DE2220556A1 - Apparatus and method for feeding a plurality of strands of yarn to a knitting machine or the like - Google Patents

Description

Patent attorneys Dipl.-Ing, F. Weickma, nn,

Dipl.-Ing, H.Weickmann, Dipl.-Phys. Dr. K. Fincke

ENHO '

Dipl.-Ing. F. A. Weickmann, Dipl.-Chem. B. Huber

8 MUNICH 86, POST BOX 860 820

MÖHLSTRASSE 22, CALL NUMBER 48 3921/22

<983921/22>

Morris Philip
2519 Grand Avenue
Bronx, New York, V, St.A,

Device and method for feeding a plurality of strands of yarn to a knitting machine or the like,

The invention relates to a device and a method for feeding a plurality of yarn strands at substantially same tension and same feed rate from a storage device to a knitting machine or the like. In particular, the invention relates to a device and a method and parts thereof for reducing and equal to ^ at the same time as the voltage is approximately switched into line with a large number of strands, which are then carried out at a target pumping rate to the machine which processes these strands.

The invention is particularly concerned with the feeding of strands to a multi-thread knitting machine, although they

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can also be used in other machines in which a plurality of strands at a predetermined target delivery rate must be supplied. As is known, multi-thread knitting machines are provided with a large number of knitting systems, which are made of the strands that are supplied from a storage device who manufacture knitwear. The storage device comprises several conical or other coils for the individual strands and each strand is fed from the spool to a separate knitting unit of the machine. The knitting is sometimes also called the conveyor system, although the strand is actually not conveyed in these stations, i.e. moved further to the needles in the positive sense, but rather in which the rod is more likely to be moved into a position by a thread guide out of which the needles they draw during the knitting process.

Because of the elasticity of the thread, because of the thread material and because of the way in which it is wound on the spool, varies the tension of the yarn as it is unwound from the bobbin. In addition, the thread occasionally wraps itself does not depend freely on its bobbin, but hangs tight, so that more tension must be applied to free the yarn receive. In addition to the differences in tension in each strand of yarn as it is unwound from the bobbin, this varies There is also tension between the various strands of yarn. When the yarn goes straight from the bobbins to the conveyor of the Machine is directed, the tension in each strand changes as well as between the strands as it passes through the needles are unwound during the knitting process. As a result, the needles have different lengths of yarn pull at different tensions, which makes the knitted fabric uneven.

Attempts have been made to overcome these problems by that the yarn in measured lengths to the conveyor

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works, but these devices cannot feed and measure the yarn with the same tension. if Therefore, corresponding lengths of the yarn are under different tensions during the measurement, these are the lengths in the relaxed state, such as in the finished knitted fabric, no longer of the same length. That also leads to uneven knitting. on the other hand the problem is not solved by the fact that the tension in all yarn strands, as it is from the storage device come and are led to the knitting works, are adjusted to each other without a positive metering and conveying occurs because irregularity of the knitting machine continues to cause uneven knitting.

According to a feature of the present invention, these difficulties are overcome by reducing the tension in the Strands is first reduced and substantially adjusted to one another, and that the yarn is then positive with a predetermined target delivery rate is promoted. Since the Tension in all yarns is essentially constant and the same if the yarn is positively metered and conveyed, all knitting units receive the exact amount of yarn required for the knitting process during the entire knitting process, the yarn essentially always maintaining its tension, so that a uniform knitted fabric is produced. Additionally the invention provides a system for temporarily releasing one or all of the yarn strands from the conveying device, see above that the machine can be readjusted. The invention also provides special means to substantially equalize the tension of the yarn strands and these then to promote further positively.

According to one feature of the invention, a device is provided for this purpose provided that a plurality of strands deviate from a

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advice device with essentially the same voltage and Conveying rate promotes, this device having voltage regulating devices, by means of which the voltage of a plurality is reduced by strands and at the same time substantially aligned with one another. Furthermore are guide facilities as well as conveying devices for positively conveying these strands at a target conveying rate, the guide devices removing the strands from the voltage regulating devices to the conveyor and this conveyor, the strands with substantially the same tension, with the it has taken over these from the management institutions.

According to another feature of the invention, the tension regulating devices comprise a tension regulating cylinder, means for rotatable mounting of this cylinder about its axis, drive means for driving this cylinder and devices for Feeding the strands from the storage device to this cylinder and around at least a portion of its surface so that the tension in the strands frictionally engages between the surface of the cylinder and the strand. This moves the strands from the storage device to the Guiding institutions directed, with an increase in Tension of each strand also increases the delivery rate, a decrease in tension also decreases the delivery rate, and thereby the tension in all strands is essentially the same.

According to a further feature of the invention, the conveyors comprise a main feed roller extending in the transverse direction, at least one auxiliary feed roller resting against it, Means for the rotatable mounting of these rollers about their axis, as well as means for driving the rollers. According to the invention

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is at least part of the surface of the main feed roller engaged with at least part of the opposing surface of the auxiliary feed roller so that by rotation of these roles, the engaged portions result in a positive conveyance of the strands in between Has.

According to a further feature of the invention, the opposite one another Surfaces of these feed rollers have a plurality of axially separated sections which are connected to one another are engaged, and which the transport sections represent for the strands. Furthermore, the feed rollers have other axially separated sections, which are not in engagement with each other and are not transporting Form sections, the transport sections and the non-transporting sections in an axial direction Alternate direction. There are means provided to the strands either the transport sections or the non-transporting To feed sections.

According to the invention, a method is also proposed to a multitude of strands at essentially the same tension and promote the funding rate positively. The process comprises the following process steps

The voltage in a plurality of strands is reduced and, at the same time, essentially switched into line; afterward the strands are positively conveyed at a predetermined target delivery rate, the strand tension being essentially the same is held.

Further features of the invention are directed to the various details of the apparatus as well as the method.

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Several embodiments of the invention are shown in FIG Drawing shown and described in more detail below.

Show it:

Fig. 1 is a partial perspective view of a device, with some strands and some strand guide fingers are recognizable;

Fig. 2 is a partial cross-section along line 2-2 of Fig. 1, with the guide fingers initially their oscillation zone or normal zone and the cam disk at its lowest point, where the left finger has been omitted to show the recess in the feed roller;

Figure 3 is a partial plan view taken along line 3-3 in Figure 2;

Fig. 4 is a partial longitudinal section along the line 4-4 in Fig. 2;

5 shows a partial section corresponding to FIG. 2, with the guide fingers at the end of the vibration zone and the cam disk is at its highest point;

FIG. 6 is a partial view corresponding to FIG. 5, with the guide fingers are pivoted into their fiegulierbereich and the cam is disengaged;

Fig. 7 is a partial view corresponding to Fig. 2, the Guide fingers are pivoted into a non-transporting position;

8 shows a development of the cam disk.

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In the following description, the "rear part" of the device is always the part shown in FIG. 1 on the right-hand side or shown in FIG. 4 on the left-hand side Part designated. The "front" or "front" is correspondingly shown in Fig. 1 on the left, in Fig. 4 on the right · and finally, the "forward direction" is the direction from the rear to the front. The "left side" is in 1 facing the viewer and shown on the left in FIGS. 2, 3, 5, 6 and 7, while the "right side" in FIG is the side facing away from the viewer or the side shown on the right in FIGS. 2, 3, 5, 6 and 7. The "cross direction" runs between left and right and the "longitudinal direction" between the back and the front side.

In the following, the structure of the device and then its function will first be described.

The actual structure of the device results in particular from FIGS. 1, 2 and 4. The device is on a support frame mounted, which by the vertical posts 10, the longitudinal horizontal struts 12, the formed in the transverse direction horizontal struts 14 and transverse plates 16, 18 and 2o, the latter are connected to the struts 12 extending in the longitudinal direction. The various elements that make up the support frame are rigidly connected to each other in any way, for example by bolts or welded connections. At the back of the Support frame are fixed at a distance in the transverse direction perpendicular support brackets 22 on the plate 16, in which the journals of the shaft 25 are freely rotatable about a horizontal axis. The shaft 25 belongs to the cylinder or the drum 24, which is called a tension regulating cylinder 24 for reasons which will be explained later. On the left end

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the shaft 25, outside of the support bracket 22, a spur gear 26 is arranged coaxially with the V / elIe.

At the front end of the support frame are spaced in Transversely extending, 'vertical support brackets or plates 28 (right) and 30 (left) are arranged. The wave 32 of the transverse main feed roller 34 is mounted in these support brackets 28 and 3o so that they are about a horizontal Axis can rotate. To the left of the support bracket 3o are initially a small spur gear next to one another and coaxial with the shaft 32 36, then a large spur gear 38 and a pulley 4o attached. The pulley 4o is supported by a belt driven by drive 44 which, as will be explained later becomes, an independent motor, a variable speed control gear driven by such a motor or a control gear which is driven by the main drive of the knitting machine. One Rotation of the pulley 4o causes the spur gears 36 and 38, the shaft 32 and the main feed roller to rotate Between the cylinder 24 and the main feed roller 34 is open the plate 18 a longitudinally extending support bracket 46 is arranged in which the shaft 48 of the spur gear 5o is rotatably mounted. The teeth of the spur gear 38 mesh with the teeth of the spur gear 5o, which in turn with the Comb spur gear 26. If the pulley 4o the spur gear 38 and thus dB main feed roller 34 in the indicated by the arrow drives designated direction, the spur gear rotates 5o in the direction indicated by the arrow 54 and the spur gear 26 and the cylinder 24 rotate in the direction of arrow 56. It is noted that the main feed roller

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and the cylinder 24 rotates in the same direction, counterclockwise in Fig. 1 and clockwise in Fig. 4.. - "

Above the main feed roller 34 is a support bracket 28 vertical slot 58 and, accordingly, a vertical slot 6o arranged in the support bracket 3o, the slots 58 and 6o are opposite. The support brackets 28 and 3o also have in each case a further, forwardly directed and inclined to the slots 58 and 6o slots 62 and 64, respectively. In a bearing block 66 is slidably disposed in each of the slots 58, 60, 62 and 64. In the bearing blocks of the slots 58 and 6o the respective ends of the shaft 68 of a first auxiliary feed roller 7o are received. Accordingly, in the Bearing blocks of the slots 62 and 64 support the shaft 72 of a second auxiliary feed roller 74. The waves 68 and 72 and the associated auxiliary feed rollers 7o and 74 are parallel to Shaft 32 of the main feed roller 34. The bearing blocks 66 and therewith the auxiliary feed rollers 70 and 74 are also supported by compression springs 76, which are each arranged between the upper sides of the bearing blocks 66 and the cover plates 78 and 8o, resiliently against the main feed roller 34 is pressed. Press the compression springs 76 in this way the outer surfaces via their associated bearing blocks of the auxiliary feed rollers 7o and 74 resiliently into contact with the outer surface of the main feed roller 34.

On the left ends of the shafts 68 and 7o and coaxially thereto, spur gears 82 and 84 are arranged, the teeth of which with the Teeth of the small spur gear 36, which is mounted on the shaft 32 of the main feed roller 34, are in mesh. A rotation of the main feed roller 34 and thus of the spur gear 36 in the direction indicated by the arrow 52 (in FIG. 4 clockwise) causes a rotation of the auxiliary feed

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roll 7ο and 74 in the direction indicated by arrow 85 Direction (in Fig. 4 in the G-counterclockwise direction), ao that all located between the main and auxiliary feed rollers Strands are promoted forward.

In each of the bearing blocks 28 and 3o, behind the main feed roller 34 »a vertical slot 86 is provided into which the respective ends of a pair of transverse beams 88 and 90 are inserted. The carrier 88 is solid and the carrier 9o is movable. The carrier 88 has an L-profile, as best shown in FIG. 4, the horizontal Leg 91 of the L-profile points to the rear and one shoulder 92 forms. The fixed bracket 88 is cap screws 94 attached to the support brackets 28 and 3o, so that the carrier 28 is fixed relative to the support frame. The mobile carrier 9o is located behind the fixed support 88 and is slidably or movably mounted on the shoulder 92 formed by this, so that it can swing in the transverse direction, i.e. so left to right and right to left. The vertical Schliüze 86 are dimensioned so that the distance in the longitudinal direction between the front vertical cheek 96 and the rear vertical cheek 98, which * - common to the slot 86 form, is approximately the same size as the thickness of the carrier 88 and 9o taken together in the longitudinal direction of the device. on in this way, the movable support 9o cannot slip backwards from the shoulder 92. It is noted that the fixed support 88 or more precisely its horizontal leg 91 laterally (or downwards, as shown in FIG. 4) under the movable carrier 9o extends.

The right end of the movable beam 9o has a horizontal one Open the slot. On the fixed support 88 is a lever Io2

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fastened by means of a bolt or tenon Io4, which passes through the horizontal slot loo, the Pin Io4 penetrates the fixed support 88 and is fixed in this. The diameter of the pin Io4 is about the same the vertical width of the slot loo, so that the movable support 9o is prevented from moving relative to the fixed support 88 moved up. The lever Io2 can be rotated around the pin Io4 and is provided with two hub or cam surfaces Io8, which can engage against the stop pin Ho on the movable support 9o when the lever Io2 is pivoted, as described below.

At the left end of the solid support 88 is a plate or disk 112, which extends backwards over the upper edge of the movable support 9o. This disk 112 is connected to the fixed support 88 by means of the bolt 114. The disk 112 prevents the movable carrier 9o relative to the fixed carrier 88 on the left side of the pair of carriers moved in the vertical direction.

A horizontal shaft 116, which extends in the transverse direction and which carries a spur gear 118, is also rotatably mounted in the support bracket 3ο. Its teeth mesh with the teeth of the spur gear 36 so that its rotational movement can be transmitted to the spur gear 118. On the inside, ie on the right side of the spur gear 118, an annular cam disk 12o is arranged concentrically with the shaft 116. This cam disk 12o changes its thickness over the circumference from a minimum to a maximum, the minimum and maximum being opposite one another. This thickness is measured in a direction parallel to the axis of the shaft 116. The different thickness of the annular cam disk 12o has the effect that its inside represents an annular cam surface or control path 121, which faces the free left end 122 of the movable carrier 9o

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is and rait djesem cooperates. The minimum of the cam disc 12o forms the lowest point 123 of the controllable, while the maximum represents the highest point 124 of the control path (see Pig. 2, 5 and 8).

A helical spring 126 designed as a tension spring is arranged over the right-hand ends of the supports 88 and 9o, one of which One end connected to the movable support 9o by bolts 128 and the other end connected to the fixed support 88 by bolts 13o is (Figures 2, 3 »5, 6, and 7). The spring 126 biases the movable carrier 9o with a constant force in the direction forward to the left, and presses the left free end 122 of this carrier against the control path 121. When the cam disk 12o from a position in which the lowest point 123 of the control track is in contact with the end 122 of the movable beam, continues to rotate, the movable carrier 9o is shifted to the right by the increasing height of the control path until the the highest point of the cam rests against the end 122. When the cam disc 12o continues to rotate, will the movable carrier 9o is pushed to the left again by the spring 126, the end 122 of the control path following. It can Therefore it is assumed that during the rotation of the cam disc 12o by the interaction of the control path 121, the End 122 of the movable carrier and the spring 126 elastically pretensioning it, the carrier 9o executes a transverse oscillation .

Several strand guides arranged at a distance in the transverse direction, which are in the form of guide fingers 132 are on the movable support 9o via bolts or pins 134 pivoted. Each bolt sits in a hole in a finger and is screwed into the movable carrier.

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Between the head of each bolt 154 and the finger 152 sits a spring washer 156, the tension of which prevents the finger 152 performs an angular deflection without a control force acts on him. The axis of rotation or the pin divides each finger into a lower arm and an upper arm, whereby the lower arm extends laterally under the bottom of the movable support 9o and over the horizontal leg 91 of the solid support 88 protrudes. On the left side of the lower arm each finger 152 is in the horizontal leg 91 of the fixed support 88 each have a stop pin 188 which extends backwards and into the plane of this lower arm protrudes. Next to the upper arm of each finger, to the left of it, is a corresponding stop-r pin 14o fixed in the movable carrier 9o. When the finger 152 is vertical, it rests on the stop pin 14o, so that the finger 152 cannot rotate counterclockwise, as can be seen from FIGS. 2, 5, 6 and 7. If the movable beam is on the far left, corresponding to the lowest Point 125 of the control path 121, and the finger 152 is in a vertical position, is the left edge of the lower one Arm of the finger 152 on the stopper 158. Then when the movable carrier is shifted to the right, as in the Figures 5 and 6 shown and the finger 152 is in a vertical position, this left edge of the stop pin 158 moved. In this position each finger can For example, the finger 152A can be pivoted clockwise into the position 152B shown in phantom (FIG. 6).

Each finger 152 has a cord & guide opening in its upper arm which is formed by a bore with a thread guide eyelet 142. The strand guide openings are located

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approximately at the level of the gap which is caused by the adjacent Main feed roller 34 and auxiliary feed roller 7ö is formed. The upper end of each finger is approximately at the point indicated by 144 between the stop pin and the eyelet 142. bent forward so that the upper end 146 of the finger is inclined closer to the front of the machine, so that it can be more easily operated manually by the operator, as will be described later.

The main feed roller 34 has several one behind the other in the axial direction Grooves, channels or recesses 148 so that their surface alternates in the axial direction There are recesses 148 and elevations 15o. The / changes of Recesses 148 are preferably beveled, as shown at. Corresponds in the illustrated embodiment the number of recesses and thus the increases in the number of fingers 132.

The bumps on the main feed roller touch the opposite ones Areas of each of the auxiliary feed rollers so that transport sections lying one behind the other are located in the transverse or axial direction result. The recesses touch the surfaces of the auxiliary feed rollers not, so that in cross or Axially one behind the other dead, i.e. non-transporting sections arise. The transport sections and the dead sections alternate in the axial direction along the feed rollers.

Each guide finger 132 can be aligned with either a transport section or a dead section of the feed rollers as described below. The orientation of the guide fingers is determined by the fact that the

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Garnführungöse 142 either an increase or recess of the main feed roller 34 is opposite. If a yarn guide eyelet 142 lies exactly opposite one elevation in the longitudinal direction, the strand running through this eyelet will slide to this elevation, while in the other case it will be guided to a recess. When the guide fingers 132 are vertical and the control track 121 is in its lowest position, the strand guide is aligned with an elevation or a transport section. All guides in Figure 2 assume this position. When the control track moves the movable carrier 9o and thus the guide fingers 132 to the right into the position shown in FIG. 5 , corresponding to the highest point of the control track, each strand guide remains aligned with its corresponding elevation or transport section.

During the oscillating movement, which was described in the previous section, the lever Io2 is in the position in the Figures 2 and 5 position shown. When the lever Io2 is moved up to the position shown in Fig. 6, the nose or cam surface Io6 touches the stop pin Ho, whereby the movable carrier 9o is moved slightly further to the right from the position shown in FIG. The nose Io6 locks the movable carrier - releasably - in the position shown in FIG. 6, with the end Io2 of the movable The carrier 9o is touched neither by the highest nor the lowest point of the control path 121. When the moving Carrier 19o is in the position shown in FIG. 6, it is in the adjustment range of its transverse movement. In this Position while the finger is vertical, as shown at 132 A, is the strand guide or the yarn guide eye 142 still aligned with the associated ridge on the main feed roller. In this position the operator can by hand by exerting a lateral pressure on the upper arm of the guide finger 132 in the with

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132 B pivot position, so that the guide, in particular the yarn guide eyelet 142 to a recess or not transporting section is aligned. In the illustrated embodiment, the left edge of the lower arm touches of the guide finger 132 B the associated stop pin 138, so that its angular movement is limited.

When the lever Io2 is raised into the position shown in FIG. 7, the movable carrier 19o is displaced further to the right by the lug or cam surface Io6 in cooperation with the stop pin Ho and at the same time the guide fingers 132, whereby this carrier is displaced further to the right in the position shown in FIG Fig. 7 position shown - releasably - lock. In this position, all guide fingers 132 are aligned with recesses or non-transporting sections. In order to prevent the right edges of the lower arms of the guide fingers 132 nschlagstifte to the ^A strike 138, in the embodiment shown each guide finger is provided with a recess 153 below.

The invention can be used with any type of strand feed. In the present example, the support frame is above a Set up a yarn feeder, which has several conical yarn bobbins that deliver the yarn. Since it is immaterial whether the If the skeins of yarn are wound onto conical or somehow differently shaped bobbins, the different bobbin shapes are intended for the All are called conical because of uniformity. Such a strand feed is shown schematically in FIG. 4, wherein the conical bobbins 154 provide multiple strands S.

The plate 18 (FIGS. 1, 4) has a plurality of bores at a distance from one another, a strand guide 155 being arranged in each is. Two spaced one above the other, extending in the transverse direction struts 156 and 157 (Fig. 1), the

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.Ends connected to the post Io are connected to several ,, provided in the transverse direction spaced bores, wherein in each bore of the lower strut 156 one Strand guide eyelet 158 and in each hole in the upper strut

157 a strand guide eyelet 16o is arranged. Further yarn guides 161 are suspended from a strut 162 which is also attached to the post Io above the strut 157. Further strand guide eyelets 163 are located in a strut 164 extending in the transverse direction, the ends of which with the Support brackets 28 and 3o are connected in front of the feed rollers (Fig. 4). To simplify the drawings, strands S only shown in FIGS. 1 and 4. Each strand S runs one after the other from a delivery roll through a guide 155 under the cylinder 24, then through a guide 158 (not shown in Figure 4), clockwise and in contact with the cylinder 24 at an angle of about 33o around it, then up through a guide 16o, the guide 161, the guide eye 142 of the guide finger 132, through the gap which is formed by the feed rollers 34 and 7o, then through the gap between the feed rollers 34 and 72 and finally through the strand guide eyelets 163. The guides

158 and 16o guide the strands around the surface of the cylinder 24 at an axial distance from one another. From the strand guide eyelets 163 strands S run either directly or indirectly via further strand guides (not shown) to form one Knitting mechanism of a knitting machine processing several threads (not shown). It is not believed necessary that To show knitting machine and its knitting, since the invention can be used with any such machine and their Working method is known. However, the preferred knitting machine is a multi-thread circular knitting machine) is used, which has one or more needle banks, the needle banks rotating and the knitting units

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(knitting stations) are stationary.

If necessary, each strand S can, before it comes into contact with the cylinder 24, a weak tensioning device (not shown) happen, which for the purpose of a more even operation on the strand a slight frictional resistance brings up. For example, at one or more points in their path between guide 16o and guide 132, anyone can The strand continues to run through a shutdown device (not shown). These are conventional safety devices, which shut down the machine in the event that any strand breaks or for any other reason no longer works emotional. Each guide 161 can, for example, have such a shutdown represent facility.

In the following, the operation of the device is described, wherein the strands S in the manner described by the machine and the machine's drive is switched on. The pulley 4o, the various spur gears, rollers and cylinders rotate in the direction previously described. The movement of the rollers, cylinders and strands are called a delivery rate is described. The delivery rate is a straight line length or distance based on a unit. as Unit, the time or the movement of a certain element of the device can be selected, for example the Revolution of a specific role, especially the revolution of the knitting machine. Of course, all funding rates should be on be related to the same unit.

The delivery rate of a strand is the fed or processed Length of this strand in relation to the unit. The feed rate of a roller or cylinder is the circumferential distance that it moves a point on its surface, based on

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the unit, travels. A roll with a diameter of 5.08 cm has a circumference of pi χ 5 »o8 cm, so that a Point on the surface of the roller pi χ 5, o8 cm at each Rotation of the roller. If the revolution of this roller is chosen as the unit, then this is the delivery rate Roll equal to pi χ 5.08 cm per revolution. If the Time is chosen and the roller makes Io revolutions per minute, then the delivery rate is Io χ pi χ 5 »o8 cm per minute.

In the illustrated embodiment, the cylinder 24 is approximately 7.5 cm (3 inches) in diameter, the main feed roller about 5.08 cm (2 inches) and each of the auxiliary feed rollers 7o and 74 about 3.8 cm (1.5 in). The spur gears 36 and the spur gears 82 and 84 driven by them are designed so that with one revolution of the spur gear 36 each of the spur gears 32 and 34 makes 1 1/3 revolutions. The corresponding Rollers 34, 70 and 74 therefore have the same feed rate so that there is no slippage between these rolls. With regard to this, it can be said that the strands which run between the opposing rollers have the same measured and delivered rate as the rolls themselves. In this embodiment, the Diameter of the feed rollers measured at the elevations, as these represent the sections of the rollers that do the transport accomplish. The apparatus can be adjusted so that the main feed roller 34 has any feed rate. This delivery rate should then represent the target delivery rate. The spur gear 38, which is arranged coaxially to the roller 34 and revolves at the same speed, has the same diameter as the spur gear 26, which in turn is coaxial is arranged to the cylinder 24 and drives it. The spur gear 38 drives the spur gear 26 via the intermediate gear 5o,

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so that each revolution of the spur gear 38 results in one revolution of the spur gear 26 and thus of the cylinder 24. There the diameter of the cylinder 24 is 50 percent larger than the diameter of the main feed roller 34 »is the feed rate of the cylinder 24 is 50 percent greater than the feed rate of the feed roller 34.

All strands, particularly the strands of knitting yarns to which the invention particularly relates, have a certain amount Elasticity. Knitting yarns are particularly elastic in the sense that they are light by a relatively small force can be stretched. When the strands are wound on spools, this is done under a certain minimum tension. According to the present invention, the cylinder for regulating the tension comprises means by means of which the Tension in the strand is reduced so that it has practically no or minimal tension when it is of its Coil is fed to the guide finger. In other words, the strand is essentially completely relaxed. Also, all of the strands will be at essentially the same tension fed.

The tension control cylinder 24 is preferably made of steel with a smooth surface so that the strand is loosely seated has practically no friction on the surface of the cylinder 24 and can slide relative to the surface. If on the other hand When tension is applied to the strand, the friction between the strand and the cylinder increases and the rotating one increases The surface of the cylinder takes the strand with it from its spool in its direction of rotation. The greater the tension the greater the friction, and the length of the strand conveyed by the cylinder increases at the same time. If the

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The tension in the strand is so high that it is firmly attached to the cylinder, is applied and there is no more slip, then the cylinder obviously delivers the strand with 'the delivery rate of the Cylinder, which in the example shown is 1 1/2 times the The target feed rate of the main feed roller 54 is. That is the highest delivery rate of cylinder 24. The lowest delivery rate is of course equal to zero, and it is then reached, when the strand is so loosely wrapped around the cylinder that there is practically no friction between the strand and the cylinder. In other words, the cylinder 24 acts as a winch or capstan.

When a certain strand through the feed rollers at the target feed rate is delivered, this strand is pulled through the yarn guide I6o at this target delivery rate. If the If the strand does not unwind freely from its spool, the tension around the cylinder 24 increases immediately, and this increase in tension causes the cylinder 24 to deliver this strand to the guide 16o at an increased delivery rate. If the increased delivery rate is greater than the target delivery rate, relaxed the strand is immediately between cylinder 24 and guide 16o. This relaxation then in turn reduces the tension of the strand around the cylinder 24 and thus also the delivery rate this strand to lead Io6. However, if the strand through the cylinder 24 to guide I6o with a below the target delivery rate is delivered at a lying rate, the feed rollers act to increase the tension on this strand. This increase in tension immediately leads to the strand around the cylinder is pulled tighter, which results in an increase in the delivery rate.

The described fluctuations in the strand tension around the cylinder 24 around automatically adjust themselves and act like one

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Feedback device to the delivery rate and the voltage to regulate the strand conveyed by the cylinder 24; The system is practically in equilibrium, with the delivery rate of the line for guidance I6o corresponds almost exactly to the target delivery rate and every change is constant and immediately automatic is corrected. It should also be noted that the tension in the strand is essentially at a minimum since any increase in tension would also increase the rate of delivery of cylinder 24 and so on. It she admitted that the strand always has some tension as it extends from cylinder 24 to guide I6o, through eyelet 161 to guide 132, and because of the weight of the strand itself. It should also be said that the tension in the strand is just big enough to prevent the strand from sagging. What has been described here in connection with a particular strand, applies to all of the strands conveyed through the cylinder 24, so that all of the strands fed to the guides 132 are substantially have the same voltage.

In the illustrated embodiment, the strands that come from their bobbins are wrapped around ilen cylinder 24, that their wrap angle is about 33o. It is obvious that each strand also has a larger or smaller wrap angle with the cylinder, and it can even happen that a strand has a wrap angle of more than 360 ° if it is completely wrapped around the cylinder 24 more than once. This could be the case, for example, if the guides 158 would be omitted. It is only necessary that the strands by guides or other facilities of their coils are led to a cylinder and at least partially around its surface, so that the tension

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the strand itself causes a frictional engagement with the cylinder surface and the strands from their bobbins subtracted from. An increase in voltage in each strand increases then the delivery rate and a lowering of the voltage reduces the delivery rate. Essentially this increases the tension in regulated in all strands. '.

It is further evident that the cylinder must rotate at a higher feed rate than the feed rollers or any device which processes the strands supplied by the tension regulator cylinder 24. If the Cylinder 24 rotates at a lower delivery rate, then the delivery rate of the strands transported by it is too low. There is no theoretical maximum speed for cylinder 24, although it is clear that in practice one does exist. It can be seen that the cylinder can rotate so fast that there is a constant frictional engagement with the strands and these with a The rate far above the target rate can be promoted. Of course, this speed is not reached.

As for the conveyors, the axial length of a ridge is 150 plus recess 148 (including the Bevel 152), for example 1.9 cm, the axial length of the elevation itself being 1.1 cm and the recess being 0.8 cm. In other words, every 1.9 cm there is an elevation and also a recess. The pins 134 are also spaced apart The stop pins 138 and 14o are also arranged from 1.9 cm. When the guide fingers 132 are in their upright position. In the normal position, the openings 142 are also spaced 1.9 cm apart. With these dimensions, 48 strands can be used be transported by the feed rollers and the cylinder 24, the length of which itself is about 90 cm plus a few cm

2 0 9 8 A 6/0 8.7-8

as security.

If a guide finger 152, or more precisely its guide eyelet 142, is aligned with an elevation, then the cord will metered and fed by the feed rollers.

When the movable support 9o, which carries the guides, is in its left position, as shown in FIG. 2, with the control path 121 in its lowest position, then each G-arnführungsöse 142 to an increase 15o aligned so that it is about 1.5 mm from its left edge. The height of the cam or the transverse height difference between the low point 123 and the high point 124 about o.65 cm. When the cam disk is in its upper position, as shown in Fig. 5, then the movable support 9o has moved about 0.65 cm to the right and each guide eye 142 is about 0.8 cm from the left edge of the Increase 15o. One revolution of the cam plate 12o causes the movable carrier 9o to move in the transverse direction by an amount swings back and forth from about 0.65 cm. This oscillation amplitude of the movable carrier 9o can be the normal supply range The position shown in FIG. 2 is the beginning of this normal feed area, that shown in FIG Position represents the end of this feed area.

When the lever Io2 is pivoted into the inclined position in FIG the nose Io6 comes with the stop pin Ho in contact and temporarily locks the carrier 9o in this position. As a result, the carrier 9o is about 0.4 mm behind shifted to the right, whereby the end 122 comes free of the control path. The cam disk 12o can thereby rotate continue. In this position, when the guide finger 132 is perpendicular, as indicated at 132 A in FIG. 6, the Guide eye 142 still with the associated elevation

209846/087

aligned while the movable support 9o does not vibrate. 'The operator "moves the lever Io2 into this position, when it intends to align one or more individual strands. In this position the operator can Manually move the end 146 of the desired guide fingers to the right as shown at 132B. This will make the guide eyelet 142 of the corresponding guide finger shifted by about o, 65 cm, so that this eyelet is now assigned to an Is aligned recess of the main feed roller 34 and the corresponding strand is not conveyed by the feed rollers. The operator can use the guide fingers as well move back from position 132 B to position 132 A by hand.

When the movable support 9o is in the position shown in FIG. 6 and a guide finger is in the position, for example 132 A, then the strand guided thereby is still aligned with an elevation of the main feed roller 34. Of the The strand continues to be directed to a conveying section of the feed rollers and conveyed at the desired conveying rate. if the guide finger is pivoted into position 132 B ', the strand is no longer conveyed. If the guide finger then is again pivoted back into position 132 A, the strand from the non-transporting section of the Feed rollers into the transport section ga, the strand moving up along the bevels 152. To the The sawing can facilitate the return of the strand from the dead, non-transporting section to the transport section 152 may be roughened, although that is not absolutely necessary. In the example shown here, the axial length of the bevel 152 be about 1.5 mm. As can be seen, in the position shown in FIG Guide fingers 132 and thus each strand individually and optionally to a non-transporting or a transporting one The section of the feed rollers. In the

209846/0878

The one in Pig. 6 shown position of the movable support 9o therefore corresponds to the regulation range within the whole Oscillation range of the movable carrier 9o.

The lever Io2 also represents a device to to pivot all guides at the same time in a non-transporting position, in which each guide to one is aligned with the non-transporting section of the feed rollers. This is done in that the lever Io2 in the position shown in Fig. 7 is moved so that the cam surface Io8 in cooperation with the stop pin Ho moves the movable carrier 9o by about 0.65 cm from the position shown in FIG. 6 to the right, at the same time Carrier 9o is locked in this position. All guide fingers 132 are thereby moved to the right, so that in the vertical or normal position of the guide fingers their openings 142 each to the recesses of the main feed roller i.e., aligned with the non-transporting sections of the feed rollers. With the specified dimensions each guide should be pivoted back to its vertical position either manually or automatically before the lever Io2 is moved to the position shown in FIG. Otherwise, the guide located in the tilted position 132 B would be aligned to a transport section. It is obvious that with differently chosen dimensions, for example with a greater axial length of the recesses 148, it would not be necessary to first insert the guides into the vertical ones Swing positions back.

It is also apparent that when the guide finger 132 would not have a recess 153, the right side of the guide finger with its adjacent stop pin 138 would come into contact when the movable carrier out of the

209846/0878

in Pig. 6 shown in the Pig. 7 position shown is moved. This would automatically put the guides in the position 132 B pivoted. The recess 153 prevents this concern. Of course there could be a change in the Dimensions of the device make such a recess unnecessary, so that it would be unimportant whether the guides in a movement Pivot into the position shown in Fig. 7 or not, since these guides always lead to a non-transporting one Section ". The lever Io2 can be taken directly from the in Pig. 5 can be moved into the position shown in FIG. 7 without being stopped in the fiegulierbereich as shown in FIG.

If the lever Io2 is either moved from the position shown in Fig. or according to FIG. 6 in the position shown in FIG is pivoted, the stop pin Ho is neither with the nose still the nose Io8 in engagement, so that the spring 126 the movable The carrier moves to the left until its left end 122 touches the control path 121. At the same time the moving begins Carrier 9o controlled by the control path 121 to swing. It should be noted that the cam disk 12o continues to rotate even then can when the movable carrier is in its position according to FIG. 6, 7, but this does not have any effect, since the end 122 of the carrier 9o does not touch the control path 121.

From the foregoing description it can be seen that the fixed Carrier 88 has fastening means through which the carrier 9o, on which the guides are arranged, is movable in the transverse direction is held so that it is between a leftmost position at which the end 122 the lower point 123 of the Control track (Fig. 2) touches and a rightmost position (Fig. 7) can move. The entire sliding area

209846 / 087.8.

of the movable carrier contains a conveying area and a non-conveying area. When the guide fingers are in their normal or vertical position, they are in the conveying area with a transport section of the feed rollers aligned, while in the non-transporting area accordingly with a non-conveying section of the feed rollers are aligned. The funding area includes a normal zone and a regulation area. The normal zone corresponds the transverse area in which the control path 12o moves the movable carrier 9o, i.e. the area between the left Position (Fig. 2) and the right position (Fig. 5). The end of the normal zone is between the start of the normal zone and the non-promotional area. When the movable carrier 9o is in the normal zone, the entire device is in their normal delivery condition. The regulation area of the conveying area is near the end of the normal zone. in the illustrated embodiment closes this normal zone does not enter the regulating area so that it lies between the normal zone and the non-promoting area.

It is obvious that the regulation area if necessary also further to the left compared to the embodiment shown can be. For example, when the movable support 9o is in the position shown in Figure 5, each guide finger 132 can selectively and independently move to a non-conveying one Position can be pivoted. However, since the cam disc continues to rotate, it becomes highest each time it is Point 124 is opposite the end 122, rub against this. That causes unnecessary wear and tear. The regulation area can compared to the position shown in Fig. 5 also be shifted further to the left and can continue even with the normal Coincide with the feeding area. However, the twist would

209846/0878

. the KoGkenseheibe at least partially a swinging movement of the carrier 9o, which could be undesirable. The feeding area and the regulating area can also coincide, can overlap or can be separated from one another in the transverse direction. It should also be noted that each guide can be moved between two positions. In the first, or normal, position, the lead is to one Transport section of the feed rollers aligned, provided that the carrier 9o is in its feed area, in the second. Position, however, the guide is aligned to a non-transporting section when the carrier 9o is at least is in the regulation area.

Set the lever Io2 together with the stop pin Ho ■ Adjusting devices for a transverse positioning of the carrier 9o represent, namely for a displacement in parts of the whole possible transverse path of the carrier. These regulating devices can optionally place the movable carrier in the regulating area releasably lock, as shown in FIG. 6, you can lock it in the non-transporting position according to FIG or they can release the movable support for oscillation in the normal zone, as FIGS. 2 and 5 show. When the movable support is either in the regulation area or in the non-transporting area and the lever Io2 is released in accordance with the position shown in Fig. 5, the carrier 9o automatically moves into its feed area and begins to vibrate. Since this oscillating movement moves the carrier 9o between the positions shown in FIGS. 5 and 2 moves, so the left edge of the lower arm of each guide finger, provided it is in its pivoted position J32B is located, touch the assigned stopper 138. As the mobile carrier continues its movement towards the beginning of the normal zone, the contact leads between

20 98A6 / 0378

- 3ο -

the stop pin 138 and the guide finger automatically, that it is returned to its normal position 132A. This means that there are means which automatically move each guide finger into its vertical position during the oscillating movement Move back position and hold there. This normal movement of the guide fingers in their normal or vertical Position can be used when the movable carrier moves out of the regulation area into the normal zone for one normal conveying process moved back. However, it can also be used to hold all guide fingers in front of the movement of the wearer 9o vertically from its regulation area to the non-transporting area. This happens because the carrier 9o first moved out of the regulating area into the normal zone and then into the non-transporting area will. In the event that the conveying area coincides with the supply area collapse, the stop pins 138 must be removed, otherwise it would be impossible for the guides to shift while the cam continues to rotate. It is understood that the structure of the device also provides means with which the guides with the Uransportsektionen and the non-transporting sections the feed rollers can be aligned. The guides can either be aligned individually and independently be or together. This alignment is accomplished in that a relative movement between the guides and the feed rollers.

Preferably, the main feed roller 34 is made from steel the surfaces of the elevations being very smooth. The surface of the auxiliary feed rollers is also preferably smooth, however made of rubber or other friction material. This material is used so that the strand, provided that it becomes a

0 9 8 4 6/0878

- 51 -

Elevation is aligned, between this elevation and the opposite surface of the auxiliary feed rollers is held. Since all of these rollers rotate at the same feed rate, the firm hold causes that these rollers convey and measure a defined strand length per revolution. To this ability of metering the feed rolls To emphasize, it seems desirable to refer to this delivery rate as the target delivery rate. In the illustrated In the exemplary embodiment, the surface of the auxiliary feed rollers touches the elevations of the main feed roller. However, must the distance between the surfaces of the auxiliary feed rollers and the elevations of the main feed roller is really just that be dimensioned so that depending on the diameter and .Material of the strands they are safely gripped. When they are so close are advanced against each other so that they grasp the strands securely, the rollers are considered to be in engagement.

In the non-transporting sections are the Recesses do not engage the opposing surfaces of the feed rollers so that the strands do not travel at the desired feed rate be transported.

In the illustrated embodiment, the spur gear 36, which is mounted on the shaft of the main feed roller 34, engages, into the spur gears 82 and 84 of the auxiliary feed rollers and drives this. While this drive arrangement is preferred, it is not absolutely necessary. The auxiliary feed rollers and 74 could also be idle rollers (not shown) which are driven primarily by contact between the surfaces the auxiliary feed rollers and the main feed roller are driven.

209846/0878

Both arrangements result in drives for all roles.

In the embodiment shown there are two auxiliary feed rollers. It is clear that only one auxiliary feed roller is required is, or that more than two auxiliary feed rollers are also used can be (not shown). The purpose of the rocking movement of the carrier 9o is to move the strands also in the transverse direction to oscillate when they are conveyed through the feed rollers. The main reason for this is that through the Reciprocation of the strands is the wear and tear of the engaging surfaces caused by the movement caused by the intervening strands. This is to prevent the strands from grooving either Dig into the surface of the auxiliary feed rollers or the main feed roller to extend their life.

Of course, any or all of the auxiliary feed rollers can have annular recesses (not shown) which coincide with the recesses of the main feed roller. as well the recesses in the main feed roller may be absent (not shown) with the recesses instead in each of the Auxiliary feed rollers are arranged so that areas are created in which these roles do not touch. In other words, the recesses can either be in all roles or be provided alone in the main feed tube, or else alone in all auxiliary feed rolls. It is only necessary that the radial depth of the recesses in the roller pairing is sufficient is large, so that areas arise in which no contact and thus no metering and conveying of the strands takes place.

Since the purpose of the oscillating movement is primarily to achieve an even wear of the rollers, the Oscillation frequency is not important and is especially not available

209846/0878

. in relation to the target delivery rate. The frequency of oscillation is preferably relatively low compared to the speed of the main feed roller. For example, the cam disk Rotate 12o once every 5 or 10 or more or less revolutions of the main feed roller. The control track has preferably in the area of its lower point 123 and its upper point 124 a flat, straight course, such as shown in fig. This takes into account the time delay caused by the reverse movement of the strand. is gentle. The use case described above given dimensions are only examples, other dimensions are also possible.

The conveying device is preferably provided, as mentioned, in order to form strands into a multi-threaded, round chair Conveying knitting machine. The knitting machine can be a jersey machine, a rib machine, a Interlock machine or any other machine type be with one or more needle banks. Take, for example, a jersey cylinder knitting machine with a diameter of 75 cm, then such a machine has a circumference of pi χ 75 cm. 75 x pi is about 25o cm. In such a machine Every knitting system uses a yarn length for every revolution of the machine, regardless of the caliber of the needles from about 1 1/2 to 4 1/2 times the circumference of the machine, so that, for example, it can be expected that every knitting unit of the machine, for example. 500 cm of yarn used or knitted per turn.

When the conveyor device according to the invention is to measure and convey the yarn to such a machine as it is was described, the feed rollers would also have about

209846/0878

To convey strands of 5oo cm length each time the knitting machine rotates. If the machine is equipped with a At a speed of 20 per minute, each strand has to pass through the feed rollers at a rate of about 10,000 cm (loo m per minute). To find the exact relationship between the consumption of the machine and the delivery rate of the To be able to adhere to feed rollers, the means for driving the feed rollers, in particular the drive 44 by the The main drive motor of the knitting machine can be actuated, the drive 44 then being a gear for different speeds is. This transmission can be connected to the main drive by any means such as belts, Chains or gears (not shown). When the drive 44 is operated by the main drive of the machine, the Feeding device driven in a certain temporal relationship to the main drive, the gearbox being regulated the speed of the feeder possible power.

In the example given, in which this knitting mechanism consumes about 500 cm of yarn per revolution of the machine, the main drive of the machine is switched on and the gear is then regulated until the feed device delivers the yarn at the correct rate. At this moment the feed rollers deliver the yarn at the target feed rate. When the main drive speed is increased by '^; to achieve a higher engine speed, and the Ge - '' * ^'0 drives accelerated in proportion and still, therefore provides the strands with the target production rate since this rate is based on the speed of the main drive. In other words, if the gear is set so that the feed rollers deliver 500 cm strand length per revolution of the knitting machine,

9846/0878

then it delivers these 500 cm per revolution independently whether the knitting machine is speeding up or slowing down. When the knitting machine is turned off, so will the Feed stopped.

Of course, the drive 44 does not have to go through the main drive be operated. It can also be operated by an independent power source, of course with the knitting machine or any other machine processing the strands should run synchronously. In the illustrated Embodiment are the feed rollers and the Tension regulating cylinder 24 driven by the same drive. If necessary (not shown) the voltage regulating cylinder and the feed rollers are also operated by independent drives, only note that the tension control cylinder runs at a higher feed rate than the feed rollers. This is achieved by the intermediate gear is omitted and instead the cylinder 24 is driven by a motor, which is driven by the pulley 4o Engine is different. However, it is highly desirable that they be operated by the same drive be, so that the entire device can be designed from the outset so that the delivery rate of the cylinder 24 with security is greater than the feed rate of the feed rollers.

The device, as it has been described so far, has several control options. A number of other desirable ones Variations are possible (not shown). For example, the vibration of the carrier 9o can be omitted when the wear of the feed rollers is not a problem. The non-promoting area can also be omitted if each of the Guided tours for themselves in a non-transporting section

209846/0878

can be moved. If an individual postponement of the Guides from a transporting to a non-transporting one Position is not desired, the regulation area can omitted. Virtually all of these movements and controls can be removed by removing the Recesses and thus the non-transporting sections of the feed rollers are omitted.

Occasionally a knitting machine has individual units that use the yarn at different rates of delivery. In in such a case, additional arrangements of feed rollers and guides (not shown) may be provided preferably sits above the illustrated arrangement of the feed rollers and guides. Also such an additional arrangement of feed rollers can be driven by the same main machine drive, but with independent speed control so that the two arrangements promote at different delivery rates. Even in such a case can pull the strands through a single tension regulating cylinder be performed, or there can be several voltage regulating 'cylinders be provided (not shown).

In the illustrated embodiment, the strands are guided from the cylinder 24 to the guide eyes 16o and then to the guide fingers 132. Of course, the eyelets 16o and the guide fingers 132 are also omitted if the oscillating movement and the regulation are omitted (not shown). This can be achieved by the relative arrangement of the cylinder 24 and the main feed roller 34. Indeed, when the cylinder 24 and the feed roller 34 are arranged as shown in FIG. 4, the guide eyes 16o and guide fingers 132 can be omitted. The positioning

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- 57 -

.the cylinder and Bolle themselves already provide guidance means which direct the strands from the cylinder to the conveyors. -

When the device according to the invention conveys strands to the knitting machine and some or all of the guide fingers 132 to a non-transporting section of the feed rolls while the knitting machine is running can do so G-arn nevertheless continued to the knitting machine and processed there will. However, the yarn that runs through the non-transporting sections is not fed positively and measured. If, on the other hand, the yarn is over the transport sections the feed roller is directed, then it is fed and measured with a dimension which is suitable for the various Strands of yarn and also over the length of each strand of yarn, since these are essentially the same Voltage can be measured.

Even if preferably the voltage regulating devices as well as the positive conveying devices of the machine according to the invention are used together, each of these can also be used independently of the other. If only the positive promotion of the yarn is desired, then only the conveyor devices need to be used, with the origin these strands can be arbitrary. If, on the other hand, it is only desired to reduce the tension in the strands and to be adjusted without a positive feed being carried out at the same time, only one voltage regulating cylinder, means for guiding the strands from a delivery to and at least partially around the cylinder and means for guiding the strands needed from the cylinder to the knitting machine. When these elements of the invention are used separately, so

7 0 f J 8 / »3/0 8 7 8

they can still be driven by the main drive of the knitting machine or by any other means.

If the knitting machine produces the knitted fabric with the correct setting, then all strands are fed positively and measured on the knitting machine. Only during the setting periods when either the knitting machine or the feeder is adjusted, one or more strands are transferred to the non-transporting sections of the Feed rollers. Although the knitting machine continues to work, During this time, not all knitting systems receive their respective strands positively fed and measured, and during such At times it can happen that the knitted fabric does not achieve the desired quality.

It should be further emphasized that the strands are essentially relaxed or in a minimal state of tension when they exit the feed rollers. It is generally desirable that the strands be under low tension when they are knitted by the needles. Therefore, the needles generally pull their strands at a rate that is slightly, for example, a few percent greater than the nominal feed rate at which the strands are delivered by the feed roller. In other words, if the feed rollers deliver the strand at about 500 cm per revolution of the machine, the strand being essentially relaxed, then pull or knit the corresponding needles at a feed rate which should be around 505 cm per revolution of the machine, like this that a slight tension is applied to the strand to be knitted. In the case of the knitted fabric produced in the process, however, this strand has been processed in the relaxed state at a conveying rate of ^r > oo cm per machine revolution, I) a; j should be taken into account when aneehf <. ■■■ Ud, lau Λ ie stri ok ma iohine die

Mi ·]?! /, κ ■ ü:; 7 Π
ORiOiNAL

Strands processed with a target delivery rate,

- patent claims -

209 846/0878

Claims (1)

Claims 1. Device for feeding several strands of yarn with essentially Same tension and delivery rate from a storage device to a knitting machine or the like., characterized by tension control devices for Reduction and at the same time approximate equalization of the voltage of a plurality of those obtained from the storage device Strands, guide devices and conveyor devices for the positive promotion of these strands with a target delivery rate, this guide means the strands of the tension control device forwards to the conveyor, and wherein the conveyor essentially conducts the strands with the same tension with which it received it from the guide devices. 2. Apparatus according to claim 1, characterized in that the tension regulating device includes a tension regulating cylinder (24), means for one around its Axis rotatable mounting of the cylinder, means for driving this cylinder about its axis at a delivery rate that is greater than the target delivery rate and means for feeding the strands from the storage device to and at least to a portion around the surface of this cylinder so that the tension in the strands frictionally engages them and the surface of the cylinder and a supply of these strands from the storage device to the guide devices causes an increase in tension in each strand to increase and decrease the feed rate of each strand the tension of each strand a decrease in the delivery rate of this 209846/0878 Strand results in and wherein the tension in all strands is substantially equalized to one another. 3. Device according to one of claims 1 or 2, characterized in that the feed device is a main feed roll (34) extending in the transverse direction; and at least one auxiliary feed roller resting against this (7o> 72) comprises means for supporting these rollers rotatably about their axes, means for driving each of these rollers their axes at a target feed rate, at least part of the surface of the main feed roller with at least one Part of the abutting surface of the auxiliary feed roller engaged stands, so that by the rotation of these rollers the abutting surfaces a positive promotion of has intervening strands result, wherein the strands through the guide device of the tension control device is directed to the feed rollers. 4. Device according to one of claims 1 to 3, characterized in that the guide device a plurality of transversely spaced strand guides (132) which extend the strands to the in Guide engaging surfaces of the opposing feed rollers. 5. Apparatus according to claim 4, characterized that a device is provided by means of a relative oscillatory movement in the transverse direction between the strand guides (132) and the feed rollers (34, 70, 74) is effected. 6. Device according to one of claims 1 to 5, characterized in that that the surfaces of the feed rollers several one 209846/0878 Having spaced sections in the axial direction, which are in engagement with each other and strand Form fb'rdersätze (I5o), and that the conveyor rollers furthermore are provided with other, spaced apart sections in the axial direction, which are not with one another are engaged and which form non-transporting sections (148), the transport sections and alternate the non-transporting sections with one another in the axial sighting of the feed rollers, and means are provided are to guide the strands alternatively to transport sections or non-transporting sections. 7. Device according to one of claims 1 to 6, characterized in that the non-transporting Sections are formed by at least either the main feed roller (34) or one of the auxiliary feed rollers (7o, 74) are arranged circumferential recesses (148) separated from one another in the axial direction. 8. Device according to one of claims 1 to 7, characterized in that the circumferential recesses (148) are arranged in the main feed roller (54). 9. Device according to one of claims 1 to 8, characterized in that that the main feed roller (34) alternately with circumferential recesses separated from one another in the axial direction (148) and circumferential elevations (I5o) is provided, the elevations with the surface of each auxiliary feed roller are in engagement and in this way form the transport sections, and wherein the recesses with no surface the auxiliary feed rollers are engaged and on this Way to represent the non-transporting sections. 209846/0 8 78 10. Device according to one of claims 1 to 9 »thereby characterized in that means are provided to make each strand independent and optional either to a transport section or not to one the transporting section. 11. Device according to one of claims 1 to Io, characterized characterized in that means are provided to selectively all the strands at the same time.Either to the not transporting sections or the transport sections. 12. Device according to one of claims 1 to 11, characterized marked i without t that a transversely arranged, the strand guides supporting component is provided is, wherein the guide device is a plurality of spaced apart in the transverse direction guide fingers (132) includes, which are arranged on this component, and these guide fingers can optionally be adjusted so that they go to the transport sections or the non-transporting ones Sections are aligned and the strands lead there. 13. The apparatus according to claim 12, characterized in that each guide finger (132) is independent of the other is movably arranged on this component carrying the guide, with it opposite between adjustable in two transverse positions are and wherein in one of these positions the guide to a transport section, in the other position to a is aligned with the non-transporting section. 20984 6/08 7 8 14. Device according to one of claims 12 or 13, d a d u r c h characterized in that a support device is provided is on which the component carrying the guides is mounted so that it is in one area in the transverse direction can move, which contains a conveying area, further characterized by a device which an oscillating movement transfers this component in the transverse direction over at least part of this conveying area, each strand guide during this oscillation movement to a transport section can be aligned. 15 · Device according to one of claims 12 to 1 #, characterized characterized in that the bearing supports the guides Component can be moved between a conveying position and a non-conveying position, wherein in the conveying position each of the strand guides to a transport section and is disengaged in the non-conveying position to a non-transporting section, as well as characterized by facilities for the optional positioning of this component in a conveying or in a non-conveying position. 16. Device according to one of claims 12 bisl5t know «denies that all guided tours to the transport sections or to the non-transporting sections at the same time Sections are signable. 17. Device according to one of claims 12 to 16, characterized characterized in that the component carrying the guides in its transverse oscillation through a zone of this The conveyor area is moved, and being independent of each other movable guide fingers aligned in their first guide position to a transport section of the feed rollers while the component is in the conveying area 209846/0878 located and with the guide fingers in their second Guide position to a non-transporting section of the Bollen are aligned while the component is at least part of a section is located in this conveying area, as well as further characterized by facilities to regulate the component carrying the guides in the transverse direction within the displacement path by certain, selectable amounts, whereby the strand guides lead to a non conveying section of the feed rollers are aligned when said component is in a non-conveying Area is located. 18, device according to claim 17 »because d u r c h characterized that the zone of the feed area the subsection does not include the regulating device optionally the component carrying the guides either in the conveying zone, the said subsection or the non-conveying one Range adjusts and that means are provided to the strand guides automatically in their first guide position to hold when the component carrying the guides executes its oscillatory movement in the said conveying zone. 19. Device according to one of claims 1 to 18, characterized characterized in that the guide device comprises a transversely extending solid support (88), which extends substantially parallel to the axis of the main feed roller (34) so that it further extends into a Transversely extending movable support (9o), 'which transversely to the fixed support and on this in the transverse direction is movably mounted that the movement space of the carrier comprises a conveying area, which is a non-conveying Area follows, the production area including a normal zone as well as a regulating area that the normal zone 2038A6 / 0878 a beginning as well as one between this beginning and that not conveying area has the end that the regulation area is in the vicinity of this and not to the beginning that a plurality of extends in the transverse direction spaced apart strand guides (152) is provided, which on the movable Carriers are pivotably mounted so that each of the strand guides independently of the other between two lateral Guide positions are adjustable, the first of which is aligned with a transport section of the feed rollers when the movable carrier is located in its conveying area and its second guide position to a non-transporting one Section of the feed rollers is aligned when the movable carrier is in said regulation range, further characterized by resilient means which constantly pushes the movable carrier in the direction of the beginning of its range of motion, a cam disc which the movable The carrier moves cyclically from its initial position against the action of the spring means into its end position, whereupon the Spring means moves the carrier back in the direction of its initial position, the normal position of the movable The carrier is within said normal zone in which it can move freely between the initial position and the final position can, further characterized by regulating devices, by means of which the movable carrier can be released either in a regulating area or in its non-conveying area can be locked or released for its vibratory movement in the normal zone, each Strand guide with a transport section of the feed rollers is aligned when the movable carrier is in its non-transporting area. 209846/08 7-8 2o. Device according to one of Claims 1 to 19 because it is indicated that the solid support (88) laterally under the movable carrier (9o) that each of the strand guides extends as an elongated strand guide finger (132) which is fastened in the movable carrier by means of a protruding through the guide finger Pin (134) is pivotally mounted on the support that each guide finger has an upper arm above the pin and a lower arm, the upper arm having a strand guide opening and the lower arm extending laterally extending beyond the movable carrier and overlapping the fixed carrier that the fixed carrier has a plurality of stop pins (138) projecting into the plane of the lower arm, the stop pins so arranged are that the lower arms of the guide fingers rest against these stop pins in their first guide position, when at the same time the mobile support is in its initial position of its normal zone, and the Guide fingers also rest against their assigned stops, when they take their second leadership position and the movable carrier at the same time a different from its initial position, but not over the regulation range also assumes shifted position, so that a movement of the movable carrier from the regulating area in the direction on its starting position all guide fingers that are not are in their first guide position, by means of the stop pins pivoted into this first guide position and in this way holds the guide fingers in this first guide position during the oscillating movement of the movable carrier. 09 846/0878 21. Device according to one of claims 1 to 2o, in connection with a multi-thread knitting machine with several knitting units, characterized 'in that means are provided, the strands of the'Fördereinrichtung to the To guide knitting mills, the knitting mills processing the strands at the predetermined target feed rate. 22. Device according to one of claims 1 to 21, characterized characterized in that a main machine drive and means for driving the voltage regulating cylinder (24) are provided, which at the same time also drive the feed rollers, these drive means with a common one Main drive are connected. 23. Device according to one of claims 1 to 22, characterized characterized in that the tension control cylinder (24) has a higher feed rate than the feed rate with which the knitting mills process the delivered strands. 24. The device according to claim 23, characterized., that the drive of the tension control cylinder * (24) takes place through the main drive (44) of the knitting machine. 25. Device according to one of claims 1 to 24, characterized characterized in that all the strands are conveyed through the feed rollers (34, 70, 74) at the desired conveying rate be, with a first guide device for optional Guiding the strands from the storage device to the transporting ones or non-transporting sections of the feed rollers, as well as a second guide device for Transferring the strands from the feed rollers to the knitting units are provided. 209846/0878 26. A method of feeding a plurality of strands at substantially the same tension and feed rate to a knitting machine or the like, comprising the following procedural steps i the tension in the strands coming from the storage device is initially reduced and, at the same time, essentially matched to each other; then these strands are fed with a predetermined target delivery rate promoted, the tension of the strands being kept substantially the same. 27. The method according to claim 26, characterized that the tension in the strands is thereby reduced and essentially adjusted to one another, that this from the storage device to a cylinder and are at least partially guided around its surface, the cylinder rotating at a delivery rate that is greater than the target delivery rate, so that the tension in the strands is an accessory between the strands and the Cylinder surface causes and the strands are advanced, with an increase in tension in each strand the conveying rate of this strand increases, but a reduction in the tension in each strand increases the conveying rate of this strand String decreased so that the tension in all strands is essentially the same. 28. The method according to any one of claims 26 or 27, characterized characterized in that the strands are positively further conveyed in that they are between adjacent Feed rollers are passed through, which rotate around their axes at the target conveying rate. 2Q9846 / G878 - 5ο - 29. The method according to any one of claims 26 to 28, characterized in that the strands during the Conveying process between de.n feed rollers an oscillating Perform a back and forth motion. 30. The method according to any one of claims 26 to 29, characterized characterized in that the strands are positively conveyed to the knitting units of a multi-thread knitting machine will. 209846/0878 Blank page