JP6016926B2 - Bobbin winder - Google Patents

Description

  The present invention relates to a bobbin winder having a plurality of winding stations according to the premise of claim 1.

  A typical bobbin winder is known from EP-A-0965554.

  This type of bobbin winder is used in the manufacture of synthetic yarns to wind the yarn onto a bobbin. In this case, depending on the method and the type of yarn, a high yarn traveling speed that can be in the range exceeding 6000 m / min is produced. In the melt spinning method, the yarn is extruded, processed, and guided as a single yarn group within the spinning position, so that the winding of the yarn and the bobbin is performed in parallel with each other. For this purpose, the known bobbin winder has a protruding bobbin winding spindle, on which a plurality of winding stations arranged in a distributed manner are formed. A traversing device is provided so that the yarn can be wound around the bobbin in a cross-winding manner, and this traversing device has a flyer traversing unit for each winding station. This type of flyer traversing unit is particularly suitable so that each yarn can be reciprocated at high speed at the winding station. For this purpose, the flyer traversing unit has two flyer rotors that rotate in opposite directions, and these flyer rotors alternately guide the yarn back and forth. The flyer traverse unit is driven in synchronism, and the torque of the electric motor is transmitted to each flyer traverse unit via a belt drive.

  In each winding station, torque transmission is performed by the toothed belt without slippage in order to produce a uniform bobbin stack when the yarn is being wound. The toothed belt has two profile sides opposite to each other, and a tooth profile having a plurality of protruding belt teeth is formed on these profile sides. The toothed belt is guided in the belt drive by at least one driving wheel and a plurality of drive wheels, and the driving wheel and the drive wheel are engaged with mutually opposite profile sides of the toothed belt. Thereby, the position accuracy when the flyer traverse unit is driven can be determined by only one of the profile sides of the toothed belt, and the profile side is the side cooperating with the drive wheel. In contrast, the starting and braking loads generated by the driving wheel are absorbed by the opposite profile side, which is usually designed to be more wear resistant. However, this alternating meshing in the toothed belt causes vibrations in the toothed belt, which is known as the polygon effect, and the uniformity of the traversing at the winding station. Adversely affect. The polygon effect is further promoted by non-uniform manufacturing tolerances on the profile side.

  The object of the present invention is therefore to provide a general type of bobbin winder that can drive the flyer traversing device with high uniformity at the winding station.

  According to the invention, this object is achieved by the toothed belt being connected to the toothed drive wheel and the toothed driving wheel via the toothed profile side.

  Advantageous developments of the invention are defined by the features and combinations of features of the respective dependent claims.

  Surprisingly, it has been found that the joint engagement of the driving wheel with the drive wheel on one toothed profile side of the toothed belt has no adverse effect on the positioning accuracy for driving the flyer rotor. . With the proper choice of materials, the wear phenomenon caused by the driving wheel on the toothed profile side of the toothed belt is not between the flyer rotors driven by the flyer traversing unit, even if there are multiple drive wheels. It can restrict | limit so that a phase difference may not arise. If all the toothed wheels are in contact with the toothed belt only on one side, the other side of the toothed belt may likewise be provided with a tooth profile or may be flat.

  In order to ensure sufficient winding of the toothed belt on the drive wheel when the driving wheel and the drive wheel arranged adjacent to each other have the same direction of rotation, One is arranged between adjacent drive wheels, and a deflecting roller guides the toothed belt on the flat opposite side. As a result, in each drive wheel, the toothed belt can be driven via a plurality of meshed belt teeth. Therefore, each drive wheel can be driven in the same direction with reliable positioning via the toothed belt.

  Each deflecting roller has a guide casing with one or more continuous guide grooves and guides the toothed belt on the flat side by a guide casing with or without an endless longitudinal web By being able to, the belt guidance between the drive wheel and the driving wheel can be further improved. Thereby, the lateral guide of the toothed belt is generated, and the toothed belt is prevented from moving up and down. In particular, what is achieved is that the belt teeth can roll on the drive wheel under the same geometric conditions.

  In order to accommodate the flyer traversing unit, the flyer traversing unit is preferably arranged on a plate-like carrier movably held on a machine stand together with a drive wheel and a driving wheel. As a result of the mobility of the plate-like carrier, the traversing distance formed between the flyer rotor and the subsequent contact roller can be kept constant by the movable pressure roller even if the bobbin diameter increases. .

  In order to separate the traversing device, preferably a plurality of damping elements are provided between the traversing carrier and the machine stand, so that by driving the bobbin winding spindle and winding the bobbin The generated vibration is not transmitted to the drive system of the traverse device.

  In order to transmit and convert the rotational movement produced by the drive wheel, each flyer traversing device has a power divider, which is connected to the drive wheel and is two rotatable flyer rotors. Is driven in the opposite direction. In this case, adjacent flyer rotors can be driven in the same direction or in the opposite direction.

  When the drive wheel is driven in the same direction, the bobbin winder preferably has a power divider that rotates counterclockwise in the flyer rotor in order to obtain an overlap of rotatable flyer rotors of adjacent flyer traversing units. It is designed to be alternately formed by one of two types of gears that give rise to direction.

  Furthermore, in addition to wear resistance, the generation of noise can be favorably influenced by the development of the invention. In this development, the flat side of the toothed belt supports the damping fabric layer, the basic material of the toothed belt is made of polyurethane and a plurality of steel cords are embedded in the basic material. This type of high performance material has been found to be particularly suitable for reliably driving a plurality of flyer traversing units in a bobbin winder. That is, one belt drive in the bobbin winder can reliably drive 10, 12, or more flyer traversing units of the traversing device.

  Furthermore, remember that rapid traverse changes are required during traversing operations to avoid pattern braking windings that significantly interfere with bobbin stacking during yarn traversing and bobbin winding. I have to keep it. Thus, it has been shown that the spacing between the belt teeth affects the excitation frequency of the toothed belt. In order to avoid overlapping resonance between the traversing frequency and the excitation frequency of the toothed belt, the development of the invention in which the profile side of the toothed belt has a plurality of belt teeth with a spacing in the range of 4 mm to 5 mm. Is particularly advantageous. Surprisingly, it has been found that spacings in the range of 4 mm to 5 mm have a particularly advantageous effect on the drive of the flyer traversing unit and the lamination of the yarns for forming the bobbins.

  Exemplary embodiments of bobbin winders according to the present invention are described in further detail below for further explanation of the present invention. For this purpose, the following drawings are attached to the description.

FIG. 2 schematically shows a front view of an exemplary embodiment of a bobbin winder according to the invention. FIG. 2 schematically shows a plan view of the exemplary embodiment of FIG. FIG. 2 schematically shows a cross-sectional view of an exemplary embodiment of a deflecting roller. FIG. 6 schematically illustrates a cross-sectional view of another exemplary embodiment of a deflecting roller. FIG. 3 schematically shows a partial view of a toothed belt of an exemplary embodiment according to FIGS. 1 and 2. It is a figure which shows schematically sectional drawing of the toothed belt of FIG.

  1 and 2 show various embodiments of a bobbin winder according to the present invention in various views. FIG. 1 schematically shows a front view of an exemplary embodiment, and FIG. 2 schematically shows a plan view. The following description applies to both drawings unless indicated to refer to either drawing.

  The illustrated exemplary embodiment of a bobbin winder according to the invention is conventionally used in a synthetic yarn manufacturing process in a melt spinning apparatus for winding a group of yarns, said group of yarns being It is extruded as a single thread group, drafted, processed, and sent to a bobbin winder. In the bobbin winder, one of a plurality of winding stations is formed for each yarn.

  As can be seen from the illustration in FIG. 2, the exemplary embodiment has a total of four windings to wind the yarn around bobbins 6.1-6.4 at each winding station 5.1-5.4, respectively. It has stations 5.1, 5.2, 5.3 and 5.4. For this purpose, the bobbins 6.1 to 6.4 are held adjacent to each other on the protruding bobbin take-up spindle 2. The bobbin winding spindle 2 is driven so that the yarn is wound on the bobbins 6.1 to 6.4 at a substantially constant winding speed. A traverse device 7 is arranged in front of the bobbin winding spindle 2 to wind the yarn around the bobbin at each winding station 5.1 to 5.4. The traversing device 7 has one flyer traversing unit 8.1-8.4 for each winding station 5.1-5.4. The flyer traverse units 8.1 to 8.4 are driven as a drive group by the electric motor 10. For the transmission of torque, the electric motor 10 is connected via a belt drive 9 to a flyer traversing unit 8.1-8.4. For this purpose, the belt drive 9 has drive wheels 11.1 to 11.4 for each flyer traversing unit 8.1 to 8.4, which are connected via a toothed belt 12. Connected to the driving wheel 14. The driving wheel 14 is directly driven by the electric motor 10, and the driving wheel 14 and the drive wheels 11.1 to 11.4 are rotated in the same direction by the toothed belt 12. The toothed belt 12 has a plurality of belt teeth on one profile side, and these belt teeth are engaged with the teeth of the driving wheel 14 and the teeth of the drive wheels 11.1 to 11.4. .

  In order to drive the flyer traversing units 8.1 to 8.4 with sufficient wrapping in the drive wheels 11.1 to 11.4, each one of the plurality of deflecting rollers is connected to the adjacent drive wheel. Arranged between. That is, the deflecting roller 16.1 is arranged between the drive wheels 11.1 and 11.2, and the deflecting roller 16.2 is arranged between the drive wheels 11.2 and 11.3. The deflecting roller 16.3 is arranged between the drive wheels 11.3 and 11.4. The deflecting rollers 16.1, 16.2 and 16.3 are arranged on the flat side of the toothed belt 12. That is, the toothed belt 12 can be guided by being alternately wound around the drive wheels 11.1 to 11.4 and the deflecting rollers 16.1 to 16.3.

  The return of the toothed belt 9 takes place via two guide wheels 15.1 and 15.2. The guide wheels 15.1 and 15.2 have teeth and cooperate with the profile side of the toothed belt 12.

  As can be seen from the illustrations of FIGS. 1 and 2, each flyer traversing unit 8.1-8.4 has a power divider 13 directly coupled to one of the drive wheels 11.1-11.4. Have. FIG. 1 schematically shows a winding station 5.4 having a flyer traverse unit 8.4. Since each of the flyer units 8.1 to 8.4 and each of the subsequent winding stations 5.1 to 5.4 are configured identically, the winding station 5 having the flyer traverse unit 8.4. .4 will be described by way of example by way of illustration in FIG.

  The first flyer rotor 17.1 with the first flyer set and the second flyer rotor 17.2 with the second flyer set are driven in opposite directions by the power divider 13. The flyers of the flyer rotors 17.1 and 17.2 are assigned to the guide ruler 26, and can reciprocate the yarn along the guide edge of the guide ruler 26 via two flyer sets.

  In order to obtain a compact arrangement of adjacent flyer traversing units 8.1 to 8.4, the flyer set of the flyer rotors 17.1 and 17.2 is connected to the adjacent flyer traversing devices 8.1 and 8.2. Adjacent flyer rotors are designed to mesh with each other. For this purpose, the power divider 13 is preferably formed by two types of gears that cause rotation in opposite directions in the rotor flyer. That is, the power divider 13 can be designed as a left-hand gear or a right-hand gear.

  However, basically, the power divider 13 is such that each of the flyer rotors 17.1 and 17.2 to be driven of the flyer traversing units 8.1 to 8.4 can be driven in the same rotational direction. There is also a possibility that they are designed identically.

  The flyer traverse unit 8.4 is disposed on a plate-like traverse carrier 21, and this traverse carrier 21 extends over the entire traverse device 7, and not only the belt drive 9 but also other flyer traverse carriers 21. The swing unit 8.1-8.3 is also supported. In this exemplary embodiment, the traverse carrier 21 is supported by a swivel arm 19, and the swivel arm 19 is rotatably held on the machine stand 1 via a plurality of damping elements 32. The pressure roller 18 is supported at the free end. The pressing roller 18 is rotatably attached to the swivel arm 19 and is applied to the surface of the bobbins 6.1 to 6.4 during the winding operation.

  The traverse carrier 21 is held adjacent to the pressing roller 18 by the swing arm 19, and thereby the traverse carrier 21 is guided movably together with the swing arm 19 in the machine stand 1. As a result, the traverse distance formed between the guide ruler 26 and the pressing roller 18 is kept constant regardless of the position of the turning arm 19. To some extent, at any position of the pressing roller 18, the flyer traverse units 8.1 to 8.4 can reciprocally guide the yarn with the same drag length.

  As can be seen from the illustration of FIG. 1, the spindle carrier 4 in the machine stand 1 is designed as a bobbin winding turret, and the bobbin winding turret holds the second bobbin winding spindle 3 in a protruding state. Has been. Each bobbin take-up spindle 2 and 3 can be driven independently of each other, and the spindle carrier 4 is likewise assigned to a drive device. In this exemplary embodiment, no drive is shown. The bobbin winding spindle 2 is guided by the movement of the spindle carrier 4 in order to wind the yarn around the bobbins 6.1 to 6.4. After the bobbin winding operation is completed and the bobbins 6.1 to 6.4 are completed, the bobbin winding spindle 2 is guided from the winding region to the replacement region, and the bobbin winding spindle 3 is guided from the replacement region to the winding region. The Thereby, continuous winding of the yarn is possible.

  When the yarn is wound on the bobbins 6.1 to 6.4, the yarn is reciprocally guided at a predetermined traverse frequency by the flyer traversing units 8.1 to 8.4. The traverse frequency of the flyer traversing units 8.1 to 8.4 is determined by the electric motor 10 and transmitted from the driving wheel 14 to the drive wheels 11.1 to 11.4 via the toothed belt 12. In this case, the traversing frequency is typically varied during yarn winding to avoid what is known as pattern braking winding. This change is likewise effected directly via the electric motor 10 and the belt drive 9. As a result, a high dynamic load is generated in the toothed belt 12 with a change in speed. For the stability of the belt drive 9, the toothed belt is preferably guided reliably on the circumferential surface of the deflecting roller 16.

  FIG. 3 schematically shows an exemplary embodiment of the deflecting roller 16.1 in cross-section. The deflecting roller 16.1 has a guide casing 28 rotatably mounted on the shaft 33. The guide casing 28 has a guide groove 29 in the peripheral surface for accommodating the flat side 23 of the toothed belt 12. On the side opposite to the flat side 23, the toothed belt has a profile side 27 with belt teeth 22.

  However, as an alternative, there is also the possibility of placing one or more longitudinal webs on the flat side 23 of the toothed belt 12. A typical embodiment of this type is shown in FIG. FIG. 4 schematically shows the deflecting roller 16.1 in cross-section. In this deflecting roller 16.1, the guide casing 28 has two guide grooves 29 extending in parallel. The guide grooves 29 are designed so that the two longitudinal webs 30 on the flat side 23 of the toothed belt 12 can be guided in these guide grooves 29. As a result, a reliable and quiet running of the toothed belt 12 is achieved, particularly in the region of the drive wheels 11.1 to 11.4.

  The design of the toothed belt 12 of the belt drive 9 can be described in particular by way of example belonging to FIGS.

  FIG. 5 shows a partial view of the toothed belt 12, and FIG. 6 shows a cross-sectional view of the toothed belt 12. The following description applies to both drawings unless indicated to refer to either drawing.

  The toothed belt 12 has a profile side 27 and an opposite flat side 23. A plurality of belt teeth 22 are formed on the profile side 27. The toothed belt 12 is designed as an endless belt. Each of the belt teeth 22 integrally formed on the profile side has a parabolic shape with a completely solid tooth tip. The parabolic shape of the belt teeth 22 is substantially the same as the known high performance profile indicated by RPP. The spacing indicated in FIG. 5 by the reference character T in this case indicates the distance between adjacent belt teeth 22 on the profile side 27. Considering the use and function of the toothed belt 12 in the traverse device 7, the interval T is set to a value in the range of 4 mm to 5 mm. This spacing T advantageously avoids disturbing resonance phenomena that can have a disturbing effect on the winding of the yarn and the changing traversing frequency.

  The configuration of the toothed belt 12 can be basically understood from the illustration in FIG. The toothed belt 12 is formed from a thermoplastic base material, preferably polyurethane. A plurality of steel cords 24 are embedded adjacent to each other in the base material. The flat outer side 23 and the profile outer side 27 are provided with a fabric layer 25, which covers the surface of the toothed belt 12. This type of fabric layer 25 has a particularly advantageous effect on noise phenomena. Furthermore, as a result, the high coefficient of friction of the basic material can be reduced.

  Thermoplastic base materials have been found suitable when used in bobbin winders, particularly with respect to conditions that occur in the surrounding environment. In other words, volatile constituents such as production residues dissociated from the yarn, for example, are not likely to lead to adverse chemical reactions in the toothed belt. Premature wear and friction due to chemical attack by the production residue is advantageously avoided.

  The steel cord 24 shown in FIG. 6 in the base material is an example of a strand material for increasing strength. Other strand materials such as carbon fibers are basically possible.

  The drive wheels 11.1 to 11.4, the driving wheel 14 and the guide wheels 15.1 and 15.2 shown in FIGS. 1 and 2 preferably comprise a circular tooth profile for the belt drive 9. Designed. This type of profile, also known as the high-performance profile, for example the reference letter HDT, has a beneficial effect on the running and tooth flank wear and the rolling of the teeth, as well as the parabolic profile selected in the belt. As a result, the flyer traverse units 8.1 to 8.4 of the traverse device 7 can be reliably driven without causing slippage.

  In particular, the introduction of torque via the driving wheel 14 and the transmission of torque to the drive wheels 11.1 to 11.4 can be advantageously carried out via the profile side 27 of the toothed belt 12. The load generated by the driving wheel 14 during the start, change and braking of the traversing frequency does not have an adverse effect on the positioning accuracy of the phase position of the flyer traversing unit. As a result, high uniformity in winding the yarn at each winding station 5.1 to 5.4 can be achieved.

1 Machine stand 2 Bobbin winding spindle 3 Bobbin winding spindle 4 Spindle carrier 5.1, 5.2, 5.3, 5.4 Winding station 6.1, 6.2, 6.3, 6.4 Bobbin 7 Traverse device 8.1, 8.2, 8.3, 8.4 Flyer traverse unit 9 Belt drive 10 Electric motor 11.1,. . . 11.4 Drive Wheel 12 Toothed Belt 13 Power Divider 14 Driving Wheel 15.1, 15.2 Guide Wheel 16.1, 16.2, 16.3 Deflection Roller 17.1, 17.2 Flyer Rotor 18 Pressing Roller DESCRIPTION OF SYMBOLS 19 Revolving arm 20 Bobbin winding tube 21 Traverse carrier 22 Belt tooth 23 Flat side 24 Steel cord 25 Fabric layer 26 Guide ruler 27 Profile side 28 Guide casing 29 Guide groove 30 Longitudinal web 31 Yarn 32 Damping element 33 Shaft

Claims (9)

A bobbin winder,
A plurality of winding stations (5.1, 5.2, 5.3, 5.4), arranged adjacent to each other along the bobbin winding spindle (2, 3); A plurality of winding stations for winding a plurality of yarns in parallel in (6.1 to 6.4);
A traversing device (7) comprising flyer traversing units (8.1-8.4) for each winding station (5.1-5.4), the flyer traversing unit (8. 1-8.4) are assigned to a plurality of drive wheels (11.1 to 11.4), the drive wheels (11.1 to 11.4) being arranged adjacent to one another, and A traverse device (7) connected to a driven driving wheel (14) for driving the flyer traverse unit (8.1 to 8.4) via a toothed belt (12). A bobbin winder comprising:
Said toothed belt (12) is connected to all toothed drive wheels (11.1 to 11.4) and toothed driving wheel (14) via a single toothed side (27). Bobbin winder, characterized in that During the next Ri fit the drive wheels (11.1 to 11.4), the drive wheel toothed belt deflects the toothed belt (12) (12) (11.1 to 11.4) One of a plurality of deflecting rollers (16.1 to 16.3) for winding is disposed, and the deflecting rollers (16.1 to 16.3) are arranged on the toothed belt (12 The bobbin winder according to claim 1, wherein the guide is guided on the opposite flat side (23).   The deflecting rollers (16.1 to 16.3) each have a guide casing (28) with one or more continuous guide grooves (29), the toothed belt (12) being 3. A bobbin winder according to claim 2, wherein said flat side (23) can be guided by said guide casing (28) with or without an endless longitudinal web (30).   The flyer traverse unit (8.1 to 8.4), the drive wheel (11.1 to 11.4), and the driving wheel (14) were held movably by a machine stand (1). The bobbin winder according to any one of claims 1 to 3, wherein the bobbin winder is disposed on a plate-shaped traverse carrier (21).   The bobbin winder according to claim 4, wherein a plurality of damping elements (32) are arranged between the traverse carrier (21) and the machine stand (1).   Each of the flyer traverse units (8.1 to 8.4) has two flyer rotors (17.1 and 17.2) that can rotate in opposite directions, and the drive wheel (11.1 to 11.4). A bobbin winder according to any one of claims 1 to 5, having a power divider (13) connected to the same.   7. The power divider (13) is selectively formed by one of two types of gears that produce opposite directions of rotation in the flyer rotor (17.1, 17.2). Bobbin winder.   The flat side (23) of the toothed belt (12) comprises a damping fabric layer (25), a base material for the toothed belt (12) made of polyurethane, and a plurality of steels embedded in the base material. The bobbin winder according to any one of claims 1 to 7, comprising a cord (24). The toothed side (27) of the toothed belt (12) has a plurality of belt teeth (22) with a spacing (T) in the range of 4 mm to 5 mm. Bobbin winder according to item.

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