subsequently positively feeding said strands at a predetermined measured lineal rate while maintaining said strands at a substantially equal state of tension.

Other aspects of the invention are directed to various specific details of the apparatus and method.

These and other aspects of the invention will be readily apparent from the following description in connection with the accompanying drawings, wherein:

FIG. 1 is a fragmentary perspective view of the apparatus showing only some of the strands and some of the strand guiding fingers;

FIG. 2 is a transverse fragmentary section taken along the line 2-2 of FIG. 1, with the strand guiding fingers being at the beginning of the oscillatory or normal zone and the oscillating cam at its low point, the finger at the left side being omitted to show the groove in the feed roller;

FIG. 3 is a top plan fragmentary view taken along the line 33 of FIG. 2;

FIG. 4 is a longitudinal fragmentary section taken along the line 44 of FIG. 2;

FIG. 5 is a fragmentary view corresponding to FIG. 2, with the strand guiding fingers being at the end of the oscillatory zone or normal zone and the oscillating cam at its high point;

FIG. 6 is a fragmentary view corresponding to FIG. 5, showing the strand guiding fingers shifted into the adjusting segment, the oscillating cam becoming disengaged;

FIG. 7 is a fragmentary view corresponding to FIG. 2, showing the strand guiding fingers shifted to the nonfeeding range;

FIG. 8 is a developed view of the oscillating cam.

In the following description, the rear of the apparatus is that part to the right as viewed in FIG. 1, and to the left in FIG. 4. The front or forward end is that part to the left in FIG. 1 and to the right in FIG. 4, the forward direction being the direction from the rear towards the front. The left side of the apparatus is that facing the viewer in FIG. 1 and at the left side of FIGS. 2, 3, 5, 6 and 7, while the right side of the apparatus is that remote from the viewer in FIG. 1 and at the right side in FIGS. 2, 3, 5, 6 and 7. The transverse direction is the direction between left and right and the longitudinal direction is the direction between rear and front.

In the following description there will first be described the essential structure of the apparatus and then there will be described the operation of the apparatus.

THE STRUCTURE OF THE APPARATUS The essential structure of the apparatus will be described particularly in connection with FIGS. 1, 2 and 4. The apparatus of the invention is mounted on a supporting frame which is constituted by vertical posts 10, longitudinally extending horizontal beams 12, transversely extending horizontal beams 14 and

transverse plates

16, 18 and 20 secured to the longitudinally extending horizontal beams 12. The various elements which constitute the supporting frame are rigidly secured to each other in any desirable manner such as by bolting or welding. At the rear of the supporting frame secured to transverse plate 16 are transversely spaced apart vertically extending bearing brackets 22 in which there is journaled, for rotation about a horizontal axis, shaft 25 of roller, cylinder, or drum 24, which, for reasons which will be apparent hereinafter, will be called tension equalizing cylinder 24. At the left end of shaft 25, outside of bearing bracket 22, is coaxially mounted spur gear 26.

At the forward end of the supporting frame there are mounted transversely spaced apart longitudinally extending vertical brackets or plates 28 (on the right) and 30 (on the left). The shaft 32 of transversely extending main feed roller 34 is journaled in

brackets

28 and 30 for rotation about a horizontal axis. To the left of bracket 30 there are successively secured to shaft 32, coaxial therewith, small spur gear 36, large spur gear 38, and pulley 40. Pulley 40 is driven through belt 42 by a driving means 44 which, as will be explained hereinafter, may be an-independent motor, may be a variable speed control driven by an independent motor, or may be a variable speed control driven by the main machine drive of a knitting machine. Rotation of pulley 40 causes rotation of

spur gears

36 and 38, shaft 32, and roller 34. Between cylinder 24 and roller 34, on plate 18, there is mounted a longitudinally extending vertical bracket 46 in which is journaled shaft 48 of spur gear 50. The teeth of spur gear 38 mesh with the teeth of spur gear 50, whose teeth in turn also mesh with spur gear 26. Therefore, as pulley 40 rotates spur gear 38, and therefore roller 34 in the direction shown by arrow 52, spur gear 50 will rotate in the direction shown by arrow 54 and spur gear 26, as well as cylinder 24, will rotate in the direction shown by arrow 56. It is noted that roller 34 and cylinder 24 rotate in the same direction, counterclockwise as seen in FIG. 1 and clockwise as seen in FIG. 4.

Above roller 34 there is a vertical slot 58 in bracket 28 and a corresponding vertical slot 60 in bracket 30, slot 58 being opposed to slot 60. In bracket 28 there is another slot 62 forwardly and at an angle to slot 58 and in bracket 30 there is a corresponding slot 64 at an angle to slot 60. In each of

slots

58, 60, 62 and 64 there is slidably mounted a bearing block 66. In bearing blocks 66 mounted in slots 58 and 60, there are journaled the respective ends of shaft 68 of a first auxiliary feed roller 70 and in each of the bearing blocks 66 in slots 62 and 64 there are journaled the respective ends of shaft 72 of a second auxiliary feed roller 74. The

shafts

68 and 72 and the

respective rollers

70 and 74 are parallel to the shaft 32 of main feed roller 34. Bearing blocks 66, and therefore

rollers

70 and 74, are resiliently urged toward main feed roller 34 by means of compression springs 76 positioned between the upper end of bearing blocks 66 and

cover plates

78 and 80. The compression springs 76 resiliently urge, through their respective bearing blocks, the peripheries of each

auxiliary roller

70 and 74 into engagement with the periphery of main feed roller 34.

Coaxially mounted on the left end of

shafts

68 and 72 are

respective spur gears

82 and 84, the teeth of said spur gears mating with the teeth of small spur gear 36 on the shaft 32 of roller 34. Rotation of roller 34, and therefore spur gear 36, in the direction of arrow 52 (clockwise in FIG. 4) causes

rollers

70 and 74 to rotate in the direction shown by arrows 85 (counterclockwise in FIG. 4), so that any strands between the main feed roller 34 and the

auxiliary feed rollers

70 and 74 will be fed forwardly.

In each of

brackets

28 and 30, rearward of main feed roller 34, there is a vertical slot 86 in which are positioned the respective ends of an assembly or pair of transversely extending

bars

88 and 90. Bar 88 is a fixed bar and bar 90 is a movable bar. Bar 88, as can be seen most readily in FIG. 4, is L shaped, with the horizontal portion 91 of the L extending rearwardly to define a shoulder 92. Fixed bar 88 is secured or fixed to

brackets

28 and 30 by means of set screws 94, so that bar 88 is fixed relative to the supporting frame. Movable bar 90 is positioned rearwardly of fixed bar 88 and slidably or movably positioned on shoulder 92 of fixed bar 88, so that movable bar 90 is free to oscillate transversely, that is from left to right and right to left on shoulder 92. The vertical slots 86 are so dimensioned that the longitudinal distance between the forward vertical wall 96 and the rear vertical wall 98 which define slot 86 is about the same as the combined thickness of

bars

88 and 90 measured in the longitudinal direction of the apparatus. In this manner movable bar 90 is prevented from moving rearwardly H shoulder 92. It is also noted that fixed bar 88, and more precisely horizontal portion 91, extends laterally (downwardly as seen in FIG. 4) beyond movable bar 90.

At the right end of movable bar 90 there is a horizontal slot 100. A lever 102 is secured to the fixed bar 88 by means of a bolt or pintle 104 passing through horizontal slot 100, said pintle 104 extending into and being secured to the fixed bar 88. The diameter of the pintle 104 is substantially equal to the vertical width of slot 100 so as to prevent movable bar 90 from moving upwardly relative to fixed bar 88. Lever 102 is pivotable about pintle 104 and is provided with two notches or

camming surfaces

106 and 108 which can engage stop pin 110 on movable bar 90 when the lever 102 is pivoted, as will hereinafter be described.

At the left end of fixed bar 88 there is a plate or washer 112 which extends rearwardly over the upper edge of movable bar 90, said plate or washer 112 being secured to fixed bar 88 by means of bolt 1114. Plate or washer 1 12 prevents movable bar 90 from moving vertically relative to fixed bar 88 at the left end of the assembly of the bars.

In bracket 30 there is journaled a transversely extending horizontal shaft 116 which supports spur gear 118 whose teeth mesh with the teeth of spur gear 36 so that rotation of spur gear 36 rotates spur gear 118. On the inner face, that is, the right hand face, of spur gear 118 is mounted an annular cam 120 concentric with shaft 116. Annular cam 120 varies in thickness around its circumference from a minimum thickness to a maximum thickness diametrically opposed thereto, said thickness being measured in the direction parallel to the axis of shaft 116. This variation in thickness provides the inner face of annular cam 120 with an annular camming surface or track 121 directed toward and coacting with the free left end 122 of movable bar 90. The minimum thickness of cam 120 defines the low point 123 of the cam track and the maximum thickness defines the high point 124 of the cam track (see FIGS. 2, and 8).

Overlying the right ends of

bars

88 and 90 is a helical tension spring 126, one end of which is fastened by bolt 128 to the movable bar 90, and the other end of which is fastened by bolt 130 to the fixed bar 88 (see FIGS. 2, 3, 5, 6 and 7). Spring 126 constantly resiliently biases movable'bar 90 toward the left, urging the left free end 122 of the movable bar toward cam track 121. As cam 120 rotates from the position where low point 123 of the cam track is in contact with end 122 of the movable bar, the increasing height of the cam track moves movable bar 90 towards t lie'bright until the high point of the cam reaches end 122. As the cam 120 continues its rotation from the high point towards the low point, spring 126 urges movable bar to the left with the end 122 riding on the cam track. It will therefore be appreciated that as cam rotates, the coaction between cam track 121 and end 122 of the movable bar, together with the resilient biasing of spring 126, causes movable bar 90 to oscillate transversely.

A plurality of transversely spaced apart strand guides in the form of strand guiding fingers 132 are pivotably mounted on movable bar 90 by means of bolts or pintles 134, each bolt passing through a bore in a finger and threaded into the movable bar. Between the head of each bolt 134 and the finger 132 there is a spring washer 136 whose tension prevents finger 132 from moving angularly in the absence of an applied force. The axis of pivoting, or the pintle, divides each finger into a lower portion and an upper portion, the lower portion extending laterally beyond the bottom of the movable bar 90 to overlie the horizontal portion 91 of the fixed bar 88. To the left of the lower portion of each finger 132 there is mounted in horizontal portion 91 of fixed bar 88 a rearwardly extending stud or stop 138, each stop extending into the plane defined by the lower portion of said fingers. Adjacent the upper portion of each finger there is a corresponding rearwardly extending stud or stop 140 mounted in movable bar 90 to the left of each finger. When a finger 132 is in the upright position it abuts stop 140, thereby preventing finger 132 from rotating further in a counterclockwise direction, as viewed in FIGS. 2, 5, 6 and 7. When the movable bar is in an extreme left hand position, represented by the low point 123 of cam track 121, and the finger 132 is in a vertical position, the left hand edge of the lower portion of finger 132 abuts stop 138. However, when the movable bar is moved toward the right, as shown in FIGS. 5 and 6, and a finger 132 is in the vertical position, its left hand edge is moved away from stop 138. In this position, as shown in FIG. 6, each finger, such as finger 132A, can be rotated clockwise to the position shown in phantom 1328.

Each finger 132 has through its upper portion a strand guiding aperture which is constituted by a bore in which there is mounted a yarn guiding eyelet 142. The strand guiding apertures are about level with the nip defined by the mating of

rollers

34 and 70. The upper end of each finger is bent or inclined forwardly at about a point 144 between stud 140 and eyelet 1412, thereby inclining the upper extremity 146 of the finger closer to the front of the machine where it will be more readily accessible to the operator for manual manipulation, as will be later described.

The main feed roller 34 is provided with a plurality of axially spaced apart grooves, channels or recesses 148, so that the peripheral surface of roller 34 is provided with axially alternating grooves 148 and lands 150. Preferably the walls of the grooves 148 are beveled, as shown at 152. In the illustrated embodiment the number of grooves, and therefore the number of lands, corresponds to the number of fingers 132.

The lands of the main feed roller mate with the opposed portions of the surfaces of each of the auxiliary feed rollers, thereby providing the feed rollers with transversely, or axially, spaced apart feeding sections. The grooves do not mate with the opposed surfaces of either of the auxiliary feed rollers, thereby providing the feed rollers with transversely, or axially, spaced apart non-feeding sections. The feeding sections and non-feeding sections alternate axially along the rollers.

Each strand guide 132 can be aligned with either a feeding section or a non-feeding section of the feed rollers, as will be fully described hereinafter. The alignment of the strand guide 132 is determined by the alignment of the strand guiding aperture 142 relative to a land or groove of main feeding roller 34. When an aperture 142 is in the same longitudinal line as a land, a strand guided through said aperture will be directed to the land and when an aperture 142 is in the same longitudinal line as a groove, a strand guided through said aperture will be directed to the groove. When the strand guides 132 are in the vertical position and the cam track 121 is at its low point, the strand guide is aligned with a land or feeding section. All the guides in FIG. 2 are in this position. As the cam moves the movable bar 90, and therefore the guides 132, to the right to the position shown in FIG. 5, wherein the cam track 121 is at the high point, each guide remains aligned with its respective land, or feeding section.

During the oscillation described in the previous paragraph, lever 102 is in the position shown in FIGS. 2 and 5. When lever 102 is moved upwardly to the position shown in FIG. 6, notch or cam surface 106 contacts stud 110 moving the movable bar 90 slightly further to the right from the position shown in FIG. 5. The notch 106 releasably locks the movable bar in the position shown in FIG. 6 and end 102 of movable bar 90 is no longer contacted by cam track 121 in either the high position or the low position. When the movable bar 90 is in the position shown in FIG. 6, it is in the adjusting segment of its transverse movement. In this position, when a finger is in the vertical position, such as shown at 132A, the guide, and more particularly the aperture 142 thereof, is still aligned with the corresponding land of the main feed roller. In this position the operator can manually, by exercising transverse finger pressure on the uppermost portion 146 of a guide 132, pivot said guide to the position shown at 132B so that the guide, and more particularly the aperture 142 thereof, is now aligned with a groove, or non-feeding section. In the illustrated embodiment, the left hand edge of the lower portion of guide 1323 contacts its corresponding stop 138 and this limits the angular movement of the guide.

When lever 102 is raised to the position shown in FIG. 7, notch or cam surface 106 cooperates with stud 110 to move movable bar 90, and therefore the fingers 132, still further to the right, and releasably lock the bar in the position shown in FIG. 7. In this position, the strand guides 132 are all aligned with grooves or nonfeeding sections. In the illustrated embodiment, in order to prevent the right hand edge of the lower portion of the guide 132 from abutting the stud 138, each guide is provided with a notch or'cutout 153.

The invention may be used with any type of strand supply. By way of example, the supporting frame is positioned over a yarn creel which supports a plurality of strand cones to supply the required ends of strands to be fed by the apparatus. Since it is not material whether the strands are on cones, spools, tubes, or in any other form, the various forms will be called cones for convenience. Such a strand supply is diagrammatically represented in FIG. 4 by cones. 154 which provide a plurality of strands 8.

Through plate 18 (see FIGS. 1 and 4) there are a plurality of spaced apart bores in each of which is fastened a strand guide eyelet 155. Two vertically spaced apart transversely extending bars 156 (see FIG. 1), and 157, whose ends are secured to vertical posts 10, are provided with transversely spaced apart bores and in each of the bores of lower bar 156 is fastened a strand guide eyelet 158 and in each of the bores of upper bar 157 is fastened a strand guide eyelet 160. Spaced apart strand guides 161 are suspended from a bar 162 whose ends are secured to posts 10 above bar 157. Spaced apart strand guide eyelets 163 are provided in a transversely extending bar 164 whose ends are secured to

brackets

28 and 30 forwardly of the feed rollers (see FIG. 4).

In order to simplify the drawings, the strands S are only shown in FIGS. 1 and 4. Each end of strand S passes from a strand supply, successively, through a guide 155, under cylinder 24, through a guide 158 (not shown in FIG. 4), clockwise around and in contact with the circumference of cylinder 24 about 330, upwardly through a guide 160, through a guide 161, through the eyelet 142 of a guide 132, through the nip defined by

rollers

34 and 70, through the nip defined by

rollers

34 and 72, and finally through strand guide eyelets 163. Guides 158 and direct the strands axially spaced apart about and in contact with the surface of cylinder 24. From strand guide eyelets 163 the strands S go either directly, or indirectly through additional strand guides (not shown), to the knitting stations of a multifeed knitting machine (not shown). It is not considered necessary to show the knitting machine and its knitting stations, since this invention can be used in connection with any type machine and the operation of such machines is well known. Preferably, however, the knitting machine is a multifeed circular knitting machine having one or more needle banks wherein the needle banks rotate and the knitting stations are stationary.

Optionally, if desired, each strand S, before it makes contact with cylinder 24, may pass through a weak tensioning device (not shown) which will supply a'slight frictional drag to the strand to provide smoother operation. At one ormore points in its path, between strand guide 160 and guide 132, for example, each strand may pass through a stop motion device (not shown). These are standard safety devices which cut off the power supply to stop the machine in the event any strand breaks or stops moving for any other reason. Each guide 161 may itself be such a stop motion device.

THE OPERATION OF THE APPARATUS The operation of the apparatus will be described with the strands S being threaded through the apparatus as described above and with the power on so that pulley 40, the various gears, rollers, and cylinder rotate in the direction previously described. The rate of movement of the rollers, cylinder and strands will be described in terms of lineal rate. The lineal rate is the lineal length or distance per base unit. The base unit may be time or it may be the movement of a particular element of the apparatus such as the revolution of a particular roller, or more preferably a revolution of the knitting machine. Of course, all rates should be expressed in terms of the same base unit.

The lineal rate of a strand is the length of that strand fed, delivered, or used, per base unit. The lineal rate of a roller or cylinder is the circumferential distance a point on its periphery moves per base unit. A roller 2 inches in diameter has a circumference of 2pi inches and therefore a point on the periphery of the roller moves lineally 2pi inches each revolution of the roller. If the base unit is a revolution of that roller, the lineal rate of that roller would be 2pi inches per revolution. If the base unit is time and the roller makes ten revolutions per minute, the lineal rate would be pi inches per minute.

By way of example, in the illustrated embodiment cylinder 24 is three inches in diameter, main feed roller 34 is two inches in diameter and each of

auxiliary feed rollers

70 and 74 is 1 /2 inches in diameter. Gear 36 and gears 82 and 84, which are driven by gear 36, are so dimensioned that for each revolution of gear 36 each of

gears

82 and 84 rotate 1% revolutions. The

respective rollers

34, 70 and 74, therefore, rotate at the same lineal rate and there is no slippage of one roller relative to another roller. In view of this any strands passing between the mating rollers will be measured and fed at the same lineal rate as the rollers. in this example the diameter of the feed roller is measured at the lands, since these are the portions of the roller which do the feeding. The apparatus can be set to rotate main feed roller 34 at any particular lineal rate and this rate will be called the predetermined lineal rate.

Gear 38, which is coaxial with and rotates at the same speed as roller 34, has the same diameter as gear 26, which is coaxial with and rotates cylinder 24. Gear 38 drives gear 26 through idler gear 50 and therefore each revolution of gear 38 will cause one revolution of gear 26 and therefore cylinder 24. Since the diameter of cylinder 24 is 50 percent greater than the diameter of feed roller 34, the lineal rate of cylinder 24 is 50 percent greater than the lineal rate of roller 34.

All strands, and particularly strands of knitting yarn with which the invention is primarily concerned, have a certain amount of elasticity. Knitting yarns are particularly elastic in the sense that they can easilly be stretched upon the application of a relatively small force. When strands are wound on cones they are wound under at least some tension. According to the invention, the tension equalizing cylinder comprises a means for reducing the tension in the strand so that when the strand is delivered from the strand supply to a strand guide 132 it is at substantially no tension or at a minimum tension. In other words, the strand is substantially completely relaxed. Furthermore, all the strands are delivered at substantially equal tension.

The tension equalizing cylinder 24 is preferably a steel roller having a smooth surface so that when a strand is in loose contact with the surface of cylinder 24 there is substantially no frictional engagement between them and the surface can slip relative to the strand. On the other hand, if tension is applied to the strand the frictional engagement between the strand and the cylinder increases and the rotating surface of the cylinder will drag the strand from the strand supply in the direction of rotation of the cylinder. The greater the tension, the greater will be the frictional engagement with a corresponding increase in the length of strand delivered by the cylinder. It is apparent that once the tension in the strand reaches the level where the strand is in such tight engagement with the cylinder that there is no slippage therebetween, the cylinder will deliver such strand at the lineal rate of the cylinder, which, in the illustrated example, is 1% times the predetermined lineal rate of main feed roller 34. This is the maximum lineal rate of delivery of cylinder 24. The minimum, of course, is zero, which occurs when a strand is so loosely wrapped around the cylinder that there is no frictional engagement therebetween. In other words, it may be said that the cylinder 24 acts as a winch or Windlass.

When a particular strand is being; fed by the feed rollers at the predetermined lineal rate, the strand is being drawn through yarn or strand guide at said predetermined lineal rate. If that strand does not come off freely from its cone, the tension in the strand around cylinder 24 immediately increases and this increase in tension causes cylinder 24 to deliver that strand at an increased rate to guide 160. Since the increased rate is greater than the predetermined lineal rate, the strand immediately relaxes between cylinder 24 and guide 160 and this relaxation reduces the tension in the strand around cylinder 24 and reduces the rate of delivery of that strand to guide 160. If a strand is being delivered by cylinder 24 to guide 1160 at a rate less than said predetermined lineal rate, the action of the feed rollers on that strand increases the tension in that strand. This increased tension is immediately reflected in the tightening of that strand around cylinder 24 with a resultant increase in the rate of delivery.

The above fluctuations in the tension of a strand about cylinder 24 take place automatically and act as a feedback device for adjusting the amount and tension of the strand delivered by cylinder 24. The system remains in substantial equilibrium with the rate of delivery of a strand to guide 160 being just about equal to the predetermined lineal rate and any variation thereof is constantly and immediately automatically corrected. It is also pointed out that the tension in the strand is at a substantial minimum because any increase would in crease the delivery by the cylinder :24, etc. It will be appreciated, of course, that there always is a little tension in a strand as it moves from cylinder 24 to guide 160, through guide 161, to guide 132 merely because of the weight of the strand itself. it might be said that the tension in the strand is just enough to about keep the strand from significantly sagging. What has been described as happening in connection with a particular strand happens in all the strands simultaneously as they are delivered by cylinder 24 so that all the strands arrive at guides 132 at substantially equal tension.

in the illustrated embodiment the strands from the strand supply pass around cylinder 24 so that each strand makes contact with approximately 330 of the periphery of cylinder 24. it is apparent that each strand may make contact with more or less of the periphery of the cylinder and it may even make contact with more than 360 by making more than one complete turn around the cylinder. This would occur, for example, if guides 158 were eliminated. It is only necessary to supply guides or other means for directing strands from the strand supply about, and in contact with, at least a portion of the surface of a cylinder so that tension in the strands causes the surface of the cylinder to frictionally engage the strands and deliver them from the strand supply and so that increased tension in any strand will increase the rate of delivery of that strand and decreased tension in any strand will decrease the rate of delivery of that strand. This substantially equalizes the tension in all the strands.

it is also apparent that the cylinder must rotate at a lineal rate greater than the lineal rate of the feed rollers or of any device which utilizes the strands delivered by the tension equalizing cylinder 24. If cylinder 24 rotated at a lesser lineal rate it could not deliver the strands at the lineal rate needed. There is no theoretical maximum rate of rotation for cylinder 24, although it is apparent that there is a practical one. It can be visualized that a cylinder can be made to rotate so rapidly that it will always frictionally engage the strands and deliver them at a rate in excess of the predetermined lineal rate. Obviously, the cylinder is not rotated so rapidly.

Referring to the positive feeding means, by way of example, the axial length of a land 150 plus groove 148 (including bevel 152) is three-fourths inch with the axial length of the land being 7/16 inch and the groove being /16 inch. In other words, the grooves are on inch centers and the lands are on V4 inch centers. Referring to the intermediate guide means, the pintles 134 are on inch centers, as are stops 138 and stops 140. When the guides 132 are in the upright or normal position apertures 142 are also on inch centers. With these dimensions 48 ends of strand can be supplied by feed rollers and cylinder 24 whose lengths are 36 inches plus an inch or 2 for safety.

When a guide 132 or more precisely its aperture 142, is aligned with a land the rollers will measure and feed the strand guided by the guide 132.

When movable bar 90, the guide supporting member, is at its extreme left hand position, as shown in FIG. 2, with cam track 121 at its low point, each aperture 142 is aligned with a land 150 at a point about one-sixteenth inch from the left edge thereof. The height of the cam, or the transverse distance from low point 123 to high point 124 is one-fourth inch so that when the cam is at its high point, as shown in FIG. 5, movable bar 90 has been moved one-fourth inch to the right and each aperture 142 is aligned with land 150 at a point fivesixteenths inch from the left edge thereof. Therefore, rotation of cam 120 causes movable bar 90 to oscillate transversely through a distance of one-fourth inch. This distance through which movable bar 90 oscillates may be called the normal feeding zone, with the position shown in FIG. 2 representing the beginning of the normal zone and the position shown in FIG. 5 representing the end of the normal zone.

When lever 102 is moved to the position shown in FIG. 6, notch 106 engages stud 110 to releasably lock bar 90 in this position. This moves bar 90 one sixtyfourth inch to the right, thereby disengaging end 122 from cam track 121, although cam 120 may continue its rotation. In this position when a guide 132 is in the upright position, shown by 132A in FIG. 6, the aperture 142 is still aligned with its land and movable bar 90 does not oscillate. The operator moves lever 102 to this position when he desires to make an adjustment selectively in connection with one or more particular strands. In this position the operator can manually push the end 146 of the desired finger or fingers to the right, represented by 1328. This shifts the aperture 142 of that finger one-fourth inch so that the aperture is now aligned with its corresponding groove in feed roller 34 and the strand guided by that aperture is not fed by the feed rollers. The operator can also manually pivot the finger from the position 1328 to return it to 132A.

When the movable bar 90 is in the position shown in FIG. 6 and a guide is in the vertical position, as shown by 132A, the strand guided by that guide is still aligned with a land of main feed roller 34, that is, the guide still directs its strand to a feeding section of the feed rollers and that strand is fed by the feed rollers at the predetermined measured lineal rate. When the guide is pivoted, as shown in 1328, its strand is not fed. When the guide is then shifted from position 1328 to 132A, its strand is shifted from its non-feeding section of the feed rollers to its feeding section, the strand climbing up the bevel 152. To assist the strand in returning from non-feeding to feeding, the bevel 152 may optionally be roughened, although this is not necessary. In the dimensions according to this example the axial length of the bevel 152 may be one-sixteenth inch. It is therefore apparent that the position shown in FIG. 6 represents a position wherein each guide 132, and therefore each strand, can be individually and selectively positioned to be aligned with a non-feeding or feeding section of the feed rollers. Therefore, when the movable bar is in the position shown in FIG. 6 it can be said to be in the adjusting segment of the space through which movable bar 90 moves transversely.

Lever 102 also constitutes a means for simultaneously shifting all of the guides to a non-feeding position wherein each guide is aligned with a non-feeding section of the feed rollers. This is accomplished by moving lever 102 to the position shown in FIG. 7 so that cam surface or notch 108, in cooperation with stop 110, moves movable bar 90 about one-fourth inch to the right from the position shown in FIG. 6 and to releasably lock bar 90 in this position. All of the guides 132 are thereby moved to the right so that when the guides are in the vertical or normal position their apertures 142 are aligned with a groove of the main feed roller, that is, aligned with a non-feeding section of the feed rollers. According to the dimensions thus far given, each guide should be restored to its vertical position, either manually or automatically, before lever 102 is moved to the position shown in FIG. 7. Otherwise, the guide in the tilted position 1328 would become aligned with a feeding section. It is apparent, however, that with different dimensioning, such as for example, by increasing the axial length of the grooves 148, it would not be necessary to first move the guides to the vertical position.

It is apparent that if the guide 132 had no cutout 153, the right side of the guide would make contact with its adjacent stop 138 as the movable bar is being moved from the position in FIG. 6 to the position in FIG. 7 and this would automatically tilt the guides to the position shown in 13213. The cutout 153 prevents this abutment. It is also apparent that by changing the dimensions such cutout could be eliminated so that it would be immaterial whether or not the guide tilts when being moved to the position shown in FIG. 7, so that the guide will still be aligned with a non-feeding section. Lever 102 can be moved directly to the position shown in FIG. 7 from that shown in FIG. 5 without stopping at the adjusting segment, as shown in FIG. 6.

When lever 102 is moved from either the position shown in FIG. 7 or the position shown in FIG. 6 to the position shown in FIG. 5, stop 1 10 is no longer engaged in either notch 106 or 108, and the spring 126 moves the movable bar to the left until the left end 122 of the movable bar makes contact with cam track 121. At that time movable bar 90 commences to oscillate under the control of cam track 121. It is noted that cam may continue its rotation even when the movable bar is in the position shown in FIGS. 6 and 7 but this has no effect on the movable bar 90 since the cam track 1121 cannot make contact with end 122.

From the preceding description it is apparent that fixed bar 83 comprises a mounting means supporting guide supporting member 90 for transverse movement through a space beginning with the extreme left hand position wherein the end 122 contacts low point 123 of the cam track (as shown in FIG. 2) and terminating in the extreme right hand position (as shown in FIG. 7). This space through which the movable bar moves comprises a feeding range followed by a non-feeding range. In the feeding range the guides when in their normal or vertical position are aligned with a feeding section of the feed rollers and in the non-feeding range each guide being aligned with a non-feeding section of the feed rollers. The feeding range comprises a normal zone and an adjusting segment. The normal zone represents the transverse space through which cam 120 oscillates movable bar 90, that is, the space beginning with the left hand position shown in FIG. 2 and ending with the right hand position of oscillation shown in FIG. 5. The end of the normal zone is intermediate the beginning of the normal zone and the non-feeding range. When movable bar 90 is in the normal zone the machine is in its normal feeding operation. The adjusting range of the feeding range is near the end of the normal zone and in the illustrated embodiment the normal zone does not include the adjusting segment so that the adjusting seg ment is intermediate the normal zone and the nonfeeding range.

It is apparent that the adjusting segment may optionally be further to the left from the illustrated embodiment. For example, when the movable bar is in the position shown in FIG. 5, each finger 132 can be selectively independently shifted to a non-feeding position. However, since the cam continues to rotate each time the high point 124 becomes aligned with end 122, it will rub against it. This creates unnecessary wear. The adjusting segment can be even further to the left from the position shown in FIG. and can even coincide with the feeding zone. However, the rotation of the cam would still at least partially oscillate bar 90 and such oscillation might be undesirable. It is therefore apparent that the feeding zone and the adjusting segment may be coextensive, may overlap, or may be transversely spaced apart. It is also noted that each guide is movable between two positions. In the first or normal position the guide is aligned with a feeding section of the feed rollers when the movable bar 90 is in the feeding range and in the second position the guide is aligned with a non-feeding section of the feed rollers when the movable bar 90 is in at least the adjusting segment.

Lever 102, in conjunction with stop I10, constitutes adjusting means for transversely positioning movable bar 90 in portions of the transverse space through. which the bar may move. The adjusting means can ei ther selectively releasably lock the movable bar in the adjusting segment, as shown in FIG. 6, or it can releasably lock the movable bar in the non-feeding position shown iniFIG. 7, or it can free the movable bar foroscillation in the normal zone, as shown in FIGS. 2 and 5. When the movable bar is in either the adjusting segment or in the non-feeding range and the lever 102 is released to the position shown in FIG. 5, the movable bar 90 automatically moves to the feeding zone and commences oscillation. As the oscillation causes the movable bar to move from the position shown in FIG. 5 toward the position shown in FIG. 2, if any guide is in its tilted position, as shown in 1328, the left side of its lower portion will make contact with its corresponding stud I38. As the movable bar continues its movement toward the beginning of the normal zone, the contact between stud 138 and the finger will automatically return the finger to its normal position 132A. Thereby means are provided for automatically returning and maintaining each of the guides in their normal vertical position during oscillation. This automatic movement of the guides toward their normal, or vertical, position can be utilized when returning the movable bar from the adjusting segment to the normal zone for normal feeding. It can also be used to position all the guides vertically prior to moving movable bar 90 from the adjusting segment to the non-feeding range. This is done by first shifting bar 90 from the adjusting segment to the normal zone and then to the non-feeding range. In the event the feeding segment is coextensive with the feeding zone, these studs 138 would have to be eliminated, otherwise it would be impossible to shift the guide and at the same time let the cam continue its rotation. It will be apparent that the structure of the apparatus provides means for selectively aligning the guides to feeding or non-feeding sections of the rollers. The guides will be individually and independently selectively aligned or may be simultaneously aligned. This alignment is accomplished by causing relative transverse shifting between the guides and the feed rollers.

Preferably the main feed roller 34 is made of steel with the lands being smooth. The surface of the auxiliary feed rollers is also preferably smooth, but made of rubber or other friction material and using such materials, when a strand is aligned with a land it is firmly grasped between the land and the opposed portion of the surface of the auxiliary rollers. .Since all the rollers move at the same lineal rate, this grasping of the strand by the rollers causes the rollers to feed and measure out definite lengths of strand per rotation of the rollers. In order to emphasize this measuring aspect of the feed rollers, it is desirable to sometimes refer to the rate of feeding of the feed rollers as the predetermined measured lineal rate. In the illustrated embodiment the surfaces of the auxiliary rollers contact the lands of the main feed roller. However, the spacing between the surfaces of the auxiliary rollers and the lands of the main feed roller must merely be sufficiently close, depending upon the diameter and material of which a strand is made, to firmly grasp the strands therebetween. When they are sufficiently close to firmly grasp the strands, the rollers are considered to be mating.

In the non-feeding sections the grooves do not mate with the opposed surfaces of the feed rollers, so that any strand therebetween is not fed at the predetermined measured rate.

In the illustrated embodiment gear 36, mounted on the shaft of main feed roller 34, engages

gears

82 and 84 of the auxiliary feed rollers to thereby drive the auxiliary feed rollers. Although it is preferable to have the auxiliary feed rollers so driven, it is not absolutely necessary. Auxiliary rollers and 74 may be idle rollers (not shown) driven merely by the contact between the surfaces of the auxiliary rollers and the main feed roller. Either arrangement provides means for rotating all of the rollers.

In the illustrated embodiment there are two auxiliary feed rollers. It is apparent that only one auxiliary feed roller need be provided (not shown), or there may be provided more than two auxiliary feed rollers (not shown). The purpose of oscillating movable bar 90 is to transversely oscillate the strands as they are being measured and fed by the feed rollers. The primary purpose of the oscillation of the strands is to distribute the wear of the mating surfaces caused by the movement of the strands therebetween. This will prevent the strands from wearing grooves in either the auxiliary feed rollers or the main feed roller and thereby lengthen the life of the rollers.

It is apparent that any one or all of the auxiliary rollers may have circumferential grooves (not shown) aligned with the grooves of the main feed roller. It is also apparent that the grooves can be eliminated from the main feed roller (not shown), with the grooves instead being provided in each of the auxiliary rollers in order to provide the non-mating portions of the rollers. In other words, the grooves can be either in all the rollers, or only in the main feed roller, or only in all the auxiliary rollers. It is merely necessary that the radial depth of the grooves in the assembly of the rollers be sufficiently great as not to mate and thereby so as not to measure and feed any strands aligned therewith.

Since the purpose of the oscillation is primarily to provide uniform wear of the rollers, the rate of soscillation is not critical and is not necessarily related to the predetermined measured lineal rate. The rate of oscillation is preferably relatively slow compared to the rotational rate of the main feed roller. For example, the cam 120 may rotate once for each five or ten or more or less rotations of the main feed roller. Preferably the cam track has a flat or dwell at its low point 123 and high point 124, as shown in FIG. 8. This is to take care of the time lag as the strand changes its direction of oscillation. The dimensions given in the foregoing specific example of operation are by way of example only and other dimensions can be used.

The feeding device of the present invention, as has been pointed out, is preferably used to feed strands to a multifeed circular knitting machine. The machine may be a jersey machine, a rib machine, an interlock machine, or any other type of machine having one or more needle banks. Taking, by way of example, a jersey cylinder knitting machine having a 30 inch diameter, such a machine would have a circumference of 30pi inches. For convenience let us consider 30pi equal to 100 inches. In such a machine, regardless of the gauge of the needles, each knitting station would consume, for each revolution of the machine, a length of yarn about 1% to 4% times the machine circumference, so that we can assume, by way of example, the machine is set so that each station will consume or knit 200 inches of yarn per revolution.

When the feeding device of the invention measures and feeds the yarn to an exemplary machine, as just described, the feeding rollers would feed 200 inches of each strand each time the knitting machine rotates l revolution. If the machine is rotating at the rate of 20 revolutions per minute, each strand must be delivered by the feeding rollers at the rate of 4,000 inches per minute. In order to maintain the proper ratio between the machine consumption and the rate of feeding of the feed rollers, the means driving the feed rollers, namely driving means 44, should be driven by the main machine drive (not shown) of the knitting machine, with means 44 being a variable speed drive. The variable speed drive may be linked to the main machine drive by any means such as belts, chains, or gears (not shown). By driving drive means 44 by the main machine drive the feeding apparatus is driven in timed relation to the main machine drive with the variable speed control making the adjustments in the speed of the feeding apparatus.

In the example given wherein each knitting station consumes 200 inches of yarn per machine rotation, the main machine drive is turned on and the variable speed control is adjusted until the feeding apparatus delivers the yarn at the right rate. At this point the feeding rollers are delivering the yarn at the predetermined measured lineal rate. If the main machine drive is speeded up to increase the rate of rotation of the machine, the variable speed device is speeded up proportionately and therefore still delivers the strands at the predetermined measured lineal rate, since the rate is per revolution of the main machine drive. In other words, if the variable speed control is set so that the feed rollers deliver 200 inches of each strand per revolution of the knitting machine, it will still deliver the same 200 inches per revolution whether the knitting machine is speeded up or slowed down. When the knitting machine is stopped, the feeding also stops.

It is apparent that driving means 44 does not have to be driven by the main machine drive. It may be driven by an independent power source, in which event, of course, it should be synchronous with a knitting machine or with any other machine which utilizes the strands. In the illustrated embodiment the same drive means drives the tension equalizing cylinder 24 and the feed rollers. Optionally (not shown), the tension equalizing cylinder and the feed rollers may be driven by independent drive means, it only being necessary that the tension equalizing cylinder be driven at a lineal rate greater than the lineal rate of the feed rollers. This is accomplished by eliminating idler gear 50 and by having cylinder 24 driven by a motor different from that driving pulley 40. However, it is highly desirable that they be driven by the same drive means so that the apparatus can be preset to insure that the lineal rate of cylinder 24 is greater than the lineal rate of the feed rollers.

The apparatus thus far described provides for numerous adjustments. A number of other optional variations (not shown) are possible. For example, the oscillation may be eliminated if wear on the feed rollers is not a problem. The non-feeding range may be eliminated since each of the guides can be individually moved to a non-feeding section. If movement of the guides individually from feeding to non-feeding positions is not desired, the adjusting segment can be eliminated. In fact, all of these movements and adjustments can be eliminated by eliminating the grooves, and therefore the non-feeding sections, from the rollers.

Occasionally a knitting machine will have some stations consuming yarn at one lineal rate, with other stations consuming yarn at a difierent lineal rate. In such a case an additional assembly of feed rollers and guides (not shown) may be provided, desirably positioned above the illustrated assembly of feed rollers and guides. Such a second feed roller assembly can still be driven by the main machine drive but through an independent speed control mechanism so. that the two assemblies of feed rollers feed at different lineal rates. In such a case the strands may still be guided from a single tension equalizing cylinder or there may be plural tension equalizing cylinders (not shown).

in the illustrated embodiment the strands are directed from cylinder 24 to yarn guides 160 and then to guides 132. It is apparent that yarn guides 160 may be eliminated (not shown) and guides 132 may also be eliminated (if the oscillation and adjustments are to be eliminated). This can be accomplished merely by the relative location of cylinder 24 and main feed roller 34. As a matter of fact, when cylinder 24 and feed roller 34 are positioned, as shown in FIG. 4, guides let) and 132 may be eliminated. Such positioning of the cylinder and rollers, by itself, constitutes guide means guiding the strands from the cylinder to the feeding means.

It will be appreciated that when the apparatus of the invention is feeding strands to the knitting machine and some or all of the guides 132 are aligned with a nonfeeding section of the feed rollers and the knitting machine is rotating, the yarns being directed to the nonfeeding sections may still be guided to the knitting stations and consumed thereat. However, such yarns passing through the non-feeding sections are not being positively fed and measured. The yarns which are being directed to the feeding sections of the feed rollers are being fed and measured with the measurement being consistent among the yarns and along the length of each yarn, since they are being measured at substantially the same tension.

Although most desirably the tension equalizing means of the invention and the positive feeding means of the invention are used together, each one may be used independently of the other. If it is desired to only positively feed the yarns, only the positive feeding means need be used, with the strands coming from any strand source. On the other hand, if it is only desired to have the tension in the strands reduced and substantially equalized, without positive feeding, it is only necessary to provide a tension equalizing cylinder, means for directing strands from a strand supply about at least a portion of the cylinder, and means for conducting the strands from the cylinder to the knitting stations. If these elements of the invention are separately used, they still may be driven by the main feed of the knitting machine or by any other drive means.

it will be appreciated that when the knitting machine is producing the fabric in its proper acceptable condition, all of the strands are being positively fed and measured to the knitting stations. it is only during adjusting periods, when either the adjustment is being made in the knitting machine or in the feeding device, that one or more strands is being directed to the non-feeding sections of the feed rollers. At such times, although the knitting machine continues knitting, all of the knitting stations do not receive their strands in the positively fed and measured state and during such periods the knitting fabric may not be up to acceptable standards.

It will be appreciated that the strands as they leave the feed rollers are in their substantially relaxed condi tion, or at a substantially minimum tension. it is usually desirable for strands to be under a slight tension as they are being knitted by the needles. Therefore, the needles actually draw their strands at a rate slightly greater, perhaps a few percent, than the predetermined measured lineal rate at which the strands are delivered by the feed rollers. In other words, if the feed rollers deliver a strand at the rate of 200 inches per machine revolution with the strand in its substantially relaxed state, the needles knitting that strand will draw it or knit it at the rate of, let us say, 205 inches per machine revolution, thereby creating a slight tension in the strand as it is being knitted. However, in the finished fabric that strand in the relaxed state will have been utilized at the rate of 200 inches per machine revolution. This concept should be borne in mind when it is stated that the knitting stations utilize the strands at the predetermined measured lineal rate.

The present invention has been described in detail for purposes of illustration only and is not intended to be limited by this description or otherwise except as defined in the appended claims.

I claim:

ll. An apparatus for positively feeding a plurality of strands from a strand supply at substantially the same tension and rate of feeding to knitting stations of a mu]- tifeed machine utilizing said strands at a predetermined lineal rate, comprising tension equalizing means for reducing and substantially equalizing the tension simulta neously in a plurality of strands from a strand supply, drive means for driving said tension equalizing means, first guide means, feeding means for positively feeding said strands at said predetermined lineal rate, drive means for driving said feeding means, said first guide means guiding said strands from said tension equalizing means to said feeding means, said feeding means positively feeding said strands at substantially the same tension it received them from said guide means, second guide means for guiding said strands from said positive feeding means to said knitting stations, and a main machine drive for synchronously driving said knitting machine, said tension equalizing drive means and said feeding drive means.

2. An apparatus according to claim ll, wherein said tension equalizing means comprises a tension equalizing cylinder, means supporting said cylinder for rotation about its axis, said tension equalizing drive means rotating said cylinder about its axis at a lineal rate greater than said predetermined lineal rate, and means for directing said strands from said strand supply about, and in contact with, at least a portion of the surface of said cylinder, so that tension in said strands causes the surface of said cylinder to frictionally engage said strands and deliver them from said strand supply to said first guide means and so that increased tension in any strand will increase the rate of delivery of that strand and decreased tension in any strand will decrease the rate of delivery of that strand, whereby the tension in all of said strands is substantially equalized.

3. An apparatus according to claim 2, wherein said feeding means comprises a transversely extending main feed roller, at least one auxiliary feed roller opposed thereto, means supporting each of said feed rollers for rotation about its axis, and said feeding drive means rotating each of said rollers about its axis at said predetermined lineal rate, at least a portion of the surface of said main feed roller mating with at least a portion of the opposed surface of each said auxiliary feed roller so that rotation of said rollers will cause said mating portions to positively feed any strands therebetween, said first guide means guiding strands from said tension equalizing means to said feed rollers.

4.. An apparatus according to claim 3, wherein said guide means includes a plurality of transversely spaced apart strand guides, said guides guiding strands to said mating portion of said opposed feed rollers.

5. An apparatus according to claim 4, including means for causing relative transverse oscillation between said strand guides and said feed rollers.

6. An apparatus according to claim 3, wherein the surfaces of said feed rollers are provided with opposed axially spaced apart portions which mate to define strand feeding sections and wherein said feed rollers are provided with other opposed axially spaced apart portions which do not mate to define strand nonfeeding sections, said feeding sections and non-feeding sections alternating axially of said rollers, and wherein there are provided means for selectively guiding strands to feeding or non-feeding sections.

7. An apparatus according to claim 6, wherein said other opposed auxiliary spaced apart portions which do not mate are constituted by providing at least either said main feed roller or each auxiliary feed roller with axially spaced apart circumferential grooves.

8. An apparatus according to claim 7, wherein at least said main feed roller is provided with said axially spaced apart circumferential grooves.

9. An apparatus according to claim 8, wherein said main feed roller is provided with axially spaced apart alternating circumferential grooves and circumferential lands, said lands mating with the surface of each auxiliary feed roller to define said feeding sections and the grooves not mating with any surface of any auxiliary feed roller to define said non-feeding sections.

10. An apparatus according to claim 6, including means for guiding each of said strands independently of others selectively to either a feeding section or a nonfeeding section.

11. An apparatus according to claim 10, including means for selectively guiding all of said strands simultaneously either to non-feeding sections or to feeding sections.

12. An apparatus according to claim 6, including means for selectively guiding all of said strands simultaneously either to non-feeding sections or to feeding sections.

13. An apparatus according to claim 6, including a transversely disposed guide supporting member, and wherein said guide means includes a plurality of transversely spaced apart strand guides mounted on said guide supporting member, said guides being selectively alignable with, and guiding strands to, strand feeding or strand non-feeding sections of said feed rollers.

14. An apparatus according to claim 13, wherein each of said guides is independently movably mounted on said guide supporting member and movable relative thereto between two transversely spaced apart guide positions, in one of said guide positions said guide being aligned with a strand feeding section and in the other of said guide positions said guide being aligned with a non-feeding section.

15. An apparatus according to claim 13, including mounting means supporting said guide supporting member for transverse movement through a space comprising a feeding range, means for transversely oscillating said guide supporting member through at least a portion of said feeding range, each of said guides being alignable with a strand feeding section during said oscillation.

16. An apparatus according to claim 13, including mounting means supporting said guide supporting member for transverse movement between a feeding position and a non-feeding position, in said feeding position each of said guides being alignable with a strand feeding section and in said non-feeding position each of said guides being aligned with a non-feeding section, and means to selectively position said guide supporting member at a feeding or non-feeding position.

17. An apparatus according to claim 13, including means for aligning all of said guides simultaneously either with strand feeding sections or with strand nonfeeding sections.

18. An apparatus according to claim 13, including mounting means supporting said guide supporting member for transverse movement through a space comprising a feeding range and a non-feeding range, means for transversely oscillating said guide supporting member through a zone of said feeding range, each of said guides being independently movably mounted on said guide supporting member and movable relative thereto between two transversely spaced apart guide positions, in the first of said guide positions said guide being aligned with a strand feeding section of said feed rollers when said guide supporting member is in said feeding range and in the second of said guide positions said guide being aligned with a non-feeding section of said feed rollers when said guide supporting member is in at least a particular segment of said feeding range, and adjusting means for transversely positioning said guide supporting member in selected portions of said space, each of said guides being aligned with a nonfeeding section of said feed rollers when said guide supporting member is positioned in said non-feeding range.

19. An apparatus according to claim 18, wherein said zone of said feeding range does not include said particular segment and wherein said adjusting means selectively positions said guide supporting member in either said zone, or said segment, or said non-feeding range, and including means for automatically maintaining each of said guides in said first guide position when said means for oscillating said guide supporting member oscillates it through said zone.

20. An apparatus according to claim 6, wherein said first guide means comprises a transversely extending fixed bar mounted substantially parallel to the axis of said main feeding roller, a transversely extending movable bar substantially parallel to said fixed bar and movable supported thereby for movement in a transverse direction through a space comprising a feeding range followed by a non-feeding range, said feeding range comprising a normal zone and an adjusting segment, said nonnal zone having a beginning and an end with said end being intermediate said beginning and said non-feeding range, said adjusting segment being near said end and not extending to said beginning, a plurality of transversely spaced apart strand guides pivotally mounted on said movable bar, each of said guides being independently pivotable between two transversely spaced apart guide positions, in the first of said guide positions said guide being aligned with a strand feeding section of said feed rollers when said movable bar is in said feeding range and in the second of said guide positions said guide being aligned with a non-feeding section of said feed rollers when said movable bar is in said adjusting segment, resilient means constantly urging said movable bar towards said beginning, cam means cyclically moving said movable bar from said beginning to said end against the action of said resilient means and permitting said resilient means to move said movable bar from said end to said beginning, said movable bar being normally positioned in said normal zone and free to move between said beginning and end, whereby said movable bar is normally oscillated transversely through said normal zone by said cam means and resilient means, and adjusting means for selectively either releasably locking said movable bar in said adjusting segment, or releasably locking said movable bar in said non-feeding range, or freeing said movable bar for oscillation in said normal zone, each of said guides being aligned with a non-feeding section of said feed rollers when said movable bar is positioned in said non-feeding range.

21. An apparatus according to claim 20, wherein said fixed bar extends laterally beyond said movable bar, and wherein each of said guides is comprised of an elongated finger, each of said fingers being pivotally mounted on said movable bar by means of a pintle pass ing through said finger and fastened to said movable bar, each guide having an upper portion on one side of said pintle and a lower portion on the other side of said pintle, said upper portion having a strand guiding aperture therethrough, each of said lower portions extending laterally beyond said movable bar and overlying said fixed bar, a plurality of transversely spaced apart stops on said fixed bar, each stop extending into the plane defined by said lower portion of said fingers, each stop being disposed adjacent a lower portion of a finger and abutting its respective finger when said guide is in its first guide position and said movable bar is at said beginning of said normal zone and abutting its respective finger when said guide is in its first guide position and said movable bar is at said beginning of said normal zone and abutting its respective finger when said guide is in its second guide position and said movable bar is at a position away from said beginning but not past said adjusting segment, whereby movement of said movable bar from said adjusting segment to said beginning will cause each of said guides not at its first guide position to abut its respective stop and be moved thereby to its first guide position, thereby maintaining each of said guides in said first guide position during said oscillation.

22. An apparatus for feeding a plurality of strands from a strand supply to knitting stations of a multifeed knitting machine while reducing and substantially equalizing the tension therein, comprising a tension equalizing cylinder, means for supporting said cylinder for rotation about its axis, drive means for rotating said cylinder about its axis, means for conducting said strands to said knitting stations, means for directing said strands from said strand supply about, and in contact with, at least a portion of said surface of said cylinder, so that tension in said strands causes the surface of said cylinder to frictionally engage said strands and deliver them from said strand supply to said conducting means and so that increased tension in any strand will increase the rate of delivery. of that strand, and decreased tension in any strand willdecrease the rate of delivery of that strand, whereby tension in all of said strands is substantially equalized, said drive means rotating said cylinder at a lineal rate greater than the lineal rate at which the knitting stations use said strands, and a main machine drive for synchronously driving said knitting machine and said drive means.

23. An apparatus for positively feeding a plurality of strands from a strand source to the knitting stations of a multifeed knitting machine having a main machine drive, comprising a transversely extending main feed roller, at least one auxiliary feed roller opposed thereto, means supporting each of said feed rollers for rotation about its axis, drive means drivable by said main machine drive for rotating each of said rollers about its axis at the same predetermined measured lineal rate, axially spaced apart portions of the surface of said main feed roller mating with axially spaced apart portions of the opposed surface of each of said auxiliary feed rollers so that rotation of said rollers will cause said mating portions to positively feed any strands therebetween at said measured lineal rate, said opposed axially spaced apart portions which mate defining strand feeding sections, axially spaced apart other portions of the surface of said main feed roller not mating with the opposed surfaces of said auxiliary feed rollers, said spaced apart non-mating portions de fining non-feeding sections, said feeding sections and non-feeding sections alternating axially of said rollers, first guide means for selectively guiding strands from said strand source to said feeding or non-feeding sections, and second guide means for guiding said strands from said feeding rollers to said knitting stations.

24. An apparatus according to claim 23, wherein said guide means comprises a transversely disposed guide supporting member, mounting means supporting said guide supporting member for transverse movement through a space comprising a feeding range and a nonfeeding range, means for transversely oscillating said guide supporting member through a zone of said feeding range, a plurality of transversely spaced apart strand guides independently movably mounted on said guide supporting member and movable relative thereto between two transversely spaced apart guide positions, in the first of said guide positions said guide being aligned with a strand feeding section of said feed rollers when said guide supporting member is in said feeding range and in the second of said guide positions said guide being aligned with a non-feeding section of said rollers when said guide supporting member is in at least a particular segment of said feeding range, and adjusting means for transversely positioning said guide supporting member in selected portions of said space, each of said guides being aligned with a. non-feeding section of said feed rollers when said guide supporting member is positioned in said non-feeding range.

25. A method of feeding a plurality of strands from a strand supply to knitting stations of a multifeed knitting machine at substantially the same tension, comprising the steps of directing said plurality of strands from said strand supply to tension equalizing means to reduce and substantially equalize the tension simultaneously in said plurality of strands, conducting said strands to said knitting stations while maintaining said strands at a substantially equal state of tension, and synchronously driving said tension equalizing means and said knitting machine.

26. A method according to claim 25 wherein the tension in said strands is reduced and substantially equalized by directing said strands from said strand supply about, and in contact with, at least a portion of the surface of a cylinder rotating at a lineal rate greater than the lineal rate at which said knitting stations utilize said strands so that tension in said strands causes the surface of said cylinder to frictionally engage said strands to deliver said strands from said strand supply and so that increased tension in any strand will increase the rate of delivery of that strand and decreased tension in any strand will decrease the rate of delivery of that strand, whereby the tension in all of said strands is substantially equalized.

27. A method according to claim 25, wherein said strands are conducted to said knitting stations by positive feeding means positively feeding said strands at the predetermined lineal rate the strands are utilized at said knitting stations while maintaining said strands at a substantially equal state of tension, said positive feeding means being driven synchronously with said knitting machine.

28. A method according to claim 26, wherein said strands are conducted to said knitting stations by positive feeding means positively feeding said strands at the predetermined lineal rate the strands are utilized at said knitting stations while maintaining said strands at a substantially equal state of tension, said positive feeding means being driven synchronously with said knitting machine.

29. A method according to claim 28, wherein said strands are positively fed by guiding them to and between opposed mating feed rollers rotating about their axis at said predetermined measured lineal rate.

30. A method according to claim 29, wherein said strands are oscillated relative to the rollers as said rollers positively feed said strands.

Claims

1. An apparatus for positively feeding a plurality of strands from a strand supply at substantially the same tension and rate of feeding to knitting stations of a multifeed machine utilizing said strands at a predetermined lineal rate, comprising tension equalizing means for reducing and substantially equalizing the tension simultaneously in a plurality of strands from a strand supply, drive means for driving said tension equalizing means, first guide means, feeding means for positively feeding said strands at said predetermined lineal rate, drive means for driving said feeding means, said first guide means guiding said strands from said tension equalizing means to said feeding means, said feeding means positively feeding said strands at substantially the same tension it received them from said guide means, second guide means for guiding said strands from said positive feEding means to said knitting stations, and a main machine drive for synchronously driving said knitting machine, said tension equalizing drive means and said feeding drive means.

2. An apparatus according to claim 1, wherein said tension equalizing means comprises a tension equalizing cylinder, means supporting said cylinder for rotation about its axis, said tension equalizing drive means rotating said cylinder about its axis at a lineal rate greater than said predetermined lineal rate, and means for directing said strands from said strand supply about, and in contact with, at least a portion of the surface of said cylinder, so that tension in said strands causes the surface of said cylinder to frictionally engage said strands and deliver them from said strand supply to said first guide means and so that increased tension in any strand will increase the rate of delivery of that strand and decreased tension in any strand will decrease the rate of delivery of that strand, whereby the tension in all of said strands is substantially equalized.

4. An apparatus according to claim 3, wherein said guide means includes a plurality of transversely spaced apart strand guides, said guides guiding strands to said mating portion of said opposed feed rollers.

6. An apparatus according to claim 3, wherein the surfaces of said feed rollers are provided with opposed axially spaced apart portions which mate to define strand feeding sections and wherein said feed rollers are provided with other opposed axially spaced apart portions which do not mate to define strand non-feeding sections, said feeding sections and non-feeding sections alternating axially of said rollers, and wherein there are provided means for selectively guiding strands to feeding or non-feeding sections.

10. An apparatus according to claim 6, including means for guiding each of said strands independently of others selectively to either a feeding section or a non-feeding section.

17. An apparatus according to claim 13, including means for aligning all of said guides simultaneously either with strand feeding sections or with strand non-feeding sections.

18. An apparatus according to claim 13, including mounting means supporting said guide supporting member for transverse movement through a space comprising a feeding range and a non-feeding range, means for transversely oscillating said guide supporting member through a zone of said feeding range, each of said guides being independently movably mounted on said guide supporting member and movable relative thereto between two transversely spaced apart guide positions, in the first of said guide positions said guide being aligned with a strand feeding section of said feed rollers when said guide supporting member is in said feeding range and in the second of said guide positions said guide being aligned with a non-feeding section of said feed rollers when said guide supporting member is in at least a particular segment of said feeding range, and adjusting means for transversely positioning said guide supporting member in selected portions of said space, each of said guides being aligned with a non-feeding section of said feed rollers when said guide supporting member is positioned in said non-feeding range.

20. An apparatus according to claim 6, wherein said first guide means comprises a transversely extending fixed bar mounted substantially parallel to the axis of said main feeding roller, a transversely extending movable bar substantially parallel to said fixed bar and movable supported thereby for movement in a transverse direction through a space comprising a feeding range followed by a non-feeding range, said feeding range comprising a normal zone and an adjusting segment, said normal zone having a beginning and an end with said end being intermediate said beginning and said non-feeding range, said adjusting segment being near said end and not extending to said beginning, a plurality of transversely spaced apart strand guIdes pivotally mounted on said movable bar, each of said guides being independently pivotable between two transversely spaced apart guide positions, in the first of said guide positions said guide being aligned with a strand feeding section of said feed rollers when said movable bar is in said feeding range and in the second of said guide positions said guide being aligned with a non-feeding section of said feed rollers when said movable bar is in said adjusting segment, resilient means constantly urging said movable bar towards said beginning, cam means cyclically moving said movable bar from said beginning to said end against the action of said resilient means and permitting said resilient means to move said movable bar from said end to said beginning, said movable bar being normally positioned in said normal zone and free to move between said beginning and end, whereby said movable bar is normally oscillated transversely through said normal zone by said cam means and resilient means, and adjusting means for selectively either releasably locking said movable bar in said adjusting segment, or releasably locking said movable bar in said non-feeding range, or freeing said movable bar for oscillation in said normal zone, each of said guides being aligned with a non-feeding section of said feed rollers when said movable bar is positioned in said non-feeding range.

21. An apparatus according to claim 20, wherein said fixed bar extends laterally beyond said movable bar, and wherein each of said guides is comprised of an elongated finger, each of said fingers being pivotally mounted on said movable bar by means of a pintle passing through said finger and fastened to said movable bar, each guide having an upper portion on one side of said pintle and a lower portion on the other side of said pintle, said upper portion having a strand guiding aperture therethrough, each of said lower portions extending laterally beyond said movable bar and overlying said fixed bar, a plurality of transversely spaced apart stops on said fixed bar, each stop extending into the plane defined by said lower portion of said fingers, each stop being disposed adjacent a lower portion of a finger and abutting its respective finger when said guide is in its first guide position and said movable bar is at said beginning of said normal zone and abutting its respective finger when said guide is in its first guide position and said movable bar is at said beginning of said normal zone and abutting its respective finger when said guide is in its second guide position and said movable bar is at a position away from said beginning but not past said adjusting segment, whereby movement of said movable bar from said adjusting segment to said beginning will cause each of said guides not at its first guide position to abut its respective stop and be moved thereby to its first guide position, thereby maintaining each of said guides in said first guide position during said oscillation.

22. An apparatus for feeding a plurality of strands from a strand supply to knitting stations of a multifeed knitting machine while reducing and substantially equalizing the tension therein, comprising a tension equalizing cylinder, means for supporting said cylinder for rotation about its axis, drive means for rotating said cylinder about its axis, means for conducting said strands to said knitting stations, means for directing said strands from said strand supply about, and in contact with, at least a portion of said surface of said cylinder, so that tension in said strands causes the surface of said cylinder to frictionally engage said strands and deliver them from said strand supply to said conducting means and so that increased tension in any strand will increase the rate of delivery of that strand, and decreased tension in any strand will decrease the rate of delivery of that strand, whereby tension in all of said strands is substantially equalized, said drive means rotating said cylinder at a lineal rate greater than the lineal rate at which thE knitting stations use said strands, and a main machine drive for synchronously driving said knitting machine and said drive means.

23. An apparatus for positively feeding a plurality of strands from a strand source to the knitting stations of a multifeed knitting machine having a main machine drive, comprising a transversely extending main feed roller, at least one auxiliary feed roller opposed thereto, means supporting each of said feed rollers for rotation about its axis, drive means drivable by said main machine drive for rotating each of said rollers about its axis at the same predetermined measured lineal rate, axially spaced apart portions of the surface of said main feed roller mating with axially spaced apart portions of the opposed surface of each of said auxiliary feed rollers so that rotation of said rollers will cause said mating portions to positively feed any strands therebetween at said measured lineal rate, said opposed axially spaced apart portions which mate defining strand feeding sections, axially spaced apart other portions of the surface of said main feed roller not mating with the opposed surfaces of said auxiliary feed rollers, said spaced apart non-mating portions defining non-feeding sections, said feeding sections and non-feeding sections alternating axially of said rollers, first guide means for selectively guiding strands from said strand source to said feeding or non-feeding sections, and second guide means for guiding said strands from said feeding rollers to said knitting stations.

24. An apparatus according to claim 23, wherein said guide means comprises a transversely disposed guide supporting member, mounting means supporting said guide supporting member for transverse movement through a space comprising a feeding range and a non-feeding range, means for transversely oscillating said guide supporting member through a zone of said feeding range, a plurality of transversely spaced apart strand guides independently movably mounted on said guide supporting member and movable relative thereto between two transversely spaced apart guide positions, in the first of said guide positions said guide being aligned with a strand feeding section of said feed rollers when said guide supporting member is in said feeding range and in the second of said guide positions said guide being aligned with a non-feeding section of said rollers when said guide supporting member is in at least a particular segment of said feeding range, and adjusting means for transversely positioning said guide supporting member in selected portions of said space, each of said guides being aligned with a non-feeding section of said feed rollers when said guide supporting member is positioned in said non-feeding range.