EP3257982A1 - Twisting head rotor - Google Patents

Abstract

The invention relates to a Zwirnkopfrotor 1 for a cabling, which has to equalize the yarn tension of two verzwirnender threads multiple pulleys 2, which are each rotatably mounted on a perpendicular to the rotor axis of the Zwirnkopfrotors 1 Zwirnkopfrotor rotation axis 5 and are guided over the two threads. According to the invention, the at least one deflection roller 2 is mounted at its two ends in the twisting head rotor 1, wherein the two bearings 6 are each surrounded by a housing 7 of the twisting head rotor 1, which is closed by a cover 8 and that upstream of the at least one guide roller 2 Fadenführungsösen. 9 , which guide the inner 22 and the outer thread 17, are arranged so that they feed both threads of the at least one guide roller 2 between the two bearings 6 of the twisting head rotor 1.

Description

The invention relates to a Zwirnkopfrotor for a cabling, which has to equalize the yarn tension of two verzwimender threads several pulleys, which are each rotatably mounted on a right angle to the rotor axis of the Zwirnkopfrotors arranged in the Zwirnkopfrotor axis of rotation and are guided over the two threads.

Cabling is a process of mechanical yarn finishing to produce certain performance properties in the twine. Cabling is a special twisting process in which two threads are twisted together without the individual threads themselves becoming twisted. The advantage of so-called cords produced by cabling lies in their higher tensile strength, since the individual filaments always lie exactly in the loading direction. Preferably, the cabling is mainly used in tire cord production.

During operation of a cabling spindle, a first supply bobbin is arranged on a rotating spindle in a bobbin pot. The bobbin pot and the bobbin itself are, however, secured against rotation. From this first supply spool a so-called inner thread is pulled off axially upwards and guided on its way to the cabling or fusion point with the outer thread through an inner thread brake.

A second feed bobbin, from which the outer thread is pulled off, is arranged in a creel. After the outer thread has passed an outer thread brake and optionally a deflection device, it runs from below axially into the spindle rotor. From the spindle rotor, the outer thread is guided to form a thread balloon to the point of union with the inner thread on which the outer thread is finally wound around the inner thread.

So that both inner and outer threads are cabled with the same thread tension and a uniform twist can occur, both threads pass through a regulator or tension compensation device, also referred to as a cord regulator. Different thread tensions of the individual threads show up in the later thread or cord by different individual thread lengths and lead to a reduction of the maximum tensile strength and the fatigue strength.

With the help of Kordregulators such excess lengths are avoided and fed both threads under the same possible thread tension the point of unification. This applies not only to the number of operation of the cabling spindle, but also during the start and stop phase.

By the DE 197 00 222 C1 discloses a twisting head with rotor for a cabling machine. This Zwimkopfrotor comprises four balancing rollers, of which two are arranged on one side of a plane passing through the rotor axis symmetry plane and the other two rollers symmetrically thereto on the other side of the plane of symmetry. Two with respect to the plane of symmetry opposing rollers are arranged in pairs rotatably on the two ends of a common shaft journal whose axis of rotation is perpendicular to the plane of symmetry and at a radial distance from the axis of rotation of the rotor and which is rotatably mounted at its center by means of a ball bearing on the rotor.

A disadvantage of such a Zwirnkopfrotor that act by the distance between the ball bearings of the rotor axis and due to the high spindle speeds on the ball bearings significant centrifugal forces. Due to the centrifugal force, the grease filling is thrown out of the ball bearings to a residual amount. During further operation, the remainder of the grease is consumed until the ball bearings run dry. Even with ball bearings that are sealed with the latest technology, this degreasing due to centrifugal force can not be prevented. Therefore, the ball bearings reach only a very short life and must be regularly re-lubricated or replaced with great effort.

To solve this problem and to achieve a longer life of these bearings, is in the EP 1 371 761 A2 describes a roller assembly for a Zwirnkopfrotor whose bearings can be relubricated in a simple manner. For this purpose, the pairs of rollers are each mounted in a roller cartridge with a housing and the roller cartridges are replaceable fastened by releasable fasteners on Zwirnkopfrotor. For relubricating the roller cartridges can be easily removed from the Zwirnkopfrotor, relubricated in a Schmieivorrichtung and used again in the appropriate recording on Zwirnkopfrotor.

A disadvantage of this approach is that the cost of relubrication of the bearing is considerable despite the roller cartridge. The removal and installation always brings an undesirable downtime of the cabling with it.

To eliminate this disadvantage and to allow relubrication of the bearings without additional assembly costs, discloses EP 1 895 033 A2 a Zwirnkopfrotor on which one of the two bearing bores is connected to a connection device for supplying a lubricant and the two bearing bores are interconnected by a through hole. The rolling bearings are sealed on their side facing the balancing rollers by rolling bearing own sealing washers. As a result, both bearings can be relubricated in one operation without removing and installing the bearings. Relubrication in the mounted position shortens the maintenance interval required for relubrication and enables more frequent relubrication without reducing overall productivity.

A disadvantage of a Zwirnkopfrotor according to the EP 1 895 033 A2 is that in case of improper relubrication with a too high amount of grease or under excessive pressure, the sealing discs can be pushed out of the rolling bearings and thus can no longer fulfill their sealing function. If the twisting head rotor is put back into operation without adequate sealing, this leads to extremely rapid loss of grease and total failure of the corresponding rolling bearing.

Based on the above-mentioned prior art, the present invention seeks to develop a Zwirnkopfrotor which is designed so that the lubricant loss of the bearing is at least reduced by the centrifugal force occurring.

This object is achieved by the characterizing features of a Zwirnkopfrotors, as described in claim 1.

Advantageous embodiments of the invention are the subject of the dependent claims.

To achieve the object according to claim 1, the at least one deflection roller is mounted at its two ends in Zwirnkopfrotor, wherein the two bearings are each surrounded by a housing of the Zwirnkopfrotors, by a cover is closed and that upstream of the at least one guide roller thread guide eyelets, which guide the inner and the outer thread, are arranged so that they feed both threads of the at least one guide roller between the two bearings of the Zwirnkopfrotors.

The inventive construction of a Zwimkopfes with a two-sided storage of at least one guide roller in the cast body results in that the bearing against a loss of lubricant, which arises due to the centrifugal force occurring, can be sealed. In the context of this invention, the term bearing is used as a synonym for rolling bearings, ball bearings or plain bearings, which are installed in the Zwirnkopfrotor.

In the previous flying storage, in which the bearings were arranged inside and the deflection rollers outside, the lubricant was hurled centrifugal force during operation of the cabling machine to a residual amount from the ball bearings. Due to the now external arrangement of the bearings and the internal arrangement of the pulleys and the design of a housing around the bearings, the lubricant no longer collects as in the known embodiments after exiting the bearings on the machine wall, but remains in the housing. Due to the still occurring centrifugal forces, the lubricant is thrown to the outside, bounces off the inside of the cover and collects in a gap between the ball or slide bearings of the pulleys and the cover respectively a lid that seals the bearing point. If you make this gap as small as possible, the lubricant remains in the vicinity of the bearing.

The loss of lubricant of the pulley bearings in Zwirnkopfrotor can be significantly reduced, if not prevented. Frequent maintenance intervals for relubrication or replacement of the bearings are eliminated or reduced to a minimum. In addition, the life of the bearings of the twisting head rotor increases significantly, since they can now be operated permanently with a sufficient lubrication condition.

Another advantage that has a positive effect on the service life of the bearings is that the bearing load on both sides is more moderate overall than is the case with a flying bearing.

It is conceivable within the scope of the invention that either roller bearings or plain bearings are used. Both types of bearings can be designed so that either the inner ring or the outer ring is rotatably mounted.

Another important advantage of the invention is that a structurally related Ausfädelschutz the individual threads is achieved. Due to the flying support of the deflection rollers, the individual threads could slide in the start and stop phase or in the spindle standstill of the pulleys, so that a new manual threading had to be done before the production process could be continued. In the worst case, a threading out of the individual threads could lead to the formation of a wad, which then had to be removed manually with an even greater expenditure of time.

Due to the Ausfädelschutz not only the manual effort is reduced, but also occurring in the thread errors that are caused by a faulty threading minimized.

As described in claim 2, advantageously corresponds to the cover with a lubricant seal for the respective housing of the twisting head rotor.

Such a configuration can further reduce lubricant loss. The cover, which is necessary to close the housing in which the storage is arranged, corresponds with a lubricant seal and a lid, which seal the bearing itself. The lubricant seal can be formed for example by an O-ring or a rubber disc.

According to claim 3 exactly two pulleys in the twisting head rotor and the two axes of rotation of the pulleys are arranged in a plane formed transversely or parallel to the rotor axis.

An advantage of such a configuration of a twisting head rotor is that both inner and outer threads are guided once with different winding direction over both pulleys, whereby the formation of different Monofilament lengths that result from production-related unequal diameters of the pulleys is reduced.

In this case, lying in a plane axes of rotation of the two pulleys can be arranged differently. A parallel arrangement of the axis of rotation axis to the rotor axis is also conceivable as a transverse or oblique arrangement, wherein the oblique arrangement includes any angle from the parallel arrangement to including a vertical orientation of the axis of rotation of the pulleys to the rotor axis.

In particular, by a vertical orientation of the axis of rotation of the pulleys to the rotor axis, the load acting on the bearings of the two pulleys, distributed more evenly. The symmetrical arrangement of the pulleys in Zwirnkopfrotor also has a positive effect that the Zwirnkopfrotor is easier to balance.

In a preferred embodiment, set forth in claim 4, the yarn guide eyelets are aligned so that they lead the two threads to different deflection rollers, so that the different directions of wrap arise.

Such an orientation and arrangement of the yarn guide eyelets also contributes to the fact that in the twisting rotor according to the invention there is a Ausfädelschutz the monofilaments during the critical phases. This structurally related Ausfädelschutz improves the quality of the twist to be produced, since the possibilities for incorrect threading be reduced, for example after a spindle stop.

The cover of the respective housing can be used according to claim 5 for positioning of the respective bearing with the deflection roller.

Advantageously, the cover defines the working position of the bearing and ensures precise alignment of the guide roller.

It makes sense that the cover is releasably attached to the housing and can also be removed for maintenance purposes of the housing or removed from this. So can be done in a simple and straightforward way, an exchange of pulleys and bearings.

According to claim 6, in each case a common housing is provided in particular for the adjacent bearings of the deflection rollers.

Manufacturing technology is particularly favorable when the two adjacent bearings of the pulleys are arranged in a housing. As a result, only one cover per housing is necessary.

Of course, it is also conceivable within the scope of the invention that each bearing is surrounded by a separate housing, which in each case has a cover. However, the one-piece design of the housing simplifies the manufacturing and assembly process.

The invention will be explained in more detail with reference to the embodiments illustrated in the drawings.

Figur 1

eine schematisierte Ansicht einer Arbeitsstelle einer Kabliermaschine;

Figur 2

schematisch eine vergrößerte Ansicht eines erfindungsgemäßen Kordregulators mit zwei Umlenkrollen;

Figur 3

schematisch eine vergrößerte Ansicht eines alternativen Kordregulators mit einer Umlenkrolle;

Figur 4

schematisch unterschiedliche Anordnungen der Drehachse der Umlenkrollen;

Figur 5

schematisch die beidseitige Lagerung einer Umlenkrolle mit drehendem Innenring;

Figur 6

schematisch die beidseitige Lagerung einer Umlenkrolle mit drehendem Außenring.

It shows:

FIG. 1

a schematic view of a job of a cabling machine;

FIG. 2

schematically an enlarged view of a cord regulator according to the invention with two pulleys;

FIG. 3

schematically an enlarged view of an alternative Kordregulators with a deflection roller;

FIG. 4

schematically different arrangements of the axis of rotation of the pulleys;

FIG. 5

schematically the two-sided storage of a pulley with rotating inner ring;

FIG. 6

schematically the two-sided storage of a pulley with rotating outer ring.

In the FIG. 1 is shown in a schematic view of the structure of a job 14 a cabling. The workstation 14 has a gate 15, which serves to receive at least one second supply spool 16, from which a so-called outer thread 17 is pulled off.

Furthermore, the workstation 14 comprises a cabling spindle 18, which is driven by a spindle drive 19. The spindle drive 19 may be a motor which directly drives the cabling spindle 18 or an indirect drive, for example a belt drive. The Kablierspindel 18 carries on a arranged on the Kablierspindel 18 Zwinnnteller 20, a first feed bobbin 21, from which a so-called inner thread 22 is removed overhead, which is above the Kablierspindel 18 a Zwirnkopfrotor 1 is supplied.

The withdrawn from the second supply spool 16 outer thread 17 is a arranged between the gate 15 and the Kablierspindel 18 arranged in the yarn path, controllable Fadenspannungsbeeinflussungsvorrichtung 23, by means of which the thread tension is varied. For this purpose, the thread tension influencing device 23 is connected to a control device 24, which performs the control of the yarn tension applied by the device 23. The yarn tension influencing device 23 is arranged upstream of the twisting plate 20 in the yarn withdrawal direction. Subsequently, the outer thread 17 passes through the spindle drive 19 in the axis of rotation and exits below the twisting plate 20 from the spindle drive 19. The outer thread 17 is deflected by means of a deflection tangential to the twisting plate 20 and runs to the outer edge of the twisting plate 20. At the edge of the twisting plate 20, the outer thread 17 is deflected upward, so that the outer thread 17 along the Kablierspindel 18 to form a free thread balloon B, the first feed bobbin 21 rotates. The twisting head rotor 1, in which the outer thread 17 drawn from the second supply spool 7 and the inner thread 22 withdrawn from the first supply spool 21 are brought together, determines the height of the free filament balloon B that is being formed. The twisting-head rotor 1 contains the cabling point or point of fusion in which the two threads 22, 17 converge and form the thread 25.

Above the Kablierpunktes a take-off device 26 is arranged, withdrawn by means of which the twine 25 and is supplied via a compensating element 27 of a winding device 28. The winding device 28 has a drive roller 29 and a coil 30 driven by the drive roller 29 in a friction-locked manner.

FIG. 2 shows a Zwirnkopfrotor 1 for a cabling machine, which has two pulleys 2. The Zwirnkopfrotor 1 is provided with four, arranged perpendicular to the rotation axis 3 of the Zwirnkopfrotors 1 bearing bores 4. Each two opposite bearing bores 4 serve to receive a rotation axis 5, which is mounted in the respective bearing bores 4 by means of two ball bearings 6. The axes of rotation 5 are each formed as a deflection roller 2. That is, the guide rollers 2 are each mounted on both sides in a housing 7 of the Zwirnkopfrotors 1 that is closed by a cover 8.

Below the pulleys 2 a guide eye 9 is provided at the lower end of the Zwirnkopfrotors 1 for the inner 22 and outer thread 17. Through this guide eyelets 9 enter inner 22 and outer thread 17 in the twisting head rotor 1 a.

The withdrawn from the arranged in the coil pot first supply spool 21 inner thread 22 passes through the arranged in the central region of the Zwirnkopfrotors 1 guide eye 9 in the Zwirnkopfrotor 1 and wraps around a guide roller 2. From there, the inner thread is down and S-shaped around the other guide roller 2 looped. From this guide roller 2, the inner thread 22 is then fed in the direction of an upper guide eyelet 10 the point of union, at which the two twines to be verzwont individual threads.

The withdrawn from a arranged in the gate 15 second supply spool outer thread 17 rotates as a thread balloon B to the bobbin and passes through the arranged in the edge region of the twisting rotor 1 guide eye 9 in the twisting head rotor 1 a. The outer thread 17 wraps in the same manner as described above with respect to the inner thread 22 S-shaped, but in opposite order than the inner thread 22, the guide rollers 2, to then also fed in the direction of the upper guide eye 10 the point of union.

The twisted individual threads leave as a twist 25 or cord the twisting head rotor 1 and are then wound up.

FIG. 3 shows an alternative embodiment of the Zwirnkopfrotors 1. The only difference from the already described FIG. 2 is that in this example, the Zwirnkopfrotor 1 has only one guide roller 2, which is looped by both the inner thread 22 and outer thread 17. The one guide roller 2 is also mounted on both sides. Since otherwise the functions of both Zwirnkopfrotoren 1 are identical, is omitted at this point to repeat and to the description FIG. 2 directed.

FIG. 4 schematically shows a different arrangement of the guide rollers 2, wherein the axes of rotation 5 of the guide rollers 2 lie on a plane. By the reference numeral 31, a vertical arrangement of the axes of rotation 5 of the guide rollers 2 to the axis of rotation 3 of the twisting head rotor 1 is characterized. Reference numeral 32 shows the formation of an axis of rotation 3 parallel alignment of the axes of rotation 5. A plane arranged at a defined angle to the rotation axis 3 of the axis of rotation 5 is indicated by the reference numeral 33. In this case, the angle can be selected arbitrarily between the vertical or parallel arrangement of the axes of rotation 5 relative to the axis of rotation 3.

FIG. 5 schematically shows the two-sided storage example of a guide roller 2. For rotatably supporting the inner ring of the guide roller 2, a ball bearing 6 is provided at both ends of the rotation axis 5.

During operation, the lubricant due to the rotation of the Zwirnkopfrotors 1 caused centrifugal force is thrown to the outside. The housing 7 of the Zwirnkopfrotors 1 is closed on the outside by a cover 8. The cover 8 defines the working position of the bearing of the ball bearing 6, secures the bearing against the resulting centrifugal force and also supports the sealing of the bearing of the ball bearing. 6

Reference numeral 11 denotes a lubricant seal, in this example an O-ring. Together with a cover 13, the bearing point of the ball bearing 6 is sealed. The gap 12 is located in the lid 13 so that there stored lubricant, for example, at standstill of the twisting head 1 has a viscosity compound to the lubricant in the bearing point and thus re-lubricates the functional points. The lubricant thus remains in the vicinity of the ball bearing 6 and the rolling elements.

FIG. 6 shows an embodiment of a sliding bearing 34 with rotating outer ring. The storage of the deflection roller 2 forms with the axis of rotation 5, a storage unit. As already too FIG. 5 described during operation, the lubricant due to the rotation of the Zwirnkopfrotors 1 caused centrifugal force is thrown to the outside. The built-in between the housing 7 of the Zwimkopfrotörs 1 and the guide roller 2 cover 13 prevents the grease from escaping from the bearing. The lubricant collected on the cover 13 flows back through viscosity connection in process interruption and stationary slide bearing 34 in the bearing and lubricates it so automatically. The built-in lubricant seal 11 seals the lid 13 against direct lubricant leakage. The lubricant seal 11 may alternatively be integrated into the cover 13 by making the lubricant seal 11 of a deformable material such as rubber.

Claims (6)

Twisting head rotor (1) for a cabling machine, which has a plurality of deflection rollers (2) for equalizing the tension of two threads to be twisted, which are each rotatably mounted on a rotation axis (5) arranged at right angles to the rotor axis of the twisting head rotor (1) in the twisting head rotor (1) and over which both threads are led,
characterized,
in that at least one deflection roller (2) is mounted at its two ends in the twisting head rotor (1),
that the two bearings (6) are each surrounded by a housing (7) of the twisting head rotor (1), which is closed by a cover (8) and
in that upstream of the at least one deflection roller (2), thread guide eyes (9) which guide the inner (22) and the outer thread (17) are arranged so that they both threads of the at least one deflection roller (2) between the two bearings ( 6) of the twisting head rotor (1). Twisting head rotor (1) according to claim 1, characterized in that the cover (8) with a lubricant seal (11) for the respective housing (7) of the twisting head rotor (1) corresponds. Twisting head rotor (1) according to claim 1 or 2, characterized
that exactly two deflection rollers (2) are arranged in the twisting head rotor (1) and that both axes of rotation (5) of the deflection rollers (2) are arranged in a plane formed transversely or parallel to the rotor axis. Twisting head rotor (1) according to claim 3, characterized in that the thread guide eyelets (9) are aligned so that they lead the two threads to different deflection rollers (2). Twisting head rotor (1) according to claim 1, characterized in that the Cover (8) of the respective housing (7) for positioning the respective bearing (6) with the deflection roller (2) is usable. Twisting head rotor (1) according to claim 3, characterized in that a common housing (7) is present in each case for the adjacent bearings (6) of the deflection rollers (2).

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