JPH0372544B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a winding device for winding yarn into a cross-winding spool. This winding device is especially suitable for 6000m/
Suitable for winding yarn, especially synthetic yarn, that runs continuously at a speed of min.

The winding device known from German Patent No. 1560469 = British Patent No. 1168893 has two
It has two eccentrically supported rotors on which are supported traversing arms equiangularly distributed over the circumference. The rotors rotate in opposite rotational directions. The traversing arm guides the yarn via a curved guide bar which serves as a support for the yarn, and due to the formation of the guide bar the traverse speed of the yarn is kept constant during the traverse section. The thread is then guided through a guide roller around which the thread is partially wound. A traversing arm moves on a guide roller.

The object of the invention is to design such a winding device in such a way that it is suitable for winding a large number of threads. In particular, a number of threads entering from the same direction and in parallel must be wound onto a number of spools that are close together.

This object is achieved by the combination of features defined in claim 1.

As a result, adjacent traverse sections can be placed very close to each other and the spool sleeves can be arranged and fixed on a spool spindle closely together or end-to-end with each other, with each spool sleeve In addition, the necessary space is left for forming a waste winding and a preliminary winding of yarn.
All the entrainment arms (hereinafter referred to as wings) are 2
Due to the distribution in only one plane of rotation, it is achieved that there is the smallest possible distance between the vanes and that the distance between the plane of rotation of the vanes and the transition point of the thread to the guide roller is also very small. Ru. This is a prerequisite for accurately winding the thread onto the spool, with the principles of the winding method ensuring a satisfactory spool formation that optimizes the unwinding of the thread from the spool.

By driving the rotors of adjacent traversing sections whose blades are arranged in the same plane of rotation in opposite directions, the rotation circles of adjacent rotors can be increased to a maximum extent without the blades colliding with or interfering with each other. Overlap.

In addition to the maximum overlap of the rotation circles, the simplification of the traversing device is ensured by the rotor with its blades in one plane of rotation having a different axis distance from the rotor in the other plane of rotation in adjacent traverse sections. A good transmission structure and, in particular, a synchronization of the traverse movement from one section to another is achieved.

The spools arranged behind it by a one-line arrangement of guide rollers are provided insofar as the length of the thread between the guide rollers and the transition point where the thread passes into the spool is at least approximately equal from spool to spool and very short. Can be placed arbitrarily. Under this assumption, the spools can be arranged in a line on just one spool spindle and always have the same thickness. The periphery of the spool is in contact with the guide roller,
Or you can be a little far away. However, the spools may be fixed in individual holders and may have different thicknesses. Further, the spool is arranged in contact with the periphery of the guide roller or at a distance from the guide roller. According to this embodiment of the invention, a large number of traverse sections, 2 to 3 or more, are arranged in line with one another.

A particularly favorable relationship between the length of the traversing section and the spacing between the individual traversing sections is such that each rotor has three blades offset by 120°, and the blades of adjacent traversing sections arranged in the same rotation plane overlap. This is achieved if they mesh with each other in the same direction of movement in the range and in phase positions that are approximately symmetrically offset from each other.

In particular, the blade has a guide edge, called a braking projection, on the side opposite to its traverse edge, the point of intersection of this edge with the guide bar moving in the direction of the center of the traverse section with approximately the traverse speed. It is formed like this. This prevents the thread from moving towards the center of the traversing section faster than the guiding speed of the traversing edge of the blade running towards the center of the traversing section.

It is necessary to remove the yarn from the traversing device at the beginning and end of the winding process. For this purpose, it is proposed to arrange the guide bar on the side of the thread running surface of the rotor on which the transmission is located, and to further design the guide bar in such a way that it can be moved away from the rotor axis until the blades no longer cover the guide bar. Furthermore, this embodiment provides the advantageous possibility of providing thread retention and guide notches outside the traverse section of the guide bar. When the guide bar moves out of the area where it overlaps the blades of the traversing device, the thread slides into this thread guide notch. Advantageously, the thread guide notches are arranged at both ends of the traverse section.

In this embodiment, the guide bar serves as a thread guiding device, for example for guiding the running thread into the catch zone of the spool sleeve and/or into the prewinding zone of the thread.

Furthermore, it is proposed to design the guide bar at least partially as a forced guide. In this forced guide section, the guide bar is provided with inner and outer guide rails. This prevents the thread from leaving the guide rail. This is especially due to the winding principle of the yarn at the end of the traversing section, which accelerates and/or
This is advantageous when traversing must be performed at reduced speed.

The shape of the guide bar realizes a specific movement principle of the yarn, which reduces the traverse speed of the yarn, especially in the center of the traverse section, and wraps about 2% more yarn there than in the end area, which increases the yarn material. An advantageous possibility also arises for the deposition of.

It is also possible to give the two guide rails of the guide bar different profiles and to form the guide edges of the vanes in such a way that the thread is guided along different guide rails during the forward movement than during the return movement.

By arranging the guide bar on the side of the yarn running surface where the rotor transmission device is located, the blades are protected from the operating side of the yarn running path by a protective cover plate that extends beyond the plane of rotation of the blades in the yarn running direction. A possibility arises. This protective cover plate is fixed so as to extend from one end of the traversing section, and each extends parallel to one traversing section. At the other end of this traverse section, the protective cover plate forms a threading slot facing towards the thread running surface.
This design first of all avoids injuries caused by the rotating blades and also ensures that the blades are not damaged during thread handling, for example by the suction pistol that serves to guide the thread when setting the thread.

The threading slit opens into a known thread prewinding device, which captures the thread, introduces it into the area of the traverse section and releases it there, so that the thread is captured by the vanes.

It has already been pointed out that there is a small so-called take-off length between the traversing edge of the vane and the transition point of the thread into the spool. This take-up length can be significantly shortened by arranging a thread guide roller between the plane of rotation of the blade and the spool, through which the traversing edge of the blade passes at a distance from this roller. This thread guide roller has a relatively small diameter, so that the transition point of the thread onto this guide roller lies very closely below the lower plane of rotation. This distance is approximately equal to the radius of the guide roller. In order to reduce the take-up length, the traversing device is preferably inclined in such a way that the plane of rotation of the vanes forms an angle of at least 45° to 70° with the running plane of the thread in the area where the thread runs into the plane of rotation. . The take-up length between the plane of rotation of the vane and the point of transition of the thread onto the guide roller can thereby be made even smaller than the radius of the guide roller.

At the same time, if the rotor transmission is arranged on the opposite side of the plane of rotation from the spool, this also provides space for arranging the drive roller between the plane of rotation of the traverse device and the spool. This drive roller contacts the periphery of the spool and is driven at a constant rotational speed.

From the guide roller, the thread is guided to the spool with almost no take-up length. In order to completely avoid a take-up length between the guide roller and the spool, the guide roller can be brought into contact with the periphery of the spool. In this case, in particular the guide roller can be supported elastically and adapted to the non-circularity of the spool. Furthermore, this elastic support of the guide rollers allows simultaneous use of the drive rollers. In this case, the elastic support of the guide roller prevents the drive roller or the guide roller from moving away from the spool periphery as the spool diameter increases during the winding process. In this case, the drive roller simultaneously serves such that the distance between the spool spindle axis and the traversing device increases with increasing spool diameter. For this purpose, the drive roller and the guide roller as well as the traversing device are always supported on one slider, the guide roller being elastically movable relative to the slider, and the drive of the slider responding to the elastic displacement of the drive roller. controlled by

The traversing device facilitates maintenance, especially the removal of the wound yarn, because the transmission and drive of the rotor is located on the spool spindle side of the plane of rotation, that is, behind the plane of rotation of the vanes in the direction of yarn travel. This avoids the need to disassemble the rotor transmission when the rotor is wound.

In the case of embodiments in which the transmissions of all the rotors are on one side of the plane of rotation, one of the rotors has a rotatably supported hollow shaft. A shaft to which another rotor is fixed is supported eccentrically within this hollow shaft. The hollow shaft and the shaft are driven separately from each other, for example by belts or gears. However, in the traversing device according to the invention, the two rotors are adjusted very precisely relative to each other within one traversing section, so that a precise thread transfer from one blade to the other at the end of the traversing section is possible. Since it is important to guarantee the transition, according to an advantageous embodiment the hollow shaft and the shaft are coupled to each other electrically, in particular by means of an intermediate shaft supported in the hollow shaft, so that the hollow shaft and the shaft both move at the same speed. , but are rotationally coupled to each other with opposite rotational directions and precise phase positions.

This design provides the advantageous possibility of providing a housing as a structural unit for each traversing section, in which the two rotors of this traversing section can be supported. This casing can be installed and dismantled independently of other traverse sections for maintenance and operation. Adjustment of the precise phase position of the rotors relative to each other can be carried out at the manufacturer's factory during assembly. With this design, one shaft, in particular the hollow shaft, is driven from the outside. In this case as well, a belt drive, a gear drive, a worm-worm wheel drive, etc. are used for the drive.

According to a further embodiment, the transmission of a rotor whose blades lie in the upper plane of rotation in the direction of thread travel is located above these blades, and the transmission of a rotor whose blades rotate in the lower plane of rotation lies above this rotation. It is on the lower side of the plane. In this case, the housing is preferably divided, so that the upper housing can be pivoted away from the lower housing. This formation is advantageous for removal of wrapped threads and other maintenance.

An advantageous transmission coupling of the rotors of a number of traversing sections provides that the rotors belonging to one plane of rotation each have a common worm axis, on which the worms belonging to the individual rotors are connected to one traversing section. It is supported by left-hand and right-hand threads alternately from to other sections.

According to another embodiment, the rotors of one plane of rotation are each driven by a tangential belt, which wraps around the belt pulleys of the rotor alternately to the left and to the right and passes in a zigzag pattern between the rotors. run

Finally, the rotor of one rotational plane can be driven by a bevel gear via a common drive shaft extending over all traverse sections. The bevel gear is then supported alternately from one traverse section to another, on the left side of the rotor in one section and on the right side of the rotor in the next section.

According to the drive method, the rotors of the other rotational planes are driven in the same way by one of the drive methods, or from the first rotor via an intermediate gear, so that the rotational speeds of the rotors belonging to one traverse section are equal. , the direction of rotation is opposite and is driven in such a way that the necessary phase position for accurate thread transition at the end of the traverse section is guaranteed.

Next, embodiments of the present invention will be described with reference to the drawings.

The winding machine, whose cross section through the traversing device is shown in FIG. 2, has a spool spindle 1 and a traversing device 2 as important components. The spool spindle is driven in the direction of rotation 4 by a motor (not shown) which is coupled to the spool spindle 1. A number of sleeves 5 are fixed in line on the spool spindle. In each sleeve 5, a cross-wound spool 6 is formed by thread 3 running from the vertical direction, with the same winding time for all sleeves. Generally 3-4 or 6- on one spool spindle
Eight threads run in parallel to each other and are wound up as a corresponding number of spools 6. Each traversing device has two planes of rotation and a number of rotating vanes 7 and 8 arranged in them. In front of this vane is a guide plate 9, along which the thread slides during its traverse. The guide plate is the running surface of the thread (indicated by the chain line)
It can also be on the other side of the .

The plane of rotation and the plane in which the guide plate 9 is arranged are inclined in such a way that the plane of rotation forms an angle .alpha. of 45 DEG to 70 DEG with the direction of thread entry indicated by arrow 10. This achieves the installation of the guide roller 11 below the plane of rotation at a very small distance from this plane. The thread is guided to the respective spool 6 in contact with this guide roller. In this case, the guide roller 11 is in contact with the periphery of the spool 6. However, the guide roller 11 can also be moved slightly away from the surface of the spool and driven to rotate.

The blades 7 of each traversing device rotating in a plane of rotation are supported by a rotor 12 . The shaft 15 of the rotor 12 is rotationally driven by worm wheels 17 and 18. The blades 8 rotating in a plane of rotation are supported by a rotor 13 . The hollow shaft 16 is supported eccentrically by a distance e with respect to the axis 15 of the rotor 12, as shown in FIGS. 1, 3 and 4. The hollow shaft 16 of the rotor 13 is driven by a worm wheel 19 and a worm 20. The rotors of one traverse section are driven with opposite rotational directions, the same speed and constant phase position.

As further shown in FIG. 1, each rotor 12 and 13 has three blades 7 or 8 offset from each other by the same angular distance of 120 DEG. Feather 7 or 8
two rotors 12, 13 cooperating with each other having
therefore forms a traverse section H along the guide plate 9. The traverse section extends over a central angle of approximately 60°.

When a large number of traversing sections are arranged adjacent to each other as shown in FIGS. 1, 3 and 4, the rotation circle of the blade 7 arranged in the rotation plane and the rotation circle of the blade 8 arranged in the rotation plane according to the invention is as small as possible. There is wide overlap and the blades of two adjacent rotors mesh with each other in the overlap area, but have opposite rotational directions.
The blades are therefore arranged and driven in such a way that the blades 7 in the plane of rotation or the blades 8 in the plane of rotation have the same direction of movement in the overlapping range and rotate one after the other with a symmetrical phase difference of 60°. . In the case of the instantaneous positions of the three blades shown in FIG. 1, the symmetrical phase positions of the three blades in adjacent traversing sections are particularly visible.
In the case of the blades of the configuration shown, the rotor and shaft 15 rotate in the counterclockwise direction (arrow 27) in the first traverse section H1. That is, the blades 7 of the rotor 15,1 feed the thread to the left. The rotor 13 and the hollow shaft 16 therefore rotate clockwise (arrow 28) and the vanes 8 feed the thread to the right.

FIG. 1 shows the moment at which the thread transfers from the blade 8 to the blade 7.

Furthermore, according to the invention, a pair of rotors in adjacent traversing sections H2 are eccentric in opposite directions, and the axial distance of the rotors whose blades are in the same rotation plane changes alternately from one traversing section to the next, In two adjacent traverse sections, the distance between the shafts of a rotor in one rotating plane, for example, is not equal to the distance between the shafts of the corresponding rotor in the rotating plane.If the smaller shaft distance is denoted by A, the larger shaft distance is A+2l. It is.

Worm shafts 29 and 30 as shown in FIG.
are driven in the same direction by motor 31 and belt 32. The worm 20 of the worm shaft 30 drives the worm wheel 17 of the shaft 15 of the rotor 12 (plane of rotation). Rack 1 of worm shaft 29
8 drives the worm wheel 19 of the hollow shaft 16 of the rotor 13 (rotation plane). The worms 18 and 20 of one traversing section each have the same screw direction. The thread direction of the worm 18 or 20 is alternately left-handed or right-handed from one traverse section to the next.

The embodiment shown in FIG. 7 in a cross-sectional view and in FIG. 5 in a plan view differs from the previous embodiment in that the rotor drive is located on a different side of the plane of rotation. Approximately identical shaft supports 15, 16 are used for the two rotors 12 and 13. The two axes each have one worm wheel 17, 18
driven by. The two worm wheels are electrically connected to each other by a belt drive 39, in particular a toothed belt. The worm wheel is driven by a drive motor 40. The two casings 34 and 35 are connected to each other by a hinge 36 on the motor shaft. As a result, the housing 34 can be pivoted away from the housing 35. This facilitates the maintenance of the vanes 7 and 8, in particular the removal of any windings that may occur.
The traversing device 2 is movable by means of a guide slide 42 on a guide rod 41 such that the traversing device can be displaced vertically as the diameter of the spool 6 increases.
For this purpose suitable drive and control devices are provided,
Thereby, the pressure force with which the guide roller 11 contacts the spool 6 can be controlled to a predetermined value, and the movement of the traversing device can be controlled (for example, see German Patent No. 2,532,164 and U.S. Pat. No. 4,106,710). .

According to the plan view of FIG. 5, in this embodiment also the shaft 15 has the rotor and the blades arranged in the plane of rotation.
It is clear that the distance between the axes is small in the traverse section H1 to H2 and large in the traverse section H2 to H3. On the contrary, the distance between the shafts 16 through which the blades 8 rotate in the rotation plane is large in the traverse section H1 to H2 and small in the traverse section H2 to H3. Axis 15,1
The eccentric direction of 6 changes alternately from one traverse section to the next traverse section. Adjacent traverse section, for example H1,
The shaft 15 or rotor of H2 rotates in different directions. Since the rotors or blades mesh with each other in the overlapping range, the blade 7 of the traverse section H1 is in the instantaneous position shown.
It is clear from Fig. 5 that there is a phase difference of exactly 60° between blade 7 and blade 7 in traverse section H2.
The same applies to the remaining traversing sections.

FIG. 6 shows a special embodiment of the guide plate 9, which is used in particular when the guide bar is on the side of the thread traversing device, as shown in FIGS. 5 and 7. In this case, the guide bar has thread retention notches 3 outside the traversing range.
Equipped with 3. The guide bar can be moved away from the rotor. The thread is thereby pushed away from the range of rotation of the vane, as indicated by the dashed line. The thread then slides to one or the other end of the traverse range and into one of the thread retention notches 33 arranged on both sides of the traverse range. The thread can be retained there, for example by suction, and a spool change can be carried out.
However, in order to place the yarn in the yarn retention notch at the beginning of the winding process and to guide the yarn onto the sleeve and/or to form a preliminary winding of the yarn, the guide bar 9
can also be moved laterally.

overlapping according to the invention of the rotation circles of adjacent traversing devices;
Due to the arrangement of the rotors with alternating eccentricity and direction of rotation, the traversing sections H are very close to each other and the spacing B is necessary to form a waste winding and a pre-winding of the thread at the end of each spool. It is achieved that the size is as large as . It is pointed out that the spool or spool sleeve need not be fixed to one spool spindle as shown in the embodiments. The present invention provides a method in which a number of spools are rotatably supported in a suitable number of spool holders or other devices, the spools are substantially in line during the winding process, and the traversing devices are closely spaced so that they overlap. can also be applied.

The embodiment of FIGS. 8 and 9 shows a tangential belt drive driving rotors in two planes of rotation. In the description of FIG. 8, reference may be made to the description of FIG. 4, but in this case the worm wheels 17 and 19 of FIG. 4 are replaced by belt pulleys 43 and 44. Others, for example, the first
This is an example in which the transmission is on only one side of the plane of rotation, as in the embodiment of FIG.

FIG. 9 is a plan view of belt pullies 44 and 43. It is also clear from FIG. 9 that the distance between the axes of the rotor and belt pulleys 43, 44 alternately changes from one traversing section to another from a large value to a small value. The belt pulley 43 is driven by a tangential belt 45. In this case, each belt pulley is wrapped by a tangential belt at a certain angle. The tangential belt 45 runs between the belt pulleys 43 in a zigzag manner. The tangential belt 45 is in particular a toothed belt with teeth on both sides.

Similarly, belt pulley 44 is driven by tangential belt 46. 47 designates a common deflection pulley, which is driven by a drive motor, not shown, either directly or via a transmission or a belt drive. Another direction-changing pulley 48 serves to change the direction of the tangential belt 45 after it has passed between the belt pulleys 43 . Another deflection belt pulley 49 serves to deflect the tangential belt 46.

According to the embodiment of FIG. 10, the guide slider 42 of the guide rod 41 is movable relative to the spool 6. The guide slider 42 first supports a traversing device according to the present invention. The slider 42 secondly supports the guide roller 11 supported by a pivot arm 51 having a pivot shaft 52 . The pivot arm is held by a force-applying device, for example a disc spring pack 53 which is held under pressure. The guide roller 11 thereby comes into elastic contact with the spool.

The relative position of the swivel arm 51 with respect to the guide slide 42 can be detected, for example, by a nozzle-impingement plate system 54, the output signal of which is sent to the schematically illustrated drive (cylinder-piston unit 55) of the guide slide 42. .

The cylinder-piston unit 55 is a pressure source 56
Pressure is applied through the throttle 57 by the pressure. The pressure generated behind the throttle depends on the slit width of the nozzle 54.

It must be pointed out that in the case of the other embodiments shown in FIGS. 2, 7 and 10, the guide roller 11 can also be used as a drive roller or as a control roller. If the guide roller is used as a control roller, its rotational speed is continuously measured, the measured value is sent to the shaft drive motor of the winding device, and the circumferential speed of the spool remains constant with increasing spool diameter.

According to the invention, despite the complexity of the transmission structure due to the large number of spool positions, it is possible to traverse the threads of all spool ranges synchronously, that is, with the same synchronous direction of movement in each case, This offers significant advantages due to the mutually identical configuration of the spools and the synchronous system contact during winder start-up. FIG. 11 shows the instantaneous positions of the traversing thread 3 in a number of traversing sections.

FIG. 11 also shows details of the traverse device casing of FIG. 10 and 11 show that each traverse section is covered by a protective cover plate 75 on the front of the device. This protective cover plate 75 covers in particular the plane of rotation and the direction of entry of the yarn. This firstly eliminates the risk of injury from rotating blades. Next, when setting the thread with the thread suction pistol, the pistol enters the range of rotation of the blade, thereby avoiding damage to the blade and deviation of its phase position. The protective cover plate 75 has thread guide slits 7 for guide bars 9 not shown in FIG.
It has 6. Each slot is closed at one end, and a threading hole 77 opening into a guide groove 79 of a prewinding device 78 is formed at the other end. When the yarn is introduced into this pre-winding device, the pre-winding device 78 gradually moves in the direction of arrow 80.
It is moved in the direction of the traverse center shown by . This results in several pre-wounds on the spool sleeve that are outside the normal traverse range. The prewinding device 78 then leaves the thread area in the direction of arrow 81. The threads released thereby move towards the traversing center and are captured by the blades of the respective traversing device.

FIG. 12 shows the blades 7 and 8 with a plane of rotation and rotors 12 and 13. The rotors, shown as axes, are arranged on different sides of the plane of rotation. Each roller is driven by a bevel gear 58,59. For the drive, shafts 60, 61 are used, which extend over a number of traversing sections and are driven in the same direction via a belt 62 by a motor (not shown). Another bevel gear 63, 64 is used to transmit torque from the shafts 60, 61 to the bevel gears 58, 59. From one traverse section to another, the bevel gears 63 alternately mesh with the bevel gears 58 of the respective rotor 12 on the left and right sides. The same applies to the meshing between the bevel gear 64 or the shaft 61 and the bevel gear 59 of the rotor 13.

The structural unit according to FIG. 13 has a housing pot 65 which is circular or round in plan view, the main axis of which lies between the hollow shaft 16 and the eccentricity of the shaft 15. The shaft 15 of the blade 8 is rotatably supported in the casing pot 65. The hollow shaft 16 of the blade 7 is supported in a housing lid 67 belonging to a similar structural unit. The lid 67 and the housing pot 65 are fixedly screwed together during assembly. The hollow shaft is provided with an inner toothed wheel 68 which has teeth 72 on the outside for eclipse or gear meshing for meshing with the toothed belt. The toothed wheel 68 is a drive belt 73 in the illustrated case.
, so that the casing pot 6
5 is provided with suitable holes. The rotary movement of the hollow shaft 16 with its toothed ring 68 is transmitted to the shaft 15 via a gear 69, an intermediate shaft 66 also rotatably supported in the casing pot 65, and gears 70 and 71, the shaft 15 being in the opposite direction of rotation. rotate at the same speed. By adjusting the meshing of the gears during assembly, this structural unit is preadjusted in such a way that the phase position of the vanes 7 and 8 is ensured in the reversal position of the traverse to ensure a precise thread transition. This structural unit can be integrated in this manner into the device frame 74, ie into the traversing device housing. It is then only necessary to adjust the phase position according to the invention of the rotor of the adjacent traversing device by adjusting the meshing of the teeth of the tooth flanks 72.

FIGS. 14 and 15 show an embodiment which broadly corresponds to FIG. 10. FIG. However, this embodiment has a drive roller 50. This drive roller 50 is movably supported by the guide slider 42. Therefore, the 15th
In the figure, a support 81 is guided in a linear guide and is supported against the guide slide 42 by a plate spring pack 82. A nozzle 54 of a nozzle-impingement plate system is fixed to the slider 42 . This nozzle 54 detects the relative movement of the support body 81 with respect to the guide slider 42. Thereby, the pressure in the support system (cylinder-piston unit 55) decreases when the spool diameter increases, reducing the distance between the nozzle and the impingement plate, thus increasing the pressure in the system and causing the guide slider 42 to move again. The pressure is controlled to rise to equilibrium.

In the embodiment of FIG. 14, guide roller 11 and drive roller 50 are supported on a common pivot frame 83. In the embodiment shown in FIG. The pivot frame is pivotable about a pivot axis 84. The pivot shaft 84 is mounted on a support 85 which is movable in a guide relative to the slider and supported against the disc spring pack 82. The relative movement of the support 85 is similar to that of the nozzle.
It is detected by the impingement plate system 54 and transmitted to the cylinder-piston unit 55.

Figures 16 and 17 show a rotor suitable for producing spools with a spool length of up to 100 mm, for example 85 mm. In order to accommodate the transmission in this case, it has proven advantageous to use a rotor with four blades 7 or 8 in each plane of rotation. The 16th
As shown, the vanes 7 and 8 are bent at right angles so that only their ends rotate in or within the plane of rotation, respectively. Although the rotating planes or rotors in FIG. 16 are slightly separated from each other in the drawing, this is only for illustration purposes. In reality all vanes 7 lie in one plane and all vanes 8 in a plane.

Furthermore, the blade has a length such that its rotation circle covers the axis of rotation, at least when the distance between the axes of adjacent rotors is small. The blade may be longer than the sum of the traverse section H and the interval B between the traverse sections. To make this length possible, the vanes 7 or 8 of one rotating plane mesh with each other in a gear-like manner as explained in FIG. The blades 7 then pass through the bend 68 of the adjacent rotor. Similarly, the blades 8 pass through the bends 87 of adjacent rotors within the overlap of the rotation circles.

Furthermore, in this exemplary embodiment, it is very important that the transmission (not shown) of the rotor, which is only indicated by shafts 15 or 16, is divided into individual rotational planes or planes. The transmission members are each opposite the other plane of rotation of the rotor. In this respect, this transmission structure corresponds, for example, to the embodiments of FIGS. 7 or 12.

The transmission device and the transmission member are dimensioned to be sufficiently thick by the means described in FIGS. 16 and 17;
It is possible to arrange them in an orderly manner and at the same time achieve small traverse lengths with very small spacings. With such a traversing device, for example, eight threads can be simultaneously wound onto eight spools, each 84 mm long, on a 900 mm long spool spindle.

[Brief explanation of drawings]

Fig. 1 is a plan view of the traverse device, Fig. 2 is a longitudinal sectional view of the winding device, Fig. 3 is a plan view of the transmission device of the traverse device, and Fig. 4 is a cross section passing through the rotor axis of the traverse device. figure,
Fig. 5 is a plan view of the second embodiment of the traversing device, Fig. 6 is a plan view of the yarn guide plate, Fig. 7 is a longitudinal cross-sectional view of the second embodiment of the winding device, and Fig. 8 is the belt drive device. 9 is a plan view of a belt drive device, FIG. 10 is a vertical sectional view of an embodiment having a drive roller, FIG. 11 is a view taken along the arrow in FIG. 10, and FIG. 12 is a schematic sectional view of a bevel gear drive, FIG. 13 is a sectional view of a structural unit accommodating a set of rotors, FIGS. 14 and 15 are longitudinal sectional views of the device with drive rollers, and FIG. 16 17 is a sectional view of another embodiment of the traversing device, and FIG. 17 is a plan view thereof. 1... Spool spindle, 2... Traverse device,
3...Thread, 5...Sleeve, 6...Spool,
7, 8...Blade, 9...Guide bar, 11...Guide roller, 12,13...Rotor, 15...
Shaft, 16... hollow shaft, 17, 19... worm wheel, 18, 20... worm.

Claims (1)

[Claims] 1. (1) A guide roller 11 on which the thread is partially wound in front of the device for fixing the spool sleeve in the running direction of the thread.
(2) Thread the thread in a traversing section H approximately corresponding to the spool length.
A traversing device 2 that traverses back and forth almost at right angles to the running direction of the yarn across (2.1) two eccentrically supported rotors 12, 13 driven to rotate in opposite directions, and (2.2) at least one yarn. It consists of a guide bar 9, each rotor having at least two entraining arms 7, 8, the entraining arms of the two rotors rotating in two closely spaced planes of rotation, through which the thread passes, and a thread guide bar. 9
The thread-carrying edges of the thread-carrying arms 7 and 8 pass along the thread. a device for fixing the spool sleeve; (4) a guide roller disposed in front of each fixing device is arranged coaxially; (5) one traverse for each fixing device or for each traversing section of the cross-wound spool; a traversing device is arranged, (6) the guide bars each extend over one traversing section, the guide bars of a number of traversing sections are arranged in line with each other, and (7) the entraining arms of adjacent traversing sections are (7.1) Same 2
(7.2)
The rotors of two adjacent traverse sections H whose rotation circles overlap each other in at least one rotation plane and (8) the entraining arms 7 or 8 are arranged in the same rotation plane or are (8.1) driven in opposite directions; , (8.2)
With a small interaxial distance in one plane of rotation (for example) and an eccentric distance of 2 in the other plane of rotation
A winding device characterized in that it has a large center-to-axis distance that is twice as large. 2 With at least three traversing sections, the rotors of adjacent traversing sections with the entraining arm in one plane of rotation (for example) alternately from one section to the other with a small interaxial distance and twice the eccentric distance. 2. The device according to claim 1, having a large interaxial distance that is increased by . 3. Each rotor 12, 13 has three driving arms 7 or 8 offset by 120° relative to each other, the driving arms of adjacent traversing sections arranged in or in the same plane meshing with each other almost symmetrically like gears. An apparatus according to claim 1. 4 There is a brake protrusion 2 on the opposite side of the direction of rotation of the entraining arm.
1. The device according to claim 1, wherein the projection brakes the return movement of the yarn to the center of the traverse section after traverse reversal. 5. The device according to claim 1, wherein the guide bar is arranged on the side of the thread on which the rotor transmission is located. 6. The device according to claim 5, in which the guide bar 9 is movable away from the rotor axis. 7. Apparatus according to claim 6, in which each guide bar has a yarn retention notch 33 outside its traverse section and adjacent to this section. 8 A protective cover plate 75 is installed on the thread entry side of each traversing section.
The cover plate extends beyond the plane of rotation in the running direction of the yarn, and covers one part of the traversing section.
6. The device according to claim 5, wherein the device is fixed at one end of the traversing section so that a threading slit 77 is formed at the other end of the traversing section. 9. The device according to claim 8, wherein the threading slit 77 opens into a thread prewinding device 78. 10. Device according to claim 1, in which the planes of rotation of the entraining arms 7, 8 form an angle of 45 to 70° with the incoming thread. 11. The device of claim 1, wherein the rotor transmission is on the opposite side of the spool in the plane of rotation. 12 Claim 11 in which the spool is driven by a drive roller that rotates in contact with the periphery of the spool.
Apparatus described in section. 13. Device according to claim 1, in which the transmission 22 of the rotors 12, 13 is on the spool side of the plane of rotation. 14. The device according to claim 11, wherein the rotor 13 in the plane of rotation on the transmission side is supported on a hollow shaft 16, and the shaft 15 of the other rotor 12 in the plane of rotation is supported eccentrically within this shaft. 15 The hollow shaft 16 is driven from the outside by a gear or a belt, and an intermediate shaft 66 is supported within the hollow shaft, which allows the hollow shaft to rotate at the same rotational speed,
15. The device according to claim 14, wherein the device is transmitted to the shaft 15 with opposite rotational directions. 16 Hollow shaft 16 and shaft 15 and intermediate shaft 6
16. Device according to claim 15, characterized in that 6 are supported in a common casing 65, 67 formed as a structural unit, which casing has a hole in the region of the drive gear of the hollow shaft. 17 Transmission of the rotor 12 with the entraining arm 7 in the upper plane of rotation in the direction of thread running, above this plane of rotation, and transmission of the rotor 13 with the entraining arm 8 in the lower plane of rotation in the direction of thread running. Claim 1 in which the device is below this plane of rotation
Apparatus described in section. 18 One separate casing 3 for the transmission of the rotor group 12 of one plane of rotation and the transmission of the rotor group 13 of the other plane of rotation
4, 35, the casings of which are movable relative to one another, of the transmission of the rotor group 12 in the upper plane of rotation in the thread running direction;
18. Device according to claim 17, in which the casing 35 is connected by a hinge 36 to the other casing 35 and can be pivoted away from another rotation plane. 19 Rotor 1 in one plane of rotation (for example)
2 or 13 are driven by a common worm shaft 23 having a left-handed threaded worm 24 and a right-handed threaded worm 25 alternately through traverse sections H1, H2, H3... equipment. 20 Rotor 1 in one plane of rotation (for example)
2 or 13 are driven by bevel gears via a common drive shaft 60, and the meshing of the bevel gears of adjacent rotors alternately face each other and face oppositely to each other. . 21 The rotor in one plane of rotation (for example) is driven by one tangential belt 45, which drives the drive pulleys of the rotor alternately to the left and from one traverse section to another. 2. The device according to claim 1, wherein the device is partially encircled in a zigzag pattern in the right direction. 22 The rotor on the other rotation plane is the intermediate gear 68, 6
20. Device according to claim 19, driven in opposite rotational directions by rotors in one plane of rotation via rotors 9, 70, 71. 23 The guide bar 9 extends over a part of its traversing section, in particular in the end region of the traversing section, along the inner thread guide rail 37 and the outer thread guide rail 38.
2. The device according to claim 1, wherein the device is configured as a forced guidance device for threads. 24. The device according to claim 1, wherein the peripheral edge of the guide roller 11 is in contact with the generatrix of the spool sleeve 5 or the cross-wound spool 6. 25. The guide plate is curved so that the traverse speed of the yarn is higher than the average traverse speed when entering the traverse reversal range and/or when exiting the traverse reversal range. equipment. 26. The device according to claim 1, wherein the traverse speed of the yarn is 1 to 4% lower than the average speed at the center of the traverse section. 27. The device according to claim 1, wherein the guide roller 11 is supported elastically (spring 53) on the spool. 28 A drive device 55 that measures the elastic displacement of the guide roller with respect to the spool and adjusts the distance between the axes between the nozzle 54, the guide roller 11, and the spool according to the increase in the spool diameter is controlled according to the displacement of the guide roller. Apparatus according to claim 27. 29 The traverse device, the drive roller 50, and the guide roller 11 are arranged on a slider 42 that can move relative to the spool, the drive roller is fixedly supported by the slider, and the guide roller is supported elastically and movably. 13. The device according to claim 12. 30 The drive roller and the spool are movably supported relative to each other so as to increase the distance between the axes,
In addition, the drive roller and the guide roller are movable relative to each other and to the spool, and the relative movement of the drive rollers is measured and the measured value is fed to the drive device 55 for adjusting the center distance. Apparatus according to scope item 12. 31 The guide roller and the drive roller are supported on a common pivotable support device 83 that is movable relative to the spool, and the relative movement of the support device 83 is measured and the interaxial distance between the drive roller and the guide roller and the spool is adjusted. 31. Device according to claim 30, in which the measured values are sent to the drive control device for the purpose of determining the drive control device. 32 The length of the traversing section is less than 110 mm, each rotor has four entraining arms each offset by 90° to each other, the length of the entraining arm is greater than the minimum center distance, in particular the length of the traversing section H and larger than the sum of the spacings B of the traversing sections, the entraining arms are bent in such a way that the ends of the entraining arms rotate in or within the respective rotational plane, and the rotor transmission is operated separately in each case according to the rotational plane. 2. The device according to claim 1, wherein the device is installed on the opposite side of a rotating plane from another rotating plane.