EP0088993B1 - Twisting apparatus for stranding machines, in particular a pretwisting and drawing apparatus - Google Patents

Description

The invention relates to a stranding device for stranding machines, in particular a pre-twist and take-off device as a ballast for single or multiple impact machines, with a rotary drive rotor support frame and a rotary drive take-off disc mounted transversely to the axis of rotation and longitudinal axis of the rotor support frame, in which the cable elements on an entry stranding point in the longitudinal axis is fed to the rotor support frame and the rope on the rotor support frame is guided to the take-off disk and, after being wrapped around it, through the longitudinal axis through the rotor support frame.

Conventional single-lay machines offer the advantage of the highest quality stranding quality, but they are considerably too slow in comparison to the common double-lay machines. The known double impact machines, on the other hand, are substantially superior to the single impact machines only in their production speed. The very popular three-layer or multi-layer strands made of 16 or more bare wires can be manufactured much more gently, evenly and thinner in a single lay, especially with much smaller fluctuations in the outer diameter than in a double lay. The gentle treatment of the material in a single blow avoids excessive stretching, which would lead to hardening of the wires and thus to a decrease in the electrical conductivity. The significantly smaller wire diameter tolerances allow considerably lower sheath thicknesses for insulation with plastic or rubber. Depending on the structure of the strand - due to the number of wires and the wire diameter - the additional effort for insulation material in a double lay compared to a single lay in practically measured cases is over 19.5% to a maximum of 27.8% (see Drahtwelt 7 - 1977, p. 271) .

It has now become known that the quality of a stranding with double striking machines is particularly increased if a pre-twisting device is attached in front of the entrance of the double striking wing, which drives the strand directly at the desired speed of two strikes per one double striking revolution.

If this pre-twisting device is also designed as a trigger element, it also provides the pulling force for overcoming the total resistance of all braking voltages of the single-wire coils. This relieves the strain on the stranded wire, which is then only used for winding in the double lay-up machine.

• a) eine möglichst gleichmäßige und dünne Litze liefern können, um zu beträchtlichen Einsparungen an Isoliermaterial zu kommen,
• b) trotz hochtouriger Doppelschlag-Produktionsgeschwindigkeit so materialschonend vorverlitzen, daß ein übermäßiges Dehnen und Verhärten des Verseilgutes verhindert und somit z. B. ein Abfallen der elektrischen Leitfähigkeit der Starkstromlitze vermieden wird.

A stranding device as a pre-twist and take-off device which is particularly suitable for the production of multilayer high-voltage strands must therefore be used

• a) can supply a strand which is as uniform and thin as possible in order to achieve considerable savings in insulation material,
• b) despite high-speed double-twist production speed, pre-load so gently that excessive stretching and hardening of the stranded material is prevented and thus z. B. a fall in the electrical conductivity of the high voltage strand is avoided.

It is not important here that a strand stranded in a single lay is passed through a double lay machine onto the take-up spool without partial intermediate stranding. The decisive factor is that the entire rope run (as a double single run) is carried out in the single run pre-twister, so that the wire lengths required for the double and finished line run are drawn for all inner to outer wires. The fact that the strands struck alone on double lay machines are generally not so even and so thin is due to the fact that with the double lay machine without a pre-twisting device at the entrance to the machine, the appropriate wire lengths can only be drawn for the first, i.e. still simple, cable run. The initially matching from layer to layer - ie balanced - incoming wire lengths are no longer correct for the subsequent second stroke, because then the inner compared to the outer wire layers have a relatively large excess length. The multi-layer ropes from outer to inner layers, i.e. H. Relative excess length towards the core wire tends to form loops and thus leads to fluctuations or increases in the rope diameter.

The process described has not been able to prevail to this day because the speed of the new double impact machines developed afterwards has been increased by leaps and bounds. So far, no single twist pre-twist and take-off devices have become known which, as required, run twice as fast as today's double twist machines.

In industrial practice, so-called pre-swirl devices are already used to meet only the requirements mentioned under a) (see »Wirhtwelt« 7/1977, page 270, Fig. 7, and page 271, 4th to 6th paragraph of the article »Comparison of processes Single- and double-stroke cutting «by AC Osman). These facilities run quickly. however, they only have simple drag discs without their own deduction. The strand must also be pulled through the pre-twist device from the take-off in the double striking machine. The tensile stress in the strand is not substantially reduced after leaving the swirl device, but rather by the centrifugal force additionally generated in the device and not compensated by it even increased considerably. A driven take-off disk, which is wrapped several times by the stranded wire, is indispensable for gentle pre-stranding in high-speed operation. According to the well-known Euler looping law, the rope tension on the take-off disk is reduced very quickly, so that the tension force in the running rope run after the take-off disk is considerably smaller than in the running rope run.

The drive of a take-off disk, which is mounted with its axis of rotation transversely to the impact rotor axis in favor of a material-friendly rope guide, now becomes a problem that has not yet been solved at higher impact speeds.

The known pre-twist and take-off devices of the type specified at the outset (e.g. AT-A-286 833) are unsuitable for high-speed double-stroke product speeds because the usual drive of the take-off disk takes place via a toothed belt drive which is mounted completely eccentrically to the machine axis of rotation. The complete toothed belt transmission is arranged outside the impact rotor designed as a frame support. For a common design size with a trigger disk diameter of, for example, 180 mm, corresponding frame support dimensions and an impact rotor speed of 4000 or more revolutions per minute, such a construction would lead to an unbearable centrifugal load on the rotor support frame. In addition, this would result in a completely indisputable short service life for the roller bearings involved.

Another major difficulty now arises for fast operation: a trigger disk, which is driven not only about its axis of rotation but also about the axis of rotation of the rotor support frame, is a guided gyroscope that is forced to rotate by its guide frame (rotor support frame). The forced precession produces a strong gyroscopic effect, the gyroscopic moment, as a result of inertial forces.

The faster the rotation around the gyroscope and the precession axis and the greater the moment of inertia, the more significant are the gyroscopic forces with which the gyroscope opposes the change in direction of its axis of rotation. The greater the load on the rotor support frame when it has to endure these forces itself.

The difficulties described with regard to the effect of the gyroscopic forces and the centrifugal forces are in conflict with the use of stranding devices of the type specified at the outset in order to achieve the desired high rotational speeds and thus impact rates.

The invention has for its object to provide a stranding device of the type specified, which can be used in particular as a pre-twist and take-off device as a ballast for single or multiple impact machines and in particular for double impact machines and in which the desired particularly high rotational speeds and thus impact rates are achieved can reach an intolerable level without the described adverse effects of the gyroscopic and centrifugal forces. The rotor support frame should thus be relieved of the effects of the centrifugal and centrifugal forces as completely as possible, at least as far as possible, even at the highest possible rotational speeds and impact rates. The aim is to achieve the simplest, most compact and, above all, reliable device with a long service life. Above all, the difficulties in the design and storage of the trigger disk should be countered in this regard.

This is achieved according to the invention in particular in that a rotational element driven in the opposite direction of rotation is rotatably mounted coaxially with it on the axis of rotation of the trigger disc and the shape, dimensions, masses and rotational speeds of the trigger disc and of the rotary element as well as those rotating with them Components are chosen such that the respective product of mass moment of inertia and angular velocity of the rotating units is at least approximately the same size, and that the trigger plate and the rotating element are each mounted on the common axis of rotation with the aid of an associated hollow shaft and the hollow shafts additionally against those of the rotor support frame Directional centrifugal forces are rotatably supported on the common axis of rotation and that the product of the total mass of the components associated with the trigger plate and the distance from their common center of gravity from the longitudinal axis of the rotor support frame ns is at least approximately equal to the product of the total mass of the component assigned to the rotating element and the distance from their common center of gravity from the longitudinal axis of the rotor support frame.

Due to the inventive introduction of a counter-rotating element and the mutual dimensioning of the now counter-rotating units, the gyro moment generated by the unit containing the pull-off disk is compensated with the resulting gyroscopic forces by the gyro moment generated with the counter-rotating unit containing the rotating element, so that the described strong and harmful gyroscopic forces do not affect the rotor support frame. Due to the support according to the invention of the extractor disk and the rotating element on the side directed in each case towards the rotor support frame, a closed power flow is achieved within both structural units via the axis of rotation, so that in connection with the dimension according to the invention solution of the respective total masses and their center of gravity distances (sum of all static mass moments equal to zero) and the described disadvantageous strong centrifugal forces no longer have an effect on the rotor support frame. This makes it possible to operate the stranding device at very high speeds, in particular the speeds desired for use as a pre-twist and take-off device, without the difficulties described, which are generated by the gyroscopic and centrifugal forces. This means that the rotor support frame and extractor disc can experience extremely high speeds even in continuous operation. It has been shown that with a stranding device according to the invention, over 4000 rope strikes per minute can be generated in continuous operation, so that the difficulties described at the beginning of stranding and / or rope production can now be overcome with such a stranding device. The rotor support frame is used with regard to the trigger disk only for the spatial fixation of the entire trigger unit, a further load on the impact rotor is no longer or only to a minimal extent due to the compensation of the gyroscopic moments and the closed force flow for the centrifugal forces. The mutually compensating designs, dimensions, masses and rotational speeds of the two opposing units within the fume cupboard system can be selected depending on the application and the shape and design of the rotor support frame as well as the stranding task. The external rotatable support of the hollow shafts is conveniently carried out in a simple manner by combined radial and axial bearings. The design according to the invention results in a simple and very compact overall arrangement, which is also particularly conducive to achieving the desired high rotational speeds.

For the generation of high speeds without an unacceptable load on the rotor support frame, the design of the counter-rotating drives for the trigger disk and the counter-rotating element is of particular importance. A particularly favorable design with corresponding compensation effects is achieved according to one embodiment of the invention in that the trigger plate and the rotating element are each driven in rotation by means of a belt drive with a pulley, in particular toothed belt drive, located on the rotor support frame, and a planetary gear is arranged in this way at the rope exit end of the rotor support frame that the sun gear is rotatable about the longitudinal axis of the rotor support frame with a hollow shaft receiving the rope in the rope exit end of the rotor support frame and the opposing planet wheels, which are designed as pulleys, are mounted on a common axis of rotation which runs parallel to the axis of rotation of the pulling disk and the rotating element, and that the planet wheels are dimensioned with their rotating components in shape, dimension, mass and rotational speeds such that the respective product of the moment of inertia and angular velocity of the counter circumferential units are at least approximately the same size, and are rotatably supported on their common axis of rotation against the centrifugal forces directed towards the rotor support frame, whereby combined radial and axial bearings can in turn be used. The sun gear and planet gears have the intermeshing bevel gear teeth, to which the respective pulley is connected in the case of the planet gears. Due to its arrangement according to the invention, the planetary gear used for the drive already has, in principle, an extraordinarily symmetrical structure, and the opposite drive movement for the pull-off disk and the counter-rotating element is generated without the interposition of further drive elements via the planet gears. The basic structure of the planetary gear in turn leads to a symmetrical arrangement with respect to the rotor support frame. The gyroscopic moments of the planet gears and the components rotating with them are compensated, the centrifugal forces are in turn eliminated in a closed flow of force through the common axis of rotation and become equal due to the corresponding dimensioning of the respective total masses and their center of gravity distances (sum of all static mass moments equal to zero) described using the deduction unit dimensioned large, so that overall the rotor support frame is completely or largely relieved of the effects of centrifugal forces and centrifugal forces with this drive.

A configuration and arrangement which is advantageous for the compact design on the one hand and for the desired compensation effect for the gyroscopic torques and especially for the centrifugal forces on the other hand is achieved in a further embodiment of the invention in that the trigger disk and the counter-rotating element each comprise a disk-shaped fastening flange and a side of it protruding, directed to the other mounting flange circumferential ring body, wherein the circumferential ring body of the trigger disc forms the winding surface (the pull ring) for the rope and the circumferential ring body of the rotating element engages under the circumferential ring body of the trigger disk. The trigger plate and the rotating element thus run largely into one another and can therefore be moved close together, which promotes the compensating effect for the centrifugal forces. The design as a circumferential ring body arranged on the disk-shaped fastening flange enables shapes which are particularly favorable for the compensation effect to be achieved and the masses required in each case are pressed into one another. In particular, the mass of the associated Um forming the main mass of the counter-rotating element Catch ring body largely enclosed by the circumferential ring body of the trigger disk, which is particularly beneficial for the compensation of centrifugal forces. Materials, shape and cross-sectional shapes of the circumferential ring bodies and also of the fastening flanges can be optimally selected for the desired compensation effect on the one hand and for the desired compact design on the other hand. The nesting of the opposing components also shortens the entire extraction device, which in turn leads to a reduction in the centrifugal forces to be compensated.

A design which is expedient with regard to the described compensation effects and desired compact arrangements is achieved in a further embodiment of the invention in that the trigger disk and the rotating element and their associated annular pulley are each fastened to the associated hollow shaft and each hollow shaft is attached to its end face located to the rotor support frame a tie rod is rotatably supported by a combined radial and axial bearing, each tie rod is coaxially inserted, in particular screwed, into a common support axis forming the axis of rotation, and that each tie rod is connected to the facing rotor support frame wall. With both simply designed and easy to assemble components, a closed force flow forming unit of the entire trigger device is created, which is then fixed to the rotor support frame wall with simple connecting means.

In order to achieve a careful rotatable support in the middle in suitable applications, in a further embodiment of the invention the hollow shafts can be supported at their end directed towards the longitudinal axis of the rotor support frame via a radial or a combined radial and axial bearing on a central collar of the support axis.

For the assembly of the structural unit created in this way, the tie rods are expediently fastened in the rotor support frame wall with a screw connection which can be adjusted in the longitudinal direction.

To cope with the rope guide at the achievable high rotational speeds, it is also advantageous if the rope on the rotor support frame is guided over a plurality of rope guide rollers mounted on its inner wall. Furthermore, it is advantageous to achieve the desired high speeds and strokes if the rotor support frame is designed as a rotationally symmetrical, in particular cylindrical, hollow drum body.

For the inventive support of the planet gears and their rotating components in the drive system, as described above, the configuration of the mounting according to the invention, which is described with reference to the mounting of the pull-off disk and the rotating element, can also be used with a corresponding advantage on the common axis of rotation.

Another embodiment of the invention has for its object to further develop and improve the stranding device according to the main patent so that any uncontrolled course of the rope on the take-off disk is avoided with the possible consequence of insufficient take-off or rope tear and instead a correct and clean guidance of the rope the trigger plate is reached. The described compensation of centrifugal and centrifugal forces should continue to be fully guaranteed. Overall, therefore, the achievement of very high speeds and thus stroke rates should be further promoted.

In a further embodiment of the invention, this is achieved in a first step above all by the fact that on a further axis of rotation running transversely to the rotational and longitudinal axis of the rotor support frame, a second extraction disk with an associated rotation element driven in the opposite direction to it is mounted on the rotor support frame and the second Trigger disk and associated rotating element and the associated components are all designed, dimensioned and arranged like the corresponding elements of the first trigger disk with their rotating element, the rope, the trigger disk is guided alternately over both trigger disks and the winding surface of at least one of the trigger disks for rope guidance is provided with circumferential guide grooves . This introduction of a second take-off wheel and corresponding alternate guidance of the rope on the take-off wheels in connection with the circumferential guide grooves on at least one winding surface leads to a more precise control of the course of the rope on the take-off wheels and thus to a correct and clean guidance of the rope on the take-off wheels even at the highest possible speeds, so that an insufficient trigger or even a rope break can be avoided. The described design also leads to a complete compensation of the gyroscopic and centrifugal forces of the second trigger disk and its associated rotating element in the same way as the corresponding elements and structural units of the first trigger disk with this second trigger disk and its rotating element. It is expressly noted here that all design, dimensioning and arrangement rules which are described and identified in the main patent with regard to the first trigger disk and its rotating element are also implemented in the second trigger disk and its rotating element, so that a detailed description is not provided here becomes. Both pulling disks are expediently provided with the circumferential guide grooves for the rope in order to be able to control its guiding in a particularly reliable manner.

In this embodiment, it is also assumed that a planetary gear designed for the rotary drive of the trigger disks Drive system is used as described above, but with the exception of the belt drive described there. Starting from this drive system, a particularly reliable transmission of the drive rotary movements is achieved in that each pull-off disk and each associated rotary element is driven in rotation by an associated gear wheel connected to it by the planet gears of the planetary gear of the drive system provided with an associated gear wheel. In this way, the possible centrifugal loads on the drive belts previously used are completely avoided and a compact and secure drive connection is achieved. Here too, it is expressly noted that, in order to compensate for the centrifugal and centrifugal forces, the planet wheels of the drive system provided with the gear wheels are designed, dimensioned and arranged according to the invention.

If, according to the invention, transmission gears are used according to the invention for the rotary drive of the individual rotating elements, the result is a relatively short arrangement of the drive and the extractor disks with their respective rotating elements. This could lead to only a short cable guide starting from the second take-off disk to the exit point of the rotor support frame. In order to enable a cable guide on the rotor support frame which is as long as possible and provided with the largest possible radii of curvature, in a further embodiment of the invention a transmission gear is switched on between the planet gears of the drive system and their gears as well as the gears of the drive pulley and the associated rotating element , and there are these counter-rotating transmission gears like the planet gears on a common axis of rotation, which runs parallel to the axis of rotation of the planet gears, and there are also the transmission gears like the planet gears with their rotating components in shape, dimension, mass and rotational speeds such that the the respective product of mass moment of inertia and angular velocity of the structural units rotating against one another is at least approximately the same size, and on their common axis of rotation against the F directed towards the rotor support frame lending forces supported rotatably. In this way, the gyroscopic moments of the transmission gears and the components rotating with them are compensated, and the centrifugal forces, as in the case of the storage and support of the planet gears and their rotating components, are in turn canceled in a closed frictional connection by the common axis of rotation and are achieved by the corresponding design described of the respective total masses and their center of gravity distances (whereby the sum of all static mass moments is zero) of the same size, so that overall, even with these transmission gears and their arrangement and mounting, the rotor support frame is completely or largely relieved of the effects of the gyroscopic forces and the centrifugal forces. Thus, even with this engagement of transmission gears, the desired extraordinarily high speeds can be achieved. At the same time, the connected gears lead to the desired opposite directions of rotation, and there is a significantly increased distance between the actual drive system with the planet gears and the drive disk facing this with its rotating element, which can be used for rope guidance with a relatively large radius of curvature, and so on overall to achieve a gentle rope guide. In this arrangement, the rope is also continuously the nickel direction and the trigger plate alternately guided over the trigger plates. This results in a rope guide on the trigger disks in the form of an 8.

In order to achieve a particularly careful guidance for the rope on the trigger disks. in the case of both pulling disks provided with circumferential guide grooves, these circumferential grooves of the pulling disks are offset with respect to one another in the axial direction, preferably by half the groove spacing. However, the axis of rotation of the second trigger disk can also be inclined by a predetermined small angle with respect to that of the first trigger disk including the respective rotation elements.

Taking advantage of the described compensation effects of the stranding device according to the invention, a particularly reliable assignment of the individual speeds is also achieved in the design of the rotary drives for the stranding device according to the additional invention, in order to master both the take-off process and the subsequent winding process exactly, without complex and to have to use control devices susceptible to faults.

If the device according to the invention is used as a pre-twist and take-off device with a downstream winding device for the rope, which has a circumferential, coaxially arranged rotor element, along which the rope grained by the pre-twist and take-off device is guided along the common axis of rotation, and one of the Rotor element revolving winding drum, so in a further embodiment of the invention, the rotary drive for the rotor support frame and the rotary drive for the take-off disks of the pre-twist and take-off device, as well as the rotary drive for the rotor element of the winding device are derived from a common main drive motor in constant coupling by mechanical positive drive. There is thus, so to speak, a form-fitting coupling of the most important rotary drives to one another and thus an exact control of the forces and tensile stresses acting on the rope, without complex and fault-prone control measures on the rope itself would be required in the action on individual rotary drives or motors, so that overall the stranding device thus created is simple and reliable.

In order to enable an exactly reproducible adjustment of the stroke length in a simple manner, an adjustable gear can be switched on in a further embodiment of the additional invention between the main drive motor and the rotary drive for the trigger disks, here the planetary gear, for. B. a step or continuously variable transmission.

• Fig. 1 eine weitestgehend schematisch gehaltene Seitenansicht der Verseileinrichtung nach der Erfindung mit geschnittenem Rotortragrahmen,
• Fig. 2 einen Längsschnitt durch die Abzugeinrichtung der Verseileinrichtung nach Fig. 1 mit Abzugscheibe und gegenläufigem Rotationselement,
• Fig. 3 eine weitestgehend schematisch gehaltene Seitenansicht der Verseileinrichtung nach einer weiteren Ausgestaltung der Erfindung mit geschnittenem Rotortragrahmen und zwei Abzugscheiben mit ihren Antrieben,
• Fig. 4 eine schematische Prinzipskizze der Seilführung auf den Wickelflächen der Abzugscheiben bei der Ausgestaltung nach Fig. 3 und
• Fig. 5 eine rein schematische Seitenansicht einer gesamten Verseileinrichtung mit der Vorverdrall- und Abzugeinrichtung, hier als Beispiel gemäß Fig. 3, und der Wickeleinrichtung, wobei die Vorverdrall- und Abzugeinrichtung als Einfachschlag-Verseileinrichtung und die Wickeleinrichtung als Doppelschlagwickler beispielsweise dargestellt sind.

Further features, details and advantages of the invention result from the claims and the following description of exemplary embodiments of the stranding device according to the invention with reference to the drawing. It shows

• 1 is a largely schematic side view of the stranding device according to the invention with a cut rotor support frame,
• 2 shows a longitudinal section through the take-off device of the stranding device according to FIG. 1 with take-off disk and counter-rotating element,
• 3 is a largely schematic side view of the stranding device according to a further embodiment of the invention with a cut rotor support frame and two take-off disks with their drives,
• Fig. 4 is a schematic schematic diagram of the cable guide on the winding surfaces of the pull-off disks in the embodiment according to Fig. 3 and
• 5 is a purely schematic side view of an entire stranding device with the pre-twist and take-off device, here as an example according to FIG. 3, and the winding device, the pre-twist and take-off device being shown as a single-twist twisting device and the winding device as a double-twist winder, for example.

In the following, the basic embodiment of the invention is first described and explained with reference to FIGS. 1 and 2.

A rotationally symmetrical, namely cylindrical, rotor support frame 1 is rotatably supported at both ends about its longitudinal axis in a suitable machine frame, which is indicated at 2. At one end the rotor support frame 1 is driven via a drive wheel or a drive pulley 3 for rotation about its longitudinal axis, e.g. B. by a suitable belt drive, as indicated by the arrow 4. The drive pulley 3 also forms the entry stranding point 5 for the rope elements 6, which are twisted into the rope 7. The cable 7 is guided through the hollow bearing shaft 8 of the rotor support frame into it and is guided to the take-off disk, which is generally designated 10, via a plurality of cable pulleys 9 mounted on the inside of the rotor support frame. After wrapping the take-off pulley, the rope is returned to the longitudinal axis of the rotor support frame 1 via a further plurality of rope pulleys 9, which are mounted on the inner wall of the rotor support frame 1, and is guided outwards through the hollow bearing shaft 11 in a manner to be described. The end of the rotor support frame 1 directed towards the bearing shaft 11 is referred to below as the rope exit end of the rotor support frame.

As will be described in detail with reference to FIG. 2, the extractor disk 10 with its associated components is rotatably mounted on a common axis of rotation 12 such that the components rotating with it extend to one side of the rotor support frame, in FIG. 1 upwards.

On the same common axis of rotation 12 there is also rotatably mounted a rotational element which is rotated in the opposite direction to the direction of rotation of the extraction disk 10 and is generally designated 13 in FIG. 1. The components rotating with the rotating element 13 are arranged towards the other side of the axis of rotation, directed downwards in FIG. 1.

A pulley 14 is connected to the take-off pulley 10 and a pulley 15 to the rotating element 13.

A planetary gear arranged at the rope exit end of the rotor support frame 1 serves for the counter-rotating rotation drive of the take-off disk 10 with 14 and rotation element 13 with 15. The sun gear 16 is rotatably supported about the longitudinal axis of the rotor support frame 1 by means of a hollow shaft 17 in the hollow bearing shaft 11 of the rotor support frame 1 and is driven by a suitable drive pulley 18, for. B. a belt drive indicated by the arrow 19. The cable 7 is guided to the outside by the sun gear 16 and its hollow shaft 17. With the sun gear (bevel gear) 16 mesh the two planet gears (bevel gears) 20 and 21, which thus, as indicated by the arrows, are driven in opposite directions. The planet gears 20 and 21 are also designed as pulleys and are in drive connection via the belts, in particular toothed belts 22, with the pulleys 14 and 15 of the take-off pulleys 10 and the rotary element 13. The planet gears 20 and 21 are rotatably mounted on a common axis of rotation 23. The axes of rotation 12 and 23 are fastened in the rotor support frame wall in a rotationally fixed manner using suitable fastening means, as is initially shown schematically in each case at 24.

According to the invention, the shape, the dimensions, the masses and the rotational speeds of the take-off disk 10 and of the rotary element 13 and of the respective components rotating with them are selected such that the respective product of the moment of inertia and the angular velocity of the rotating units is at least approximately the same size. Furthermore, the product of the total mass of the components assigned to the trigger plate 10 and the distance from their common center of gravity from the longitudinal axis of the rotor support frame 1 is at least approximately equal to the product of the Total mass of the components assigned to the rotating element 13 and the distance from their common center of gravity from the longitudinal axis of the rotor support frame 1, which means that the sum of the static mass moments is zero. A corresponding dimensioning rule applies to the planet gears 20 and 21 with their components rotating together with them as counter-rotating units. In the exemplary embodiment, the planet gears 20 and 21 and the pulleys 14 and 15 and thus the take-off pulley 10 and the rotating element 13 are each driven with the same, but opposite, speeds, a suitable reduction between the planetary gear 20 and pulley 14 and the planetary gear 21 and pulley 15 being selected can.

2 shows an exemplary embodiment of the structural design of the part of the stranding device relating to the take-off device.

The pull-off disk, generally designated 10, consists of a disk-shaped fastening flange 25 and a circumferential ring body 26 arranged on its outer circumference, which forms the winding surface or the pull ring for the looping rope. The mounting flange 25 is firmly connected to the flange of an associated hollow shaft 28 together with the associated pulley 14 by a suitable screw connection 27. This hollow shaft 28 is rotatably supported on the common axis of rotation 12 designed as a support axis, specifically towards the center via a radial bearing 29 which is supported on a central collar 30 of the axis of rotation 12, and on the side facing the rotor support frame 1 via a combined one Radial and axial bearing 31. The bearing 31 is supported against the large head of a tie rod 32, which is screwed coaxially into the axis of rotation and support 12, as shown in FIG. 2. The entire circumferential assembly 25, 26, 14, 28 is thus supported in the axial direction against the tie rod 32.

The rotating element, generally designated 13, also consists of a disk-shaped fastening flange 33 and a circumferential ring body 34 arranged on its outer circumference, which, as FIG. 2 clearly shows, engages under the circumferential ring body 26 of the trigger disk 10, so that the rotating body 13 and the trigger disk 10 are nested one inside the other . With the aid of a suitable screw connection 35, the fastening flange 33 of the rotary element 13 and the associated pulley 15 are firmly connected to a hollow shaft 36. The hollow shaft 36 is supported at its center end via a radial bearing 37 on the common axis of rotation and support 12, the bearing 37 being supported on the collar 30 of the axis of rotation and support 12. At the end of the rotor support frame wall, the hollow shaft 36 is mounted on the common axis of rotation and support 12 via a combined radial and axial bearing 38. The bearing 38 is supported in the axial direction on the large-sized head of a tie rod 39, which, as shown clearly in FIG. 2, is screwed into the common axis of rotation and support 12 and, like the tie rod 32, against rotation, for. B. is secured by a pin 40 or the like. The counter-rotating unit from 33, 34, 15, 36 is thus supported by the tie rod 39 so that it can rotate in the axial direction on the common axis of rotation and support 12.

The common rotation and support axis 12 is connected to the rotor support frame via the two tie rods 32 and 39 by a suitable adjustable screwing device, which is generally designated 24, as clearly shown in FIG. 2. The arrows 41 indicate the counter-rotating drive and thus rotational movement of the extraction disk 10 with its associated components and of the counter-rotating element 13 with its rotating components.

The I ig. 2 described with regard to the trigger device special storage via the hollow shaft, the combined radial and axial bearings and the tie rods is used in a corresponding manner in the storage of the planet gears 20 and 21 on their common axis of rotation 23.

In the illustrated embodiment, the trigger plate 10 with its rotating construction. elements and the counter-rotating element 13 with its rotating components with opposite, but the same rotational speed. In order to achieve the above-described compensation of the gyroscopic torques, it is also possible, with a corresponding choice of the shape, the dimensions and the masses of the oppositely rotating units, to use opposite, but different, rotational speeds. Fig. 2 also shows particularly clearly that in order to achieve the described compensation effect in particular the shape, the dimensions and the mass, that is to say also the material, of the circumferential ring body 34 of the rotary element 13 can be selected in a particularly adaptable manner. The same also applies to the respective characteristic data of the circumferential ring body 26 of the take-off disk 10, which forms the pull ring for the rope. 2 makes it clear that the desired compensation effect can be achieved by suitable "asymmetrical" selection of the characterizing data. Likewise, Fig. 2 makes it clear that the entire extraction device has a closed power flow with respect to its centrifugal forces over the common axis of rotation and support 12, so that all centrifugal forces occurring are absorbed within this closed system and cannot affect the rotor support frame 1.

3 to 5 further embodiments of the invention are described and explained.

In Fig. To 5 and the following description, only those components of the stranding device are described, which to Er clarification of the embodiment of the invention are required. Otherwise, the structural configuration, in particular of the extraction disks with their rotating elements, corresponds to that described with reference to FIGS. 1 and 2.

A rotationally symmetrical, namely cylindrical, rotor support frame 1a is rotatably supported at both ends about its longitudinal axis in a suitable machine frame, which is indicated at 2. At one end, the rotor support frame 1a is driven via a drive wheel or a drive disk 3 for rotation about its longitudinal axis, e.g. B. by a suitable belt drive, as indicated by the arrow 4. The drive pulley 3 also forms the entry stranding point 5 for the rope elements 6, which are twisted into the rope 7. The cable 7 is guided through the hollow bearing shaft 8 of the rotor support frame 1a into it and is guided via a plurality of cable pulleys 9 mounted on the inside of the rotor support frame to the pull-off disks, which are generally designated 10a and 10b. The rope first runs onto the first take-off disk 10a facing it and is then repeatedly guided alternately over both take-off disks. As FIG. 4 shows, the cable 7 is continuously guided over the winding direction and the take-off disk alternately over these take-off disks 10a and 10b, so that there is a course in the form of figures of eight, as shown in FIG. 4 schematically. After wrapping both pulling disks 10a and 10b, the rope 7 is returned to the longitudinal axis of the rotor support frame 1a via a further plurality of rope pulleys 9, which are mounted on the inner wall of the rotor support frame 1a, and is guided outward through the hollow bearing shaft 11 in a manner to be described.

The end of the rotor support frame 1a directed towards the bearing shaft 11 is referred to below as the rope exit end of the rotor support frame.

As is described in detail with reference to FIGS. 1 and 2, both the trigger disk 10a and the trigger disk 10b with their associated components are rotatably mounted on a common axis of rotation 12a or 12b in such a way that the components rotating therewith are to one side of the rotor support frame 1a extend towards, in Fig. 3 upwards.

On the same common axes of rotation 12a and 12b, a rotation element _t , which is rotated in opposite directions with respect to the direction of rotation of the respective associated extraction disc 10a or 10b, is also rotatably supported, which rotation elements are generally designated 13a and 13b in FIG. 3. The components rotating with the rotation elements 13a and 13b are arranged towards the other side of the axis of rotation 12a and 12b, respectively, downward in FIG. 3.

Both trigger disks 10a and 10b are connected to a gear 14a and 14b. Each rotary element 13a and 13b is connected to a gear wheel 15a and 15b, respectively.

A planetary gear arranged at the rope exit end of the rotor support frame 1a serves for the counter-rotating rotation drive of the extraction disks 10a and 10b on the one hand and of the rotation elements 13a and 13b on the other hand with their respectively assigned gear wheels 14a, 14b and 15a, 15b. Whose sun gear 16 is rotatably supported about the longitudinal axis of the rotor support frame 1a by means of a hollow shaft 17 in the hollow bearing shaft 11 of the rotor support frame 1a and is driven by a suitable drive pulley 18, for. B. a belt drive indicated by the arrow 19. The cable 7 is guided to the outside by the sun gear 16 and its hollow shaft 17. With the sun gear 16 designed as a bevel gear mesh the two planet gears 20 and 21 designed as bevel gears, which are thus driven in opposite directions. The planet gears 20 and 21 are each connected to a gear 20a and 21a. Between the gears 20a and 21a of the planet gears 20 and 21 and the gears 14b and 15b of the second drive pulley 10b located to the drive system and its associated rotating element 13b, a transmission gear 20b or 21b is connected. Thus, the gearwheels 20a, 20b, 14b, 14a assigned to the extraction disks on the one hand and the gearwheels 21a, 21b, 15b and 15a assigned to the rotating elements are each driven in opposite directions to one another, as indicated by the arrows drawn on the gearwheels in FIG. 3. The planet gears 20 and 21 with their gears 20a and 21 and the transmission gears 20b and 21b are each mounted on a common axis of rotation 23a and 23b. The axes of rotation 12a, 12b, 23a and 23b are fastened in a rotationally fixed manner in the rotor support frame wall using suitable fastening means, as is shown schematically in each case at 24.

As described with reference to FIGS. 1 and 2, the shape, the dimensions, the masses and the rotational speeds of the extraction disks 10a and 10b as well as the rotating elements 13a and 13b and the respective components rotating with them are selected such that the respective product of the moment of inertia and angular velocity the units rotating around each other is at least approximately the same size. Furthermore, the product of the total mass of the components assigned to the extraction disks 10a and 10b and the distance from their common center of gravity from the longitudinal axis of the rotor support frame 1a is at least approximately equal to the product of the total mass of the components assigned to the rotating element 13a or the rotating element 13b and the Distance from their common center of gravity from the longitudinal axis of the rotor support frame 1a, which means that the respective sum of the static mass moments is zero. A corresponding dimensioning rule applies to the planet gears 20 and 21 with their gears 20a and 21a a with their components rotating with them as counter rotating components. The corresponding dimensioning rule also applies to the transmission gearwheels 20b and 21b with their components rotating together with them. In the illustrated embodiment, the planet gears 20 and 21 with their gears 20a and 21a, the transmission gears 20b and 21b, the extractor disks 14b and 14a and the rotation elements 13b and 13a are each driven at the same, but in opposite directions, speeds. Suitable ratios and reductions can, however, be selected depending on the application, while observing the design rule according to the invention. It is crucial that the design rule described in detail above and reproduced in the preceding is observed in each case.

The winding surface of at least one of the take-off disks 10a or 10b is provided with circumferential guide grooves for rope guidance, which are not shown in detail in order to simplify the drawing. These are known concentric grooves arranged next to one another and adapted to the respective application on the winding surface of the respective take-off disk. A particularly precise cable guide on the winding surfaces of the pull-off disks can be achieved in that the winding surfaces of both pull-off disks 10a and 10b are provided with such circumferential guide grooves. It is expedient if the circumferential guide grooves of the pull-off disks 10a and 10b are offset in relation to one another in the axial direction, preferably by half the groove spacing, in order in this way to achieve a particularly favorable cable guide. However, the axis of rotation 12b of the + second trigger disk 10b can also be inclined by a predetermined small angle with respect to the axis of rotation 12a of the first trigger disk 10a. Of course, the toothing of the gears 14a, 14b and 20b and 15a, 15b and 21b are to be designed accordingly.

5 shows a further embodiment of the invention largely schematically. FIG. 5 first shows schematically at V the pre-swirl and extraction device described with reference to FIG. 3 with the rotor support frame 1a. This pre-twist and take-off device V is followed by a winding device W. This winding device is designed in a manner known per se as a so-called double-winder. The rope 7 leaving the device V is fed coaxially to the winding device W. This has a coaxially arranged revolving rotor element 42 and a winding drum 43 freely oscillating therein with the associated cable guide and laying devices, which are not identified in detail and are designed in a manner known per se. The cable 7 is fed along the rotor element 42 through the longitudinal axis of the winding device W via the cable guide and laying devices (not shown) to the winding drum 43 in a manner known per se. A double twist winder follows the pre-twist and take-off device V in the form of a so-called single twist stranding machine. With this overall arrangement, the individual rotational speeds are to be coordinated with one another in a predetermined manner.

According to the invention, the rotary drive for the rotor support frame 1 a and the rotary drive for the take-off disk within the rotor support frame 1 a, i.e. for the planetary gear with its drive disk 18 of the pre-twist and take-off device V, and the rotary drive for the rotor element 42 of the winding device W are in constant coupling by mechanical positive drive from derived from a common main drive motor, which is designated 44. For this purpose, the main drive ₃ motor 44 drives a pulley 46 via a shaft 45, which drives the drive pulley 3 for the rotor support frame 1 a via the belt 4. The planetary drive system for the extraction disks of the rotor support frame 1 a is coupled to the shaft 45 of the main drive motor 44 via an adjustable gear 47 via the output shaft 48 and the pulley 49 and the belt 19 and the drive pulley 18. A differential gear with its own motor can be provided as the adjustable gear 47. Finally, the rotor element 42 is also coupled to the main drive motor 44 via a further shaft 50 of the main drive motor 44 and a suitable belt drive, which is generally designated 51. Furthermore, the drive for the rotor element 42 and for the winding drum 43 with its cable guiding and laying devices is derived from the shaft 50 of the main drive motor 44 via the belt drive 52, as shown schematically in FIG. 5. Thus, in the manner described in principle above, the individual rotary drives are in constant coupling by means of a mechanical positive drive.

The embodiment described above can also be realized with the stranding device according to FIGS. 1 and 2 as a pre-twist and take-off device V.

Claims (15)

1. Stranding device for stranding machines, particularly a pre-twist and drafting device as an advance ancillary device for single or multiple rope-lay machines, with a driven rotor support frame and a driven drafting wheel mounted on the rotor support frame transversely of the rotational and longitudinal axes thereof, in which the wire rope components are supplied to a stranding entry station in the longitudinal axis of the rotor support frame and the wire rope is guided at the rotor support frame to the drafting wheel and, after passing round it, is guided from the rotor support frame along the longitudinal axis, characterized in that a rotary member (13), driven in the opposite direction of rotation, is rotatably mounted on the axis of rotation (12) of the drafting wheel (10) coaxially to it and the shape, dimensions, masses and velocities of rotation of the drafting wheel (10) and the rotary member (13), as well as the components (26, 25,14, 27, 28; 34, 33, 15, 35, 36) rotating with them, are so se lected that the product of the mass moment of inertia and the angular velocity of the counter-rotating components is at least approximately uniform in magnitude and that the drafting wheel (10) and the rotary member (13) are each mounted on their common axis of rotation (12) by means of an associated hollow shaft (28, 36) and the hollow shafts (28, 36) additinally are rotatably mounted and supported (31, 32; 38, 39) on the common axis of rotation (12) against centrifugal forces directed toward the rotor support frame (1) and that the product of the total mass of the components (26, 25, 14, 27, 28, 31, 32, 12, 24) associated with the drafting wheel (10) and the distance of their common centre of mass from the longitudinal axis of the rotor support frame (1) is made at least approximately equal to the product of the total mass of the components (33, 34, 15, 35, 36, 38, 39, 24, 12) associated with the rotary member (13) and the distance of their common centre of mass from the longitudinal axis of the rotor support frame (1).

2. Stranding device according to claim 1, characterised in that the drafting wheel (10) and the rotary member (13) are rotatably driven by means of a belt drive with belt pulleys (14, 15), particularly a toothed belt drive, arranged on the side facing the rotor support frame (1) and planetary gearing (16, 20, 21) is arranged at the wire rope outlet end of the rotor support frame (1) so that the sun wheel (16) is mounted for rotation about the longitudinal axis of the rotor support frame (1) upon a hollow driving shaft (17) receiving the wire rope (7) at the wire rope outlet end (11) of the rotor support frame (1) and the coun ter-rotating planet wheels (20, 21), constructed as belt pulleys, are mounted on a common axis of rotation (23), which runs parallel to the axis of rotation (12) of the drafting wheel (10) and the rotary member (13), and that the planet wheels (20, 21) with the components rotating with them, are so arranged in shape, dimensions, masses and velocities of rotation, that the product of the mass moment of inertia and the angular velocity of the counter-rotating components is at least approximately uniform in magnitude and are rotatably mounted and supported, on their common axis of rotation (23), against centrifugal forces directed toward the rotor support frame (1).

3. Stranding device according to claim 1 or 2, characterized in that the drafting wheel (10) and the counter-rotating rotary member (13) respectively consist of a disc-shaped mounting flange (25, 33) and a laterally projecting peripheral annular body (26, 34) directed toward the other mounting flange, where the peripheral annular body (26) of the drafting wheel (10) forms the winding surface (drafting tool) for the wire rope and the peripheral annular body (34) of the rotary member (13) lodges within the peripheral annular body (26) of the drafting wheel (10).

4. Stranding device according to any of claims 1 to 3, characterized in that the drafting wheel (10) and the rotary member (13) and their associated annular belt pulleys (14, 15) are secured on the respective associated hollow shafts (28, 36) and each hollow shaft is rotatably supported at its end facing the rotor support frame on a tie rod (32, 39) by means of a combined radial and axial bearing (31, 38), each tie rod (32, 39) is inserted coaxially, and preferably screwed, into a common mounting shaft (12) forming the axis of rotation and each tie rod (32, 39) is connected with the adjacent rotor support frame wall.

5. Stranding device according to claim 4, characterised in that the hollow shafts (28, 36) are supported at their ends adjacent the longitudinal axis of the rotor support frame (1) by means of a radial or combined radial and axial bearing (29, 37) at a central collar (30) of the mounting shaft (12).

6. Stranding device according to claim 4 or 5, characterised in that the tie rods (32, 39) are secured in the rotor support frame wall by means of a screw connection (24) which is adjustable in the longitudinal direction.

7. Stranding device according to any of claims 1 to 6, characterized in that the wire rope (7) is guided in the rotor support frame (1) by means of a plurality of wire rope guide rollers (9) mounted on its interior wall.

8. Stranding device according to any of claims 1 to 7, characterized in that the rotor support frame (1) is constructed as a rotationally-symmetrical, and especially cylindrical, drum- shaped hollow body.

9. Stranding device according to any of claims 1 to 8, characterized in that a second drafting wheel (10b), with an associated rotary member (13b) driven in the opposite direction of rotation, is mounted on the rotor support frame on a further axis of rotation (12b) running transversely of the rotational and longitudinal axes of the rotor support frame (1 a) and the second drafting wheel (10b) and the associated rotary member (13b), as well as the associated components, are shaped, dimensioned and arranged in the same way as the corresponding components of the first drafting wheel (10a) with its rotary member (13a), the wire rope (7) is guided so as to pass continuously round and from one to the other of both of the drafting wheels (10a, 10b) and the winding surface of at least one of the drafting wheels (10a or 10b) is provided with peripheral guide grooves for guiding the wire rope.

10. Stranding device according to claim 9 with a driving system constructed as planetary gearing according to claim 2, characterised in that each drafting wheel (10a, 10b) and each associated rotary member (13a, 13b) is rotationally driven, by means of an associated gearwheel (14a, 14b, 15a, 15b) connected with it, from the planet wheels (20, 21) which are provided with associated gearwheels (20a, 21 a).

11. Stranding device according to claim 10, characterised in that a transmission gearwheel (20b, 21b) is mounted between the planet wheels (20, 21) of the driving system and their gearwheels (20a, 21a) and the gearwheels (14b, 15b) of the second drafting wheel (10b) connected to the driving system and its associated rotary member (13b) and these counter-rotating transmission gearwheels (20b, 21b) are mounted like the planet wheels (20, 21) with their gearwheels (20a, 21a) on a common axis of rotation (23b), which runs parallel to the axis of rotation (23a) of the planet wheels (20, 21), and that the transmission gearwheels (20b, 21b) are arranged in shape, dimensions, masses and velocities of rotation, like the planetary gearing and the gearwheels with their rotating parts, so that the product of the mass moment of inertia and the angular velocity of the counter-rotating components is at least approximately uniform in magnitude and are rotatably mounted and supported on their common axis of rotation (23b) against centrifugal forces directed toward the rotor support frame (1a) and that the wire rope (7) is guided continuously, so as to pass round and from one to the other of the drafting wheels (10a, 10b) while changing its direction of winding.

12. Stranding device according to any of claims 9 to 11, characterised in that the peripheral guide grooves on the drafting wheels (10a, 10b) are mutually displaced in the axial direction, preferably by half the groove width.

13. Stranding device according to any of claims 9 to 11, characterized in that the axis of rotation (12b) of the second drafting wheel (10b) is inclined at a prescribed small angle relative to that of the first drafting wheel (10a).

14. Pre-twist and drafting device according to any of claims 1 to 13 with an associated winding device for the wire rope, which comprises a rotating coaxially-arranged rotor member at which the wire rope from the rotor support frame is guided along the common axis of rotation, and a winding drum orbited by the rotor member, characterised in that the rotary drive (3, 4) for the rotor support frame (1a) and the rotary drive (18, 19) for the drafting wheels of the pre-twist and drafting device, as well as the rotary drive (51, 52) for the rotor (42) of the winding device (W), are derived, in continuous connection by mechanical driving means, from a common main driving motor (44).

15. Device according to claim 14, characterised in that a variable gear unit (47) is provided between the main driving motor (44) and the rotary drive (18, 19) for the drafting wheels in the rotor support frame (1a).

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