EP0205485B1 - Cable stranding machine system - Google Patents

Abstract

A cable stranding machine system with a single-turn and winding device for the cable in which are coaxially arranged a winding reel (5) and a single-turn rotor (7) running around and enclosing the winding reel. The winding reel and the single-turn rotor can move back and forth axially in relation to one another in order to effect a laying travel for the cable, and it is the cable which is fed from the longitudinal axis of the single-turn rotor along the latter to the winding reel. For winding, a difference arises between the rotation speed of the winding reel and the single-turn rotor, this difference varying according to the relevant winding diameter which has been reached on the winding reel. The winding reel is driven at the nominal rotation speed and the single-turn rotor is driven separately at the rotation speed required to produce the difference in the rotation speed.

Description

The invention relates to a stranding machine system with a single lay and take-up device for the rope, in which a take-up reel and a take-up spool rotating and enclosing the take-up spool are arranged coaxially, the take-up spool and the single take-up rotor relative to one another to produce a laying stroke for the rope axially are movable back and forth and the rope is guided along the longitudinal axis of the single-lay rotor to the take-up spool, a difference in the rotational speeds of the take-up spool and single-lay rotor being generated depending on the take-up diameter of the take-up spool.

In a known stranding machine system of this (DE-PS-2 037 607) the rope is prefabricated in a so-called pre-twisting station with a driven trigger. The rope is then fed to the single-lay and take-up device in such a way that it is fed to the single-lay rotor surrounding the take-up spool and is guided along this to the take-up spool. This take-up reel is freely suspended, separately driven in rotation and is also moved back and forth to lay the rope in the axial direction. It thus immerses the take-up spool in the known single-stroke rotor. When the operating speed has been reached after the system has started up smoothly, the speed of the single-shot rotor remains constant until the winding reel is completely filled or until an emergency braking, usually over a longer production time. In order to be able to wind up the rope in the known system, the take-up spool must also rotate coaxially with the single-lay rotor at high speed. As is known, however, the take-up spool must always have a certain differential rotational speed in relation to the single-stroke rotor. Since the rope is delivered at a constant web speed or conveying speed, it is known that the rotational speed of the take-up spool is to be adjusted depending on the current winding diameter and thus on the filling condition of the spool. The differential rotational speed of the still almost empty spool in relation to the single-stroke rotor will initially be a relatively large one, but will be suitably reduced as the winding diameter increases.

In the known systems (e.g. according to DE-PS-2 037 607 or in other comparable single lay and winding devices), in order to maintain constant lengths of rope lay and as constant or compatible rope tension as possible, the control of the rotational and lifting speed of the back and forth movable reel on the one hand depending on the predetermined rotational speed of the assigned single-lay rotor and on the other hand taking into account the associated conveying speed of the rope or derived. In this case, the primary controlled single-stroke rotor, so to speak, the take-up coil secondary.

Such an adjustment of the winding speed and the laying stroke speed can be implemented in terms of control technology without any particular difficulties, as long as production is carried out at a constant cable conveying speed or only moderately accelerated or decelerated. For particularly fast stranding machine systems, however, the known solution of the single-lay and take-up device leads to practically insurmountable difficulties, for the following reasons: An increase in the number of strands simultaneously leads to the highest degree of stranding speed or rope conveying speed and thus also to the rotational speed of the known solution the single-stroke rotor with a relatively small speed difference leading or lagging take-up reel. A strong increase in the rotational speed of the separately driven winding reel in the known system, however, leads to undesirably high requirements and disadvantages. Difficulties arise, in particular, when twisting thin or collapsible stranding elements for the following reasons: When winding a rope onto a winding spool rotating about its axis, the regulation of the tension in the rope wound by it is always associated with a corresponding change in the rotational speed of the spool . On the one hand a take-up drive and on the other hand a brake acting on the take-up reel must be provided. Unpredictable and quickly effective emergency braking of the take-up spool while maintaining a constant tension in ropes and in particular in sensitive ropes, e.g. B. in thin but multi-stranded high-voltage copper wires. The particular difficulty for coordinated rapid braking of the single-stroke rotor and the take-up spool is that the take-up spool following the rotor has a completely variable mass and, above all, a dynamic mass moment of inertia which is variable to an increased extent, depending on the winding condition achieved. The dynamic mass moment of inertia is proportional to the fourth power of the winding diameter reached. Since the braking torque is directly proportional to the moment of inertia and the braking time is inversely proportional to the braking torque, this means that in order to maintain the same braking times for the single-stroke rotor on the one hand and the rewinding reel on the other hand, a braking system equipped with an extraordinarily large adjustment range for the unpredictably large braking torque would be required, which despite Excessive ßer variation range is still able to brake fully controlled from high speeds within a few seconds completely. Such a brake system would only be feasible in practice with an extremely high outlay and therefore is neither technically nor economically justifiable. In the known systems, such emergency braking would therefore lead to damage to the rope or to loops or the like. The serious disadvantage of the known systems is therefore primarily to be seen in the fact that the take-up spool with its relatively large and variable mass must on the one hand carry out the axial laying stroke movement and on the other hand regulates its speed during operation and in particular during the decelerations described, that is to say in their respective cases Movement states must be mastered.

The invention has for its object to provide a stranding machine system of the type mentioned, in which by a special design of the single lay and take-up device a reciprocating take-up reel that can be controlled in terms of its speed of rotation depending on the state of filling is avoided, and in particular also at the highest blow - and speeds of the necessarily rotating machine parts, a perfect winding of the rope is achieved and at the same time the dangers of overstressing the rope to be wound up and especially sensitive ropes are eliminated and finally the achievable speeds and speeds can be further increased without the described impairments and also under extreme operating conditions, especially in the event of emergency braking, the described hazards are averted from the rope to be wound up.

This is achieved according to the invention above all in that the take-up reel is driven separately at the nominal speed of rotation and the single-stroke rotor at the speed required to generate the differential speed.

This has the advantage that the take-up spool with its relatively large and in particular variable mass does not have to be subjected to a change in speed. Instead, it is achieved that the single-stroke rotor, which has a practically constant mass and is much easier to design, is driven as a function of the cable conveying speed or the cable pull, the nominal stroke speed and the instantaneous diameter of the take-up spool with the required own speed and for generating the required differential speed in its speed can be regulated and thus adapted to the speed of the take-up reel. The further advantage is achieved that, in contrast to the known systems described, the single-stroke rotor enclosing the take-up reel with its practically constant and relatively small mass and thus constant, smallest possible mass moment of inertia, the heavy and variable inertia take-up reel can be tracked, even with that described rapid braking. The control task of changing the speed of the single-shot rotor is considerably simplified, in particular a so-called guided braking, since no regulation via the variable mass and therefore via the variable mass moment of inertia of the take-up spool is required. It only needs to be decelerated depending on changes in speed and especially when braking, the single-stroke rotor with its much lower and, above all, constant moment of inertia, so that the dangerous overstressing described, in particular sensitive ropes and rope elements, is avoided. All in all, significantly higher speeds and thus the number of impacts can be mastered during the winding process, in particular also in the case of braking.

According to one embodiment of the invention, the speed of the single-lay rotor and thus the differential speed between the take-up spool and the single-lay rotor is regulated depending on the tension of the rope fed to the single-lay rotor in accordance with the winding diameter on the take-up spool. Since the change in the winding diameter on the winding spool leads to a change in the tension of the rope fed to the single-lay rotor, this tension is thus used in a simple manner to determine the required differential speed and thus to the controlled winding operation depending on the winding diameter. At the same time, this regulation ensures the constant maintenance of the rope tension required for the removal of the rope elements.

According to a further embodiment of the invention, the take-up spool is mounted so as to be free-floating in the axial direction, and the single-stroke rotor, which surrounds the take-up spool as a hollow body closed on one side, is mounted so as to be free-floating on its closed side facing away from the take-up spool and is displaceably driven in the axial direction. This has the advantage that the take-up spool and its drive with the nominal stroke speed can be accomplished completely independently of the laying stroke movement and the regulation of the differential speed, while the laying stroke movement takes place on the one hand and the regulation of the difference speed via the single-stroke rotor with its low and, above all, constant mass can. Both the structural and the functional design of the laying stroke movement and the speed control for the single-stroke rotor are therefore considerably simplified. A structural and Functionally particularly advantageous embodiment of the invention is achieved in a further embodiment in that the take-up reel with a hollow drive shaft facing the cable inlet and mounted in a stationary machine part is arranged on the end remote from the cable inlet that the single-stroke rotor is rotatably mounted on its drive shaft in a sliding carriage which is in turn driven to and fro on a stationary machine part, and is rotatably and displaceably mounted on a continuation of its drive shaft in the stationary machine part, and in addition that the cable passes through the hollow drive shaft of the take-up spool to its end facing the single-stroke rotor and from there the longitudinal axis of the single-stroke rotor is guided along it to the take-up reel. This design initially enables the winding reel to be securely and vibration-free supported, but at the same time its particularly favorable position compared to the single-stroke rotor surrounding it. The hollow drive shaft of the take-up reel can be connected in a suitable manner to the required rotary drive or can also be linked to a suitable impact and / or extraction device. The single-lay rotor can then be arranged on the side of this single lay-up and take-up device, which is located from the cable inlet, and in a particularly favorable manner, because it is stored independently of the storage and arrangement of the take-up spool and can both be rotated and thrust-driven. The cable guide described takes this advantageous structural arrangement into account in a particularly expedient manner.

A further embodiment of the invention makes it possible to achieve the highest possible rope speed and quality. For this purpose, in a further embodiment of the invention, the hollow drive shaft of the take-up reel is preceded by a pre-twisting machine with a pre-twist rotor with a driven pull-off disk mounted on a hollow shaft, and the rope emerging from the hollow shaft of the pre-twist rotor is fed to the drive hollow shaft of the take-up reel. Such a pre-twisting machine with a driven take-off disk (e.g. in particular a pre-twist and take-off device according to DE-OS-3 209 169) enables a substantial reduction in the pre-pull or take-off tension in the rope before it reaches the single-lay and winding device according to the invention . This device is thus relieved of the task of the trigger, and in it only the device-related cable tension can be mastered, which considerably simplifies the design of the single-lay and take-up device and enables an extraordinarily high increase in the machine speed, i.e. the number of cable runs, without that increase the total tensile stress occurring in the rope (e.g. due to centrifugal and frictional forces).

The pre-twisting machine and the single beating and winding device according to the invention can be combined in a simple manner in that the hollow shaft of the pre-twist rotor facing the winding reel and the hollow drive shaft of the winding reel are formed in one piece. The pre-twist rotor and the take-up spool are thus rigidly coupled in terms of their speed, that is to say they both execute the nominal take-up speed, in which case the single-take-up take-up device then carries out the necessary generation of the differential speed and the laying stroke movement. The entire stranding machine system can be made compact and with simple drive and control means.

For the guidance of the rope to be wound on the single lay rotor of the single lay and take-up device, it is essential that particularly narrow radii of curvature of the rope are avoided with this rope guide and in particular the transfer of the rope initially guided in the longitudinal direction on the single lay rotor into the cross-sectional plane to the take-up spool even with changing winding diameters without tight curvature radii or even kinks that impair the rope. For this purpose, it has proven to be particularly expedient if, in a further embodiment of the invention, the single-stroke rotor is provided on the outer circumference of its open end with at least one radially outward projection, which on its outward edge has a curved guideway running in a cross-sectional plane for the forms the winding reel to be fed, and the rope, after being guided on the inner surface of the rotor shell, is fed to the beginning of this guideway and runs from the end of the guideway out of the winding reel, the center of the segment of the circle of curvature of the end section of the guideway being arranged such that the common Cut the tangents of the coil core circle and curvature circle segment at the point on the circumference of the single-lay rotor at which the rope leaves the single-lay rotor at the start of winding. This ensures that the rope does not always fall below an admissible radius of curvature and in particular that the inflow of the rope to the take-up spool remains at the end of the guideway even when the winding diameter changes without an impermissible curvature. With the smallest winding diameter, namely the diameter of the coil core circle at the start of the winding process, the rope does not experience any deflection when it leaves the guideway and can rise with increasing winding diameter at receding points on the guideway, so that any additional curvature at the end of the guideway is avoided.

In order to achieve safe guidance of the rope at the open end of the single-lay rotor, the open end of the single-lay rotor on the outer circumference is expediently provided with a Provide a collar that covers the guideway at a radial distance that allows the cable run.

The measures characterized in claim 9 ensure safe and essentially deflection-free guidance of the rope in the longitudinal axis of the take-up reel and single-lay rotor. The rope guide tube always encloses the rope running in the longitudinal axis, since it constantly encloses the rope section created during the laying stroke movement of the single-lay rotor between the end of the take-up spool and the bottom of the single-lay rotor.

In order to reduce and control any vibrations that occur in the drive hollow shaft as a result of the free-floating mounting of the take-up reel, the measures described in claim 10 are expediently followed. The spool mandrel made of the composite material described leads to an extraordinarily high strength with the required still small diameter. The coil mandrel can then be connected to the hollow hollow drive shaft, the bending stiffness of which reduces vibrations or avoids them entirely.

In order to generate the required differential speed between the take-up spool and the single-shot rotor of the single-shot and take-up device on the one hand and the laying stroke to be linked therewith with regard to the back and forth movement of the single-shot rotor, a further embodiment of the invention is particularly advantageous, which is characterized in that for the regulation of the speed of the single-stroke rotor and thus the differential speed, a continuously variable transmission is connected downstream of a drive motor delivering the nominal stroke speed, that the output of this transmission is connected to the drive shaft of the single-stroke rotor in terms of rotary drive, and for the adjustment of the continuously variable transmission, an actual signal corresponding to the actual cable pull when the rope enters the single-stroke rotor generated, compared with a target signal corresponding to the target cable, the comparison signal to a controller and its output signal to the actuator (servomotor) of the transmission and that to regulate the speed of the displacement movement of the sliding carriage for the single-stroke rotor, the nominal stroke speed and the output speed of the continuously variable transmission, after reversing the direction of rotation of one of these rotations, in each case a sun wheel of a planetary gear train designed as a coaxial bevel gear planetary gear with external teeth of the two sun wheels and the Output speed of the web of the planetary gear, possibly with a suitable translation, is given to the input of a laying lifting gear for the sliding carriage.

It is thus possible, depending on the tensile stress of the rope fed to the single lay rotor and thus depending on the winding diameter on the take-up reel, to link the differential speed between the take-up reel and the single lay rotor as well as the speed of the sliding movement of the sliding carriage and thus the laying stroke, namely always optimally regulated in order to achieve a perfect laying of the rope on the take-up spool without exceeding the permissible cable tension. This is achieved using simple and robust means derived from the speeds of a single drive motor.

As already described at the beginning, the braking of the stranding machine system and in particular the emergency braking in the event of a wire break represent a particular problem. With the aid of the stranding machine system according to the invention in the described upstream connection of a pre-twisting machine, braking can be achieved in a particularly advantageous manner according to the invention in that Braking of the system, in particular in the event of a wire break in the rope elements, the nominal impact speed of the pre-twist rotor and thus the take-up spool kept constant in a predetermined total braking time during a first predetermined braking time segment, but the drive speed of the take-off disk and thus the lay length and conveying speed of the rope to a predetermined minimum be reduced and that during this and / or after the end of this first braking period, the complete braking of the other machine parts (take-off disk, pre-twist rotor, wind-up oil spool and single-stroke rotor) and is carried out within the remaining second braking period. This ensures that the emergency braking does not have to be carried out with immediate and permanent brief braking of all machine parts involved with their high moments of inertia. Rather, the conveying speed of the rope is first reduced as much as possible by reducing the lay length, so that if the speed of the take-up spool is initially the same, a smaller rope section must be wound up with a correspondingly reduced winding speed and only then is the actual braking process carried out, with the other machine parts being braked. The total rope length that arises during the braking process can be reduced to a minimum in this way. A major advantage is that during the braking process, the control of the winding process does not have to take place via the winding spool with its particularly high mass moment of inertia, but instead the other machine parts and in particular the single-stroke rotor with its much lower and, above all, constant mass moment of inertia must be influenced in a regulating manner. Another cheap way of Braking with these advantages consists in a braking operation after a predetermined deceleration curve in each case via a process computer with specification of the braking time, that is to say regulation with a constant deceleration value.

In the description above and in the description below, the expression “nominal speed of rotation” always means the speed corresponding to the nominal number of cycles of the rope to be produced.

• Fig. 1 eine teilweise geschnittene Seitenansicht einer Ausführungsform des Verseilmaschinensystems nach der Erfindung mit der Einfachschlag-und Aufwickelvorrichtung und einer dieser vorgeschalteten Vorverdrallmaschine mit angetriebener Abzugscheibe,
• Fig. 2 eine teilweise geschnittene Teilansicht in Draufsicht des offenen Teils des Einfachschlagrotors der Einfachschlag- und Aufwickelvorrichtung,
• Fig. 3 in rein schematischer schaubildlicher Darstellung einen Einfachschlagrotor der Einfachschlag- und Aufwickelvorrichtung mit Seilführung,
• Fig. 4 eine schematische Ansicht des offenen Endes des Einfachschlagrotors nach Fig. 2 und
• Fig. 3 zur Demonstration der geometrischen Verhältnisse,
• Fig. 5 eine geschnittene Teilansicht der Aufwickelspule mit ihrer Antriebshohlwelle und des zugehörigen Einfachschlagrotors der Einfachschlag- und Aufwickelvorrichtung in einer besonderen Ausfühungsform.

Features, further advantages and details of the invention result from the following description of exemplary embodiments of the invention with reference to the drawing. To simplify the illustration, the drawing is largely schematic and contains only those parts of the stranding machine system that are required to explain the invention. Show it:

• 1 is a partially sectioned side view of an embodiment of the stranding machine system according to the invention with the single lay and winding device and a pre-twisting machine with a driven take-off disk connected upstream thereof.
• 2 is a partially sectioned top view of the open portion of the single lay rotor of the single lay and winder;
• 3 in a purely schematic diagrammatic representation a single-stroke rotor of the single-stroke and winding device with a rope guide,
• Fig. 4 is a schematic view of the open end of the single-stroke rotor according to Fig. 2 and
• 3 to demonstrate the geometric relationships,
• Fig. 5 is a sectional partial view of the take-up reel with its hollow drive shaft and the associated single-shot rotor of the single-shot and take-up device in a special embodiment.

The principle of the stranding machine system according to the invention is explained on the basis of the special embodiment according to FIG. 1. In the stranding machine system, the single twist and winding device, generally designated ESW, is preceded by a pre-twisting machine, generally designated VVA. As will be described in detail below, the pre-twist rotor and the hollow drive shaft of the take-up spool are rigidly coupled to one another in that they are formed in one piece. However, it is already stated at this point that the single lay and take-up device reaching as far as the drive hollow shaft of the take-up reel can be regarded as a complete stranding machine system in the form of a single lay machine with a take-up system, in which, in a further embodiment, a pre-twisting machine can also be separately connected by linking the respective drives the principle shown in Fig. 1.

The pre-twisting machine designated with VVA in FIG. 1 is expediently designed as described in DE-PS-3 209 169, possibly additionally according to DE-OS-3 226 572. The entire stranding machine system according to FIG. 1 is on one common machine frame 1 arranged. The rope manufactured and guided in the stranding machine system is generally designated by 3. The pre-twisting machine has a pre-twisting rotor 2, in which the driven pulley 4 wrapped and driven by the cable 3 is mounted, as is shown and described in detail in DE-PS-3 209 169. To simplify the illustration, a single-disc deduction is shown schematically here. The pre-twist rotor 2 has a hollow drive shaft 6 and is rotatably supported on both sides at 6a and 6b. In the embodiment shown in FIG. 1, the hollow drive shaft 6 of the pre-twist rotor 2 is extended beyond the roller bearing 6b in the cable conveying direction, running from left to right in FIG. 1. On this extension of the hollow drive shaft 6, a take-up spool 5 is arranged to be exposed in a manner to be described. The take-up reel 5 is thus connected in one piece to the pre-twist rotor 2 via the hollow drive shaft 6 and is therefore always driven at the same speed, namely at the nominal impact speed.

Due to the hollow drive shaft 6 of the pre-twisting machine VVA, the rope 3 is now guided to the single lay and take-up device, which is described in the following for the sake of simplicity in terms of structure and function, which is generally referred to as ESW. Conceptually, the take-up reel 5 itself is to be regarded as a component of the single-lay and take-up device, as will be explained below.

As already explained, the take-up reel 5 is driven together with the pre-twist rotor 2 with the same, namely with the nominal speed of rotation. The rotary drive for the pre-twist rotor 2 and the winding spool 5, which is always rotating at the same speed and in the same direction, and the rotary drive for the take-off disk 4 within the pre-twist rotor 2, i.e. according to DE-PS-3 209 169, for the associated, only schematically illustrated planetary gear with its drive disk 8 of the pre-twisting machine VVA as well as the rotary drive for the single-shot rotor 7 of the single-shot and winding device ESW is derived from a common drive motor 9 in constant coupling by mechanical positive drive. For this purpose, the drive motor 9 drives a drive pulley 11 via a shaft 10, which, for. B. via a drive belt 12 drives a drive pulley 13 for the hollow drive shaft 6 and thus for the pre-twist rotor 2 and for the take-up spool 5. The drive system is also via an adjustable gear 14 via the drive shaft 15 and the drive pulley 16 with the drive belt 17 and the drive pulley 8 for the trigger plate 4 in the pre-twist rotor 2 coupled to the shaft 10 of the drive motor 9.

A continuously variable transmission 19 is driven in rotation via a further output shaft 18 of the drive motor 9. This gear 19 is via a suitable actuator, for. B. an electric actuator y, remotely adjustable. Via its output shaft 20 and the pulley 21 as well as the belt 22 and the drive pulley 23, the drive shaft, generally designated 24, for the rotary drive of the single-stroke rotor 7 is coupled. The drive shaft 24 is designed in a manner known per se as a two-part shaft which, when the rotary drive is transmitted, allows the two parts to move axially against one another, for. B. using a torque-transmitting, rigidly connected to the drive pulley 23 bushing with endless ball circulation, a so-called. Torque ball bushing with profile shaft.

At the beginning of the stranding, the transmission ratio and thus the speed ratio between the speed for the take-off disk 4 and the speed of the pre-twist rotor 2 are determined on the adjustable transmission 14, and thus the length of cable run to be generated by the pre-twist machine VVA is determined.

As already explained in principle, the single-lay rotor 7 of the single-lay and take-up device ESW must be dependent on the cable conveying speed and on the speed of the pre-twist rotor 2 and thus at the same time the take-up spool 5 and depending on the take-up diameter reached on the take-up spool 5 with a suitable differential speed of the take-up spool 5 pursue ahead or appropriate. Starting with a differential speed when the take-up reel 5 is empty with the aid of a basic setting of the continuously variable adjustment gear 19, the transmission ratio on the continuously variable adjustment gear 19 must continuously change in an automatically controlled manner until the full winding of the take-up reel 5 is reached.

As has already been described at the beginning, the cable 3 is guided through the hollow drive shaft 6 of the pre-twist rotor 2 and the take-up spool 5 from the longitudinal axis of the single-stroke rotor 7 along this to the take-up spool 5, as schematically shown in FIG. 1.

According to the invention, the described regulated change in the transmission ratio on the adjusting gear 19 for changing the differential speed between the single-stroke rotor 7 and the take-up spool 5 takes place depending on the winding condition in the embodiment according to FIG. 1 in the following way: So that the rope 3 does not slide on the take-off disk 4, it must can be tensioned according to the well-known Euler's rope wrap formula with a minimum tensile load after leaving the trigger disk 4. Depending on the tensile load in the rope at the deflection point of the rope when entering the single-lay rotor 7, the single-lay rotor 7 is axially loaded with its shaft 24. Via an axial roller bearing 25, with which the outer part of the drive shaft 24 is mounted in the carriage 39, which will be described below. then presses the single-stroke rotor 7 more or less onto a pressure measuring device of known design, e.g. B. A so-called force transducer 26. The actual cable tension measured there as a measured pressure value is compared in a controller 27 with a nominal cable tension which is specified via a potentiometer 28 set before the start of the stranding. If the differential speed of the single-shot rotor 7 is too great compared to the take-up reel 5, the actual cable pull in the area of the single-shot rotor 7 increases as a result. The pressure on the pressure measuring device 26 then also rises. The controller 27 then acts overlapping the actuator y. The gear ratio is corrected there via the gearbox 19 until the differential speed between the single-shot rotor 7 and the take-up reel 5 is appropriately reduced. In the event of an impermissible decrease in the actual cable pull in cable 3, conversely, the differential speed is increased via the described device until the compensation is reached again.

The speed of the single-lay rotor 7 and thus the differential speed between the single-lay rotor 7 and the take-up spool 5 is thus regulated as a function of the tension of the rope 3 fed to the single-lay rotor 7 in accordance with the winding diameter on the take-up spool 5.

For winding the rope, the axial reciprocating movement of the single-lay rotor 7, which has already been described in principle, must also be carried out. This so-called laying stroke drive of the single-stroke rotor 7 is carried out according to the invention in the following way:

Decisive for the laying stroke speed are the true winding speed, ie the difference in speed, the rope conveying speed as well as the laying step width that has to be adjusted according to the rope strength or rope diameter before the start of production. In the exemplary embodiment according to FIG. 1, the control and regulation of the laying stroke required here for explanation is explained as a function of the differential speed described. On an output gear 29 rotating with the input speed of the drive shaft 18 of the transmission 19 and from the already described shaft 20 via a pulley 30, on the one hand the nominal impact speed with which the take-up reel 5 rotates and on the other hand the speed of the single-stroke rotor 7. The direction of rotation of the gear 29 is reversed by the counter gear 31 meshing with it. The rotation of the pulley 30 is transmitted to the pulley 33 via the drive belt 32 and is therefore retained. At the drive wheels or disks 31 and 33 are associated shafts in the manner shown schematically in Fig. 1, each with a sun gear as a coaxial bevel gear planetary gear with external teeth of the two Sun gears trained planetary gear connected. In a manner known per se, the sun gears are rotationally connected at the same time to the planet gear web surrounding them. The web in turn is firmly connected to the driven wheel 34. The speed of the web of the planetary gear transmission is thus transmitted via a drive belt 35 to an associated drive pulley 36. The drive disk 36 drives, via a schematically illustrated reversing gear 37 to be designed in a suitable manner, and a laying lifting spindle 38, an axially displaceable sliding carriage 39 which, according to FIG. 1, carries the bearing box for the single-stroke rotor 7 with its rotary drive shaft 24 of the single-stroke and winding device ESW.

In order to be able to continuously adjust the laying stroke and the laying stroke speed, it can be expedient to use a rolling ring gear known per se for traversing movements instead of the reversing gear shown.

As already stated above, the embodiment according to FIG. 1 represents a stranding machine system in an embodiment in which a pre-twisting machine is coupled with a single-lay and winding device according to the invention. Other embodiments in deviation from FIG. 1 are possible. First of all, it is possible to store and drive the single-stroke rotor 2 with its take-off disk 4 on the one hand and the take-up reel 5 with its associated hollow drive shaft separately, that is to say, in contrast to FIG. 1, to “separate” the drive shaft 6 and to store the two remaining machine sections accordingly. The hollow drive shaft of the take-up reel 5 is expediently mounted twice over a greater length and the hollow drive shaft is given an enlarged diameter in order to avoid vibrations.

A further embodiment consists in that a pre-twisting machine according to FIG. 1 is completely dispensed with and the single beating and winding device according to the invention is designed and used as an independent single beating machine with a winding device. Here, the take-up reel 5 with its hollow drive shaft "6" is also mounted on its own machine frame within the overall frame 1, again expediently on a longer hollow drive shaft and a double bearing at a greater distance with an enlarged shaft diameter. In terms of the construction principle, the stranding machine system shown in FIG. 1 would in principle end at the dividing line L shown in broken lines. Such a system represents a complete single-beating machine with a winding device, which can be operated either alone or with other upstream systems.

2 to 4 schematically show an embodiment of the single-stroke rotor 7 which is particularly expedient both for reasons of strength and in particular for reasons of optimal rope guidance.

As shown schematically in FIG. 1 and, as is shown schematically in particular in FIG. 3, the single-shot rotor 7 of the single-shot and winding device ESW is designed as a hollow body enclosing the winding spool on one side and closed. The cable 3 is, as described, guided through the hollow drive shaft 6 of the take-up reel 5 to its end facing the single-lay rotor and from there along the longitudinal axis of the single-lay rotor 7 to the take-up reel 5. It is necessary to convert the rope from its longitudinal guide into a circumferential or tangential course in order to then be able to feed it to the take-up reel 5. The guidance on the body of the single-stroke rotor 7 takes place in a suitable manner, for. B. by ceramic tubes, slideways, hollow spigot or the like. The basic cable guide is shown in particular in FIG. 3.

According to the invention, the single-stroke rotor 7 is now provided on the outer circumference of its open end with at least one radially outwardly directed projection 40, which on its outwardly directed edge forms a curved guide track running in a cross-sectional plane for the cable 3 to be supplied to the take-up reel 5, as shown in FIG. 2 to 4 show. The rope 3 is thus fed to the beginning of this guideway 40 after it has been guided on the inner surface of the jacket of the single-stroke rotor 7 and runs from the end of the guideway 40 out of the take-up reel 5.

For a perfect rope guide, it is now extremely useful not to fall below the smallest possible radius of curvature at any point. This becomes critical at the point where the rope leaves the guideway of the projection 40 in order to run tangentially to the take-up reel 5. Because with this guidance different cable runs at the end of the guideway 40 must be taken into account on the one hand when the bobbin core is empty and on the other hand when the bobbin is full. 4 shows the geometrical relationships for explanation, and the further embodiment of the invention is to be demonstrated in this way:

In order to avoid any inadmissibly tight rope curvature and in particular a rope kink when leaving the guideway 40, the center M of the circle of curvature segment of the end section 40a of the guideway 40 is arranged according to the invention such that the common tangent 41 of the coil core circle 5a and the circle of curvature segment 40a is at the point T of Cut the circumference of the single-lay rotor 7 on which the rope 3 leaves the single-lay rotor 7 at the start of winding. These geometric relationships are shown schematically in FIG. 4, with both extreme positions of the cable guide on the take-up spool 5 being shown schematically, likewise in FIG. 3. FIG. 3 shows furthermore, to compensate for the imbalance produced by the projection 40, a diametrically opposite second projection, which, however, is not required for the function.

As further shown in FIG. 2, the open end of the single-stroke rotor 7 is provided on the outer circumference with a collar 42 which covers the guideway 40 at a radial distance which permits the cable run.

Fig. 5 shows a sectional partial view of a special embodiment of the single lay and take-up device to avoid disadvantageous rope vibrations in the rope run between take-up spool 5 and single lay rotor 7 and thus for an exact rope guide. As shown in FIG. 5, the single-stroke rotor 7 is provided on its closed bottom surface 7a with a cable guide tube 43, which runs coaxially with the hollow drive shaft 6 and is directed towards the take-up spool 5, which has a smaller outer diameter than the inner diameter of the hollow drive shaft 6 and through which the cable 3 comes out Hollow drive shaft 6 is guided to the single impact rotor 7. As further shown in FIG. 5, the take-up spool 5 is arranged on a hollow spool mandrel 44 made of a fiber-reinforced, in particular carbon-fiber-reinforced, composite material with a high modulus of elasticity, which is firmly connected to the hollow steel drive shaft 6, the hollow drive shaft 6 opposite one Outer diameter of the coil mandrel 44 has a substantially larger outer diameter in order to achieve a high stability against vibrations.

Claims (12)

1. Cable stranding machine system with a single- turn and winding device for the cable, in which a winding reel (5) and a single-turn rotor (7) which runs around and encircles the winding reel are arranged coaxially, wherein the winding reel and the single-turn rotor are movable back and forth axially relative to each other in order to produce a laying stroke for the cable, wherein the cable is fed from the longitudinal axis of the single-turn rotor along the latter to the winding reel, and wherein a difference in the speed of rotation of the winding reel and of the single-turn rotor arises during winding in dependence upon the particular winding diameter which has been reached on the winding reel, characterised in that the winding reel (5) is rotationally driven at the nominal speed of rotation and the single-turn rotor (7) is rotationally driven separately at the speed of rotation necessary to create the difference in the speeds of rotation.

2. Cable stranding machine system according to claim 1, characterised in that the speed of rotation of the single-turn rotor (7), and consequently the difference in the speeds of rotation, is controlled in dependence upon the tension of the cable being fed to the single-turn rotor in conformity with the wound diameter on the winding reel (5).

3. Cable stranding machine system according to claim 1 or 2, characterised in that the winding reel (5) is mounted in a free-floating manner but is not axially displaceable and the single-turn rotor (7) which encircles the winding reel (5) and which is formed as a hollow body closed at one end is mounted to be free-floating at its closed end remote from the winding reel (5) and is mounted to be driven displaceably back and forth in the axial direction.

4. Cable stranding machine system according to claim 3, characterised in that the winding reel (5) is provided with a hollow drive shaft (6) which receives the cable supply and is mounted on a stationary machine part, the reel being located at the end of the drive shaft from which the cable supply discharges, wherein the single-turn rotor (7) is rotatably mounted on its drive shaft (24) on a travelling carriage (39) which for its part is driven (37, 38) movably back and forth on a stationary machine part and is rotatably and displaceably mounted by an extension of its drive shaft (24) on the stationary machine part, and wherein the cable (3) is fed through the hollow drive shaft (6) of the winding reel (5) to the end of the reel adjacent to the single-turn rotor (7) and from there is fed from the longitudinal axis of the single-turn rotor (7) along the latter to the winding reel.

5. Cable stranding machine system according to claim 4, characterised in that a pre-twisting machine (VVA) which comprises a pre-twisting rotor (2) mounted on a hollow shaft and with a driven delivery pulley (4) is located coaxially in advance of the hollow drive shaft (6) of the winding reel (5), and the cable (3) coming from the hollow shaft of the pre-twisting rotor (2) is fed to the hollow drive shaft (6) of the winding reel (5).

6. Cable stranding machine system according to claim 5, characterised in that the hollow shaft (6) of the pre-twisting rotor (2) facing towards the winding reel (5) is formed as one piece with the hollow drive shaft.

7. Cable stranding machine system according to one of claims 1 to 6, characterised in that the single-turn rotor (7) is provided at the outer periphery of its open end with at least one radially outwardly directed protuberance (40) whose outwardly facing edge forms a curved guide path extending in a cross-sectional plane of the rotor for the cable to be fed to the winding reel (5), and the cable, after its guidance on the internal surface of the rotor sleeve, is fed to the start of this guide path (40) and from the end of the guide path is fed to the winding reel (5), wherein the centre-point (M) of the part-circular segment (40a) of the end section of the guide path (40) is such that the common tangents (41) from the circular reel core (5a) to the part-circular segment (40a) cut the periphery of the single-turn rotor (7) at the points (T) at which the cable leaves the single-turn rotor at the beginning of the winding operation.

8. Cable stranding machine system according to claim 7, characterised in that the open end of the single-turn rotor (7) is provided at the outer periphery with a collar (42) which encloses the guide path at a radial spacing which permits passage of the cable.

9. Cable stranding machine system according to claim 7 or 8, characterised in that the single-turn rotor (7) is provided at its closed base surface (7a) with a cable guide tube (43) which is directed towards the winding reel (5) and which extends coaxially in relation to the hollow drive shaft (6), said cable guide tube having a smaller external diameter than the internal diameter of the hollow drive shaft (6) and through which the cable (3) is guided from the hollow drive shaft (6) to the single-turn rotor (7).

10. Cable stranding machine system according to one of claims 4 to 9, characterised in that the winding reel (5) is arranged on a hollow reel spigot (44) of a fibre-reinforced, particularly carbon-fibre reinforced, compound material with high modulus of elasticity which is rigidly connected to the hollow drive shaft (6) which is of steel, wherein the hollow drive shaft has a substantially larger outer diameter than the outer diameter of the reel spigot (44).

11. Cable stranding machine system according to one of claims 1 to 10, characterised in that, for the control of the speed of rotation of the single-turn rotor(7) and consequently of the difference in the speeds of rotation, a steplessly adjustable gear system (19) is connected to follow a drive motor (9) which delivers the nominal speed of rotation, in that the output (20, 21) of this gear system (19) is connected in a rotary driving manner with the drive shaft (24) of the single-turn rotor and, for the adjustment of the steplessly adjustable gear system (19), produces an actual signal corresponding to the actual cable tension at the entry of the cable into the single-turn rotor (7), said actual signal being compared with a desired signal corresponding to the desired cable tension, and the comparison signal being fed to a controller (27) with its output signal being fed to the setting member (setting motor y) of the gear system (19), and in that in order to control the speed of the displacement movement of the displaceable carriage (39) of the single-turn rotor (7) the nominal speed of rotation (via 29) and the output speed of rotation (via 20, 21) of the steplessly adjustable gear system (19), after reversal of the direction of rotation of one of these rotary motions, are fed to respective sun wheels of a planetary gear system (31, 33, 34) formed as a coaxial bevel-epicyclic-type reduction gear with external toothing of the two sun wheels, and the output speed of rotation (via 34) of the link of the planetary gear system, possibly with suitable reduction, is transferred to the input of a laying stroke gear system (37) for the displaceable carriage (39).

12. Cable stranding machine system according to claim 5 or one of claims 6 to 11, characterised in that in order to brake the system, particularly in the case of a wire fracture in the cable elements, the nominal speed of rotation of the pre-twisting rotor (2) and thus of the winding reel (5) is held constant during a first predetermined braking period of a predetermined total braking time, but with the driving speed of rotation of the drive pulley (4) and consequently the laying length and feed speed of the cable being reduced to a predetermined smallest possible value, and in that during this and/or after the completion of this first braking period the complete braking of the rest of the machine parts (delivery pulley 4, pre-twisting rotor 2, winding reel 5 and single-turn rotor 7) is initiated and is completed within the remaining, second braking period.

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