EP0088993A1 - Twisting apparatus for stranding machines, in particular a pretwisting and drawing apparatus - Google Patents

Abstract

In such a device with a rotor support frame and a take-off disk mounted transversely to its axis of rotation, the effects of the centrifugal and centrifugal forces on the rotor support frame are to be largely avoided. For this purpose, an opposite rotationally driven rotating element (13) is mounted on the axis of rotation (12) of the trigger plate (10). Shape, dimensions, masses and / or speeds of rotation of the take-off disc (10) and rotary element (13) and of the rotating components (26, 25, 14, 27, 28; 34, 33, 15, 35, 36) are selected such that the respective product of the moment of inertia and the angular velocity of the structural units rotating against one another is at least approximately the same size. The take-off disk (10) and the rotating element (13) are each mounted on the common axis of rotation (12) via a hollow shaft (28, 36). The hollow shafts (28, 36) are rotatably supported (31, 32; 38, 39) against the centrifugal forces directed towards the rotor support frame (1) on the axis of rotation (12). The product of the total mass of the components (25, 26, 14, 27, 28, 31, 12, 24) assigned to the pull-off disk (10) and the distance from their common center of gravity from the longitudinal axis of the rotor support frame (1) is at least approximately the same Measure the product of the total mass of the components (33, 34, 15, 35, 36, 38, 29, 24, 12) assigned to the rotary element (13) and the distance from their common center of gravity from the longitudinal axis of the rotor support frame (1).

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 rotational 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; however, they are considerably too slow compared to the conventional double impact 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 single layers, especially with significantly smaller fluctuations in the outer diameter than in 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 much smaller wire diameter tolerances allow considerable ge thinner 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) in spite of high-speed double-stroke production speed, pre-load so gently that excessive stretching and hardening of the stranded material is prevented and thus, for example, a drop in the electrical conductivity of the high-voltage strand is avoided.

It is not important here that a strand stranded in single lay without partial intermediate rope is passed through a double impact machine onto the take-up reel. It is crucial that the entire rope run (as a double single run) is carried out in the single run pre-twisting device, so that the correct wire lengths required for the double and finished line run are drawn for all inner to outer wire layers. 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 incoming wire lengths, which initially matched from position to position - that is to say balanced - are no longer correct for the subsequent second lay, because then the inner wire layers have a relatively large excess length compared to the outer wire layers. The relative excess length, which increases in the case of multilayer ropes from outer to inner layers, ie 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 to today's double twist machines.

So-called pre-swirl devices are already used in industrial practice to meet only the requirements mentioned under a) (see "Wireworld" 7/1977, page 270, picture 7 and page 271, 4th to 6th

Paragraph of the essay "Comparison of the Single and Double Punching Process" by A.C. Osman). Although these facilities run quickly, they only have simple drag disks 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 twist device, but is even increased considerably by the centrifugal force additionally generated in the device and not compensated by it. A driven take-off disk, which is wrapped several times by the strand, 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 released 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 well-known pre-twist and take-off devices of the type specified at the outset (eg AT-PS 286 833) are unsuitable for high-speed double-stroke production speed 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. This would also result in one completely indiscutable short lifespan of the roller bearings involved.

A further 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 which 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 about 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 without the described adverse effects the gyroscopic and centrifugal forces reach an intolerable level. 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 number of seaweeds. 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 take-off disk and the shape, dimensions, masses and / or the rotational speeds of the take-off disk and the rotary element as well as with their rotating components 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, and that the trigger plate and the rotating element are each mounted on the common axis of rotation with the help of an assigned hollow shaft and the hollow shafts are also against the centrifugal forces directed to the rotor support frame are rotatably supported on the common axis of rotation and that the product of the total mass of the components assigned to the trigger disk and the distance from their common center of gravity from the longitudinal axis of the rotor support frame is dimensioned at least approximately equal to the product of the total mass of the components assigned to the rotary 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 components, the gyro moment generated by the component containing the extractor disc with the resulting gyroscopic forces is compensated for by the gyro torque generated with the counter rotating component containing the rotating element, so that the described strong and harmful gyroscopic forces do not affect the rotor support frame. Due to the inventive support of the extractor disk and the rotating element on the side facing the rotor support frame, a closed power flow is achieved within both units via the axis of rotation, so that in connection with the inventive design of the respective total masses and their center of gravity distances (sum of all static mass moments equal to zero) 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 more than 4000 rope strikes per minute can be generated in continuous operation, so that now with such a stranding device the difficulties described above in the strand and / or rope production can be overcome. The rotor support frame only serves for the spatial fixation of the entire trigger unit with regard to the trigger disk, a further load on the impact rotor is no longer or only to a small extent due to the compensation of the gyroscopic moments and the closed force flow for the centrifugal forces stem measure instead. 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 and 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 construction with corresponding compensation effects is achieved according to one embodiment of the invention in that the trigger disk and the rotating element are each driven in rotation via a belt drive with belt pulley, in particular toothed belt drive, located on the rotor support frame, and a planetary gear is arranged at the rope exit end of the rotor support frame in such a way that 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 take-off disk and the rotating element, and that the planet wheels also their rotating components are dimensioned in shape, dimension, mass and / or rotational speeds such that the respective product of the moment of inertia and angular velocity of the against each other-rotating components is at least approximately equal size, and at their common pivot _- axis are directed against the centrifugal forces to the rotor support frame rotatably mounted, again combined radial and thrust bearings may 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 in principle has an extraordinarily symmetrical structure, and the opposite drive movement for the trigger plate 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 torques of the planet gears and the components rotating with them are compensated, the centrifugal forces are in turn canceled in a closed power flow through the common axis of rotation and apply the same dimensioning of the respective total masses and their center of gravity distances (sum of all static mass moments equal to zero) as described by 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 that is advantageous for the compact design on the one hand and for the desired compensation effect for the gyro moments 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 consist of one disk-shaped mounting flange and a laterally projecting, facing the other mounting flange directed circumferential ring body, the circumferential ring body of the pull-off disk forms the winding surface (the pull ring) for the rope and the circumferential ring body of the rotary element engages under the circumferential ring body of the pull-off 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 circumferential ring body, which forms the main mass of the counter-rotating element, is largely enclosed by the circumferential ring body of the take-off disk, which is particularly beneficial for the compensation of the 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 in view of 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 located on the rotor support frame End face on 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 unit that forms the closed power flow 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 support according to the invention, which is described on the basis of the mounting of the pull-off disk and the rotating element, can be carried out on tie rods on the common axis of rotation can also be used with a corresponding advantage.

A further embodiment of the invention is based on the object, to design and improve the stranding device according to the main patent so that any uncontrolled course of the rope on the take-off disk with the possible consequence of inadequate removal or rope tear is avoided and instead a correct and clean guidance of the rope reached on the trigger disk. 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 rotational element driven in the opposite direction of rotation is mounted on the rotor support frame and the second Trigger disk and associated rotary element and the associated components are all designed, dimensioned and arranged like the corresponding elements of the first trigger disk with their rotary 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 disk and corresponding alternate guidance of the rope on the take-off disks 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 disks and thus to a correct and clean guidance of the rope on the take-off disks even at the highest possible speeds, so an inadequate Deduction 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 take-off disk and its associated rotating element in the same way as the corresponding elements and structural units of the first take-off disk in this second take-off disk and its rotary element. It is expressly noted here that all of the design, dimensioning and arrangement rules which are described and identified in the main patent with regard to the first pulling disk and its rotating element are also implemented in the second pulling disk and its rotating element, so that there is no detailed description 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 particularly reliably.

In this embodiment, it is also assumed that a drive system designed as a planetary gear is used for the rotary drive of the extraction disks, 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 expressly noted that 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, in the sense characterized above, transmission gears are used according to the invention for the rotary drive of the individual revolving 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 that 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 located on the drive system and its associated rotating element , and these counter-rotating transmission gears, like the planet gears, are mounted on a common axis of rotation, which runs parallel to the axis of rotation of the planet gears, and the transmission gears, like the planet gears, with their rotating components are dimensioned in the form, dimension, mass and / or rotational speeds, that the respective product of the moment of inertia and the angular velocity of the structural units rotating against one another is at least approximately the same size, and is directed at their common axis of rotation against the rotor support frame Centrifugal bearings are supported so that they can rotate. In this way, the gyroscopic moments of the transmission gearwheels and the components rotating with them are also compensated for, and the centrifugal forces are the same as in the case of storage and support the planet gears and their rotating components in turn in a closed power flow through the common axis of rotation and are dimensioned by the described corresponding dimensioning of the respective total masses and their distances from the center of gravity (the sum of all static mass moments is zero), so that overall also with these transmission gears and their arrangement and storage of 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 extremely 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 exhaust disc facing this with its rotating element, which can be used for cable 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 changing the winding direction and the take-off disk over the take-off disks. This results in a rope guide on the trigger disks in the form of an 8.

In order to achieve particularly careful guidance for the rope on the pull-off disks, in the case of both pull-off disks provided with circumferential guide grooves, these circumferential grooves of the pull-off 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 rotating, coaxially arranged rotor element, along which the rope coming from the pre-twist and take-off device is guided along the common axis of rotation, and a winding drum encircled by the rotor element, 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 . This results in a kind of form-fitting coupling of the most important rotary drives with each other and thus an exact control of the forces and tensile stresses acting on the rope, without the need for complex and fault-prone control measures on the rope itself in the action of individual rotary drives or motors, so that the total thus created stranding device is simple and reliable.

In order to enable a precisely reproducible setting of the stroke length in a simple manner, in a further embodiment of the additional invention, an adjustable gear can be switched on between the main drive motor and the rotary drive for the trigger disks, here the planetary gear, e.g. a gear that can be adjusted in stages or continuously.

• 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. Show it

• 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, for example 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 hereinafter referred to as the rope exit end of the rotor support called 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 example 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 contact with the pulleys 14 and 15 of the take-off pulley 10 and the rotating element 13 via the belts, in particular toothed belts 22 drive connection. 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 / or the _' rotational speeds of the take-off disk 10 and the rotary element 13 and 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 rotary 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 a combined radial and Axial bearing 38 mounted on the common axis of rotation and support 12. The bearing 38 is supported in the axial direction on the large-sized head of a tie rod 39, which, as FIG. 2 clearly shows, is screwed into the common axis of rotation and support 12 and, like the tie rod 32, against rotation, for example by a pin 40 or the like is secured. The counter-rotating unit from 33, 34, 15, 36 is thus also 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 special bearing described with reference to FIG. 2 regarding the trigger device via the hollow shaft, the combined radial and axial bearings and the tie rods is used in a corresponding manner in the bearing of the planet gears 20 and 21 on their common axis of rotation 23.

In the exemplary embodiment shown, the take-off disk 10 with its rotating components and the counter-rotating element 13 with its rotating components are driven with opposite, but the same rotational speed. In order to achieve the above-described compensation of the gyroscopic moments, however, with a corresponding choice of the shape, the dimensions and the masses of the oppositely rotating structural units, counter-rotating but different speeds of rotation can be achieved be applied. 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 applies correspondingly to the respective characteristic data of the peripheral ring body 26 of the take-off disk 10, which forms the pull ring for the rope. Fig. 2 makes it clear that the desired compensation effect can be achieved by suitable "asymmetrical" selection of the characterizing data. FIG. 2 also makes it clear that the entire extraction device has a closed force 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.

3 to 5 and the following description only those components of the stranding device are described which are necessary to explain the embodiment of the invention. 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 rotatable on both ends about its longitudinal axis in a suitable machine frame device _j , which is indicated at 2. At one end, the rotor support frame 1 a is driven via a drive wheel or a drive pulley 3 for rotation about its longitudinal axis, for example 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 led back 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 described in detail with reference to FIGS. 1 and 2, both the extraction disk 10a and the extraction disk 10b with their associated components are rotatably mounted on a common axis of rotation 12a and 12b in such a way that the components rotating therewith extend to one side of the rotor support frame 1a extend upwards in FIG. 3.

On the same common axes of rotation 12a and 12b there is also rotatably mounted, that is to say assigned to each pull-off disk, a rotation element which is rotated in the opposite direction to the direction of rotation of the respective associated pull-off disk 10a or 10b, which rotation elements are generally designated by 13a and 13b in FIG. The components rotating with the rotation elements 13a and 13b are arranged on the other side of the axis of rotation 12a and 12b, respectively, pointing downwards in FIG.

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 cable exit end of the rotor support frame 1 a serves for the counter-rotating rotation drive of the extraction disks 10 _a and 10 b on the one hand and the rotation elements 13 a and 13 b on the other hand with their respectively assigned gear wheels 14 a, 14 b and 15 a, 15 b. Its 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 and is driven by a suitable drive pulley 18, for example 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. The two mesh with the sun gear 16 designed as a bevel gear designed as bevel gears planet gears 20 and 21, which are thus driven in opposite directions. The planet gears 20 and 21 are each connected to a gear 20a or 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 rotary 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 21a 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 / or 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 is based on the moment of inertia and the angular velocity of the structural units rotating against one another is at least approximately the same size. Furthermore, the product of the total mass of the components assigned to the 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 From stood 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 equal to zero. A corresponding dimensioning rule applies to the planet gears 20 and 21 with their gears 20a and 21a with their components rotating with them as oppositely 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 20 a and 21a, the transmission gears 20b and 21b, the trigger plates 14b and 14a and the rotating 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 - at least one of the pull-off disks 10a or 10b is provided with circumferential guide grooves for cable 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 extraction disks 1ca and 10b are offset from one another in the axial direction, preferably by half the groove spacing, in order in this way to provide a particularly favorable cable guide to reach. However, the axis of rotation 12b of the second trigger plate 10b can also be inclined by a predetermined small angle with respect to the axis of rotation 12a of the first trigger plate 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-twist and withdrawal device described with reference to Figure 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 rotating rotor element 42 and a winding drum 43 freely oscillating therein with the associated cable guiding 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 1a and the rotary drive for the take-off disk within the rotor support frame 1a, that is to say for the planetary gear with its drive disk 18, 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 one common samen main drive motor derived, which is designated 44. For this purpose, the main drive motor 44 drives a pulley 46 via a shaft 45, which drives the drive pulley 3 for the rotor support frame 1a via the belt 4. The planetary drive system for the extraction disks of the rotor support frame 1a is also coupled to the shaft 45 of the main drive motor 44 via an adjustable gear 47 via the output shaft 48 and the belt pulley 49 as well as 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 implemented 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, in particular pre-twist and take-off device as ballast for single or multiple impact machines, with a rotary driven rotor support frame and a rotary driven take-off disk mounted transversely to the rotational and longitudinal axis of the rotor support frame, in which the cable elements at an entry stranding point in the longitudinal axis fed to the rotor support frame and the rope on the rotor support frame to the take-off disk and after being wrapped around it by the longitudinal axis is guided out of the rotor support frame, characterized in that on the axis of rotation (12) of the take-off disk (10) coaxially to it a rotating element (13) driven in the opposite direction of rotation is rotatably mounted and the shape, the dimensions, the masses and / or the speeds of rotation of the take-off disk (10) and the rotary element (13) and the components rotating with them (26, 25, 14, 27, 28; 34, 33, 15) , 35, 36) are selected such that the respective product is inertial The torque and angular velocity of the rotating units is at least approximately the same size, and that the extraction disk (10) and the rotating element (13) are each mounted on the common axis of rotation (12) with the aid of an associated hollow shaft (28, 36) and the hollow shafts ( 28,36) are additionally supported rotatably against the centrifugal forces directed to the rotor support frame (1) on the common axis of rotation (12) (31.32; 38.39) and that the Pro product of the total mass of the components (25, 26, 14, 27, 28, 31, 32, 12, 24) assigned to the pull-off disk (10) and the distance from their common center of gravity from the longitudinal axis of the rotor support frame (1) at least approximately equal to that Product of the total mass of the components (33, 34, 15, 35, 36, 38, 39, 24, 12) assigned to the rotary element (13) and the distance from their common center of gravity from the longitudinal axis of the rotor support frame (1). 2. Stranding device according to claim 1, characterized in that the take-off disc (10) and the rotary element (13) are each rotationally driven via a belt drive with belt pulley (14, 15), in particular toothed belt drive, arranged on the side facing the rotor support frame (1) and A planetary gear (16, 20, 21) is arranged at the rope exit end of the rotor support frame (1) such that the sun gear (16) can be rotated about the longitudinal axis of the rotor support frame (1) with a hollow drive shaft (17) receiving the rope (7) in the rope exit end ( 11) of the rotor support frame (1) and the counter-rotating planet wheels (20, 21) designed as pulleys are mounted on a common axis of rotation (23) which runs parallel to the axis of rotation (12) of the extractor disc (10) and the rotating element (13), and that the planet gears (20, 21) with their rotating components in shape, dimension, mass and / or rotational speeds are dimensioned such that the respective product of mass inertia eits moment and angular speed of the rotating units is at least approximately the same size, and are rotatably supported on their common axis of rotation (23) against the centrifugal forces directed to the rotor support frame (1). 3. stranding device according to claim 1 or 2, characterized ge indicates that the pull-off disk (10) and the counter-rotating element (13) each consist of a disk-shaped fastening flange (25, 33) and a circumferential ring body (26, 34) which projects laterally thereon and faces the other fastening flange, the circumferential ring body (26) the pull-off disk (10) forms the winding surface (pull ring) for the rope and the peripheral ring body (34) of the rotary element (13) engages under the peripheral ring body (26) of the pull-off disk (10). 4. stranding device according to one of claims 1 to 3, characterized in that the take-off disc (10) and the rotary element (13) and their associated annular pulley (14, 15) are each attached to the associated hollow shaft (28, 36) and each Hollow shaft is rotatably supported on its end face facing the rotor support frame on a tie rod (32, 39) by a combined radial and axial bearing (31, 38), each tie rod (32, 39) coaxially in a common support axis (12) forming the axis of rotation used, in particular screwed in, and that each tie rod (32, 39) is connected to the facing rotor support frame wall. 5. stranding device according to claim 4, characterized in that the hollow shafts (28,36) at their end directed to the longitudinal axis of the rotor support frame (1) via a radial or a combined radial and axial bearing (29,37) on a central collar ( 30) of the support shaft (12) are supported. 6. stranding device according to claim 4 or 5, characterized in that the tie rods (32, 39) are fastened with a longitudinally adjustable screw connection (24) in the rotor support frame wall. 7. stranding device according to one of claims 1 to 6, characterized in that the rope (7) on the rotor support frame (1) is guided over a plurality of mounted on the inner wall of the rope guide rollers (9). 8. stranding device according to one of claims 1 to 7, characterized in that the rotor support frame (1) is designed as a rotationally symmetrical, in particular cylindrical, hollow drum body. 9. stranding device according to one of claims 1 to 8, characterized in that on a further, transverse to the rotational and longitudinal axes of the rotor support frame (1a) rotating axis (12b), a second take-off disc (10b) with an associated, in the opposite direction of rotation driven rotary element (13b) is mounted on the rotor support frame and the second extractor disc (10b) and associated rotary element (13b) and the associated components are all designed, dimensioned and arranged like the corresponding elements of the first extractor disc (10a) with their rotary element (13a) Rope (7) the take-off disk (10a, 10b) is continuously alternately guided over both take-off disks (10a, 10b) and the winding surface of at least one of the take-off disks (10a or 10b) is provided with circumferential guide grooves for guiding the rope. 10. stranding device according to claim 9 with a drive system designed as a planetary gear according to claim 2, characterized in that each take-off disc (10a, 10b) and each associated rotary element (13a, 13b) via an associated gear connected to it (14a, 14b, 15a) , 15b) of those with an associated gear (20a, 21a) provided planet gears (20,21) is driven in rotation. 11. Stranding device according to claim 10, characterized in that between the planet gears (20,21) of the drive system and their gears (20a, 21a) and the gears (14b, 15b) of the second take-off disk (10b) and its associated rotating element which is located towards the drive system (13b) each have a transmission gear (20b, 21b) and these opposing transmission gears (20b, 21b) like the planet gears (20,21) with their gears (20a, 21a) are mounted on a common axis of rotation (23b) which is parallel to the axis of rotation (23a) of the planet gears (20, 21), and that the transmission gears (20b, 21b), like the planet gears and their gears with their rotating components, are dimensioned in the form, dimensions, mass and / or rotational speeds in such a way that the respective product is made of Mass moment of inertia and angular velocity of the units rotating against each other is at least approximately the same size, and on their common axis of rotation (23b) against the rotor carrier hmen (1a) directional centrifugal forces are rotatably supported and that the rope (7) continuously the winding direction and the take-off disc is alternately guided over the take-off discs (10a, 10b). 12. Stranding device according to one of claims 9 to 11, characterized in that the circumferential guide grooves of the take-off discs (10a, 10b) are offset from one another in the axial direction, preferably by half the groove spacing. 13. Stranding device according to one of claims 9 to 11, characterized in that the axis of rotation (12b) of the second take-off disc (10b) relative to that of the first Trigger disc (10a) is inclined by a predetermined small angle. 14. Pre-twist and take-off device according to one of claims 1 to 13 with a downstream winding device for the rope, which has a circumferential, coaxially arranged rotor element, on which the coming from the rotor ...... support frame is guided along the common axis of rotation and has a winding drum encircled by the rotor element, characterized in that the rotary drive (3, 4) for the rotor support frame (1 a) and the rotary drive (18, 19) for the extraction disks of the pre-twist and extraction device and the Rotary drive (51, 52) for the rotor element (42) of the winding device (W) in continuous coupling by mechanical positive drive can be derived from a common main drive motor (44). 15. The device according to claim 14, characterized in that between the main drive motor (44) and the rotary drive (18,19) for the trigger disks in the rotor support frame (1a), an adjustable gear (47) is switched on.

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