DE1048305B - Winding drum, the braking effect of which is regulated by the weight of the drum, in particular for rope-like winding material for electrical cables - Google Patents

Description

The invention relates to winding trunks, in particular for rope-shaped winding material for electrical Cables, such as wires and other stranding elements, for the production of twisted wire groups of telecommunication cables. The invention is concerned with the problem of the strand-shaped winding material with a certain and as constant tension as possible to wind up or unwind from the drum. .

In order to achieve a constant tensile stress in the strand-like winding material to be wound up or unwound, it is already known to provide additional braking elements which perform braking as a function of the respective diameter or radius of the winding supply located on the drum. But the effect of such · / .. example by means of adjustable springs working brake bodies can be kept constant difficulty with time.

It is already known the weight of the drum including the winding material for its Take advantage of braking. So it is with central spinners for helical application of insulating elements, such as cords or paper tapes, known on cores of telecommunication cables (German Patetitschrift 503 928) to use the weight of the supply reels for braking. A related embodiment of a cord spinner is the cord spool to rest on a driven and rotating funnel-shaped grating plate, so that the Coil constantly only with its circumference, i. H. with the circular lower edge of the winding body the funnel wall rests. As a result, the cord reel is only braked by its weight. If necessary, an additional "weight" can be placed on the cord reel to increase the braking force will. In the context of this proposal, it is also known in a central paper tape spinner for Telephone cores the paper tape reel on a rotating disc (paper plate) with a rubber plate on top to arrange and the paper tape from the tape reel in the opposite direction to Drchrichtuiig pull off the disc and wrap it around the conductor after deflection. In these known methods the tension generated in the strand-shaped winding material is a function of the weight of the coil, changes during operation. A fundamental disadvantage of this spinner is that the radius of application of the brake changes during the unwinding process and thus the size of the braking surface changes.

According to another known proposal (German Patent 662 693) is in a brake for a Discharge drum for cable cores the weight of the wire drums which changes with the unwinding of the cores used to regulate the braking. In the case of a winding drum, its braking effect

is regulated by the drum weight, especially for rope-shaped winding material

for electrical cables

Applicant:

Siemens-Schuckertwerke

Corporation,

Berlin and Erlangen,

Erlangen, Wemer- \ ^r on-Siemens-Str. 50

Dipl.-Ing. Wilhelm Wirth,

Fritz Wilke, Berlin-Siemensstadt,

and Herbert Menke, Berlin-Spandau,

have been named as inventors

With this arrangement the brake disks of the vein drums should run on brake blocks, and it should The weight of the core drum must be equal to the weight of the maximum amount of cores to be applied under the assumption that that the radius when the drum is fully wound is about twice as large as the radius of the contact surface with empty drum. This known arrangement is intended for such vein drums, where the drum axis is horizontal, and as such it has several disadvantages This is how the hollowed-out braking surface of the brake pad, on which the brake disc of the horizontal arranged drum wave is stronger at the edges than at the deepest during operation Place worn out, whereby the specific brake pressure changes over time, resulting in an uneven brake Running of the drum and a change in the braking effect. Furthermore, when replacing the drum, which is cumbersome, soiling of the braking surfaces can easily occur. In addition there is also the size of the angle between the direction of travel of the vein and that through the drum axis laid horizontal plane influences the tensile stress. The given rule, the vein drum weight to equalize the weight of the winding material, only applies in the case that the radius of the core

rates with a fully wound drum is twice as large ■ as the corresponding radius with an empty drum. To avoid these disadvantages, a

"Winding drum, the braking effect of which is regulated by the drum weight, especially for Stranded winding material for electrical cables, with • the drum shaft with the drum firmly seated on it

'Is arranged perpendicular or inclined to the perpendicular, according to the invention between the lower end face a horizontal braking surface or a braking surface inclined to the horizontal is arranged on the drum and the supporting surface, which is so effective that when winding or unwinding the winding material with a constant The radius of attack of the braking surface and keeping the braking surface constant, the specific braking pressure changes automatically so that the tension in the winding material remains constant. Such a winding drum is -In principle, it can be used both as a discharge drum and as a take-up drum.

Figs. 1 and -2 show in side view and in

"Top view first of all a winding drum according to the ■ invention in principle.

Thereafter, the winding drum 10 with the winding 12 is pushed onto the vertical shaft 11 and fixed thereon. Between the drum and the base plate 14 is the horizontally lying brake with the brake rings 13 and 13 ', the brake ring 13 opposite the drum by driving pins 15 and the brake ring 13' opposite the base plate 14 by screws 15 '(or driving pins) in the Direction of rotation is determined. Instead of coupling the drum to the brake ring 13 by pins or other drivers, however, the drum shaft 11 is expediently connected to the brake ring 13. As indicated in the figures, r "is the radius of the fully wound drum and thus the radius of attack of the strand in the outermost winding layer. Furthermore, r _{t is} the radius of the empty drum, ie the radius of action of the strand in the innermost winding layer.

In order to determine the factors influencing the tensile stress in the strand-like winding material and to obtain more detailed dimensioning rules for the winding drum, a pay-off drum is considered below, from which a core is to be withdrawn at a constant withdrawal speed ν from the beginning to the end of the unwinding process. During this unwinding process, the following varying factors A, B and C occur:

Factor A: The attack radius r of the outgoing wire decreases, in this case at the beginning equal to the radius r _{a of} the outermost winding layer and at the end equal to the radius r _; the innermost winding layer.

Factor B: The running speed (angular speed or speed / min.) Of the discharge drum increases, namely the running speed

n _a - at the beginning, w "= at the end,

d _a π di τι

if d _a = 2r _{a is} the diameter of the outermost and d; - Ir _{1 is} the diameter of the innermost winding layer.

Factor C: The weight includes:

1. the weight G _{1 of} the empty drum,

2. the weight G _n , of the shaft including the upper brake ring,

3. The weight G _{wi of} the winding on the drum, where the weight of the drum including the weight of the shaft and weight of the winding shall be referred to as the gross weight of the drum and the weight of the empty drum including the weight of the shaft shall be referred to as the tare weight of the drum. At the beginning or at the beginning of the settlement process the total or maximum gross weight G _B and at the end of the settlement process the tare weight G _{c is} effective. The factor A causes the tensile stress to increase in the ratio of the reciprocal radii r " and?" / The factor C causes the tensile stress to decrease in the ratio of the weights G _a and G _e .

The factor B is to be regarded as negligible, since the coefficient of friction of the brake disks is in the speed range of interest is independent of speed.

In order to obtain the same core tension at the end of the unwinding process, ie in the innermost winding layer, as at the beginning of the unwinding process, ie in the outermost winding layer, according to the invention the attack radii r ₁ and T 1 and the weight values G _a and G _{e are} superimposed on one another matched that relationship

T ₀ Ir ₁ - G _a : G _e

at least approximately applies.

The wire tension P, which should remain constant while the wire is running, is proportional to the gross weight of the drum, the radius rjg. at which the braking effect acts (ie the mean radius of the brake ring), and the coefficient of friction μ and inversely proportional to the attack radius r _a or Tj of the wire, so that at the beginning and at the end of the unwinding process, the following relationships for the wire tension P. result:

ρ ^ 2 ^ ± _{at the} beginning and P = £ i »! * - at the end.

Since on the one hand from

^ - = ^ L gives the ratio - ^ = A

U Ge ? i 'α

and on the other hand the tensile force P is the same at the beginning and the end of the development process, so. the mean braking radius is obtained from the above equation

, = JlL ·. ₌ ^Pr * ^r * μ G. ~ [iG _e '

This value for the mean braking radius of the brake ring must be at least approximately fulfilled.

The application of the specified rules within the scope of the invention is illustrated in the following example explained using a storage drum made of wood:

Be it

G _t = weight of the drum 2.5 leg

G _w = weight of the shaft 1.0 kg

G \ vi - weight of the vein wrap 6.5 kg

r _a = radius of the outermost winding layer 115 mm T ₁ - radius of the innermost winding layer 50 mm

r _B = mean brake ring radius 35 mm

. The values for r _a and r, - result in a radius ratio of

> _ ^ i ¹ JL = 2.3.- , 50

The relationship

C.

would, however, with the specified values

2.5-1-1.0 + 0.5
2.5 + 1.0

= 2.85

be. The calculation shows that the drum or the shaft would have to be loaded with an additional weight of 1.5 kg in order to obtain the desired value of 2.3 for the weight ratio. The tensile stress P results in a value of 350 g.

Since the withdrawal speed is constant, the gross weight increases linearly with time away. The unwinding radius, however, decreases more slowly at the beginning than at the end; so he takes off after one Curve that has an increasingly downward trend. It follows that the tensile stress value is at the beginning increases slightly in order to reach the starting value of 350 g again towards the end of the unwinding process. However, this deviation is of minor importance for the purposes according to the invention and can be neglected.

Likewise, the heating of the brake discs that occurs can be neglected because the too destructive braking energy is at 50 m / min. Take-off speed only around 0.3 mkg / sec., That is 3 watts or 0.72 cal / sec.

In certain cases, arrangements can be useful in which the axis of the winding drum is also arranged inclined to the vertical. This arrangement is shown in Fig. 3, after which two drums 10 and 10 'with their shafts 11 and 11' are inclined relative to the vertical plane, so that the .Brake disks 13 and 13 'of the two drums on surfaces of the inclined to the horizontal plane Foundation 14 rest. The angle of inclination between the drum shafts and the vertical is denoted by α. Such an arrangement can, as indicated, for example for the supply drums of the cores 16 of a pair 17 to be twisted for. Telecommunication cables come into question, on the one hand for structural reasons, on the other hand to achieve lower braking values. In this case, the braking values decrease with the sine of the angle of inclination α, so that only part of the weight of the drum acts as a pressure against the braking surface. The angle between the drum shafts and the vertical can be adjustable, for the drum shafts individually or together.

As already stated, the upper brake ring is expediently connected to the drum shaft. It then only needs the storage drum attached to the vertical shaft and firmly connected to it and it is a solution and disclosure of the brake when changing the drum not mandatory. The brake rings are advantageously made of such a material and designed in such a way that that the lowest possible coefficient of friction is created. Experiments have shown that the Manufacture of the brake rings from porous sintered metal, preferably sintered iron, especially with oil impregnation is appropriate. A coefficient of friction of 0.1 and below is then obtained. Are with advantage also brake rings made of a non-porous metal obtained by powder metallurgy, e.g. B. made of copper and Iron powder, usable, containing the lubricant in the form of colloidal graphite. Furthermore, The aim is to have the shaft supported as smoothly as possible. .

In Fig. 4, a further embodiment of a winding drum with weight is clarified. In accordance with FIGS. 1 and 2, the winding forrimel is with 1Ö and the drum axis with 11 designated. The drum is on the wilt between the centering cone provided on the shaft 18 and the centering cone 18 'of the fastening nut

ίο 19 stuck. This type of fastening has the advantage that there are differences in the bore diameters the Tronimel flange bushings have no effect on the firm mounting of the drum. The lower one is cone-shaped formed end 20 of the shaft is mounted in a journal bearing. This consists of the bearing housing or bearing pot 21 with the needle bearing 22, the lower bearing ring 22 on a pressure ball positionf 23 rests in order to ensure an almost smooth rotation of the pin and thus the drum.

so between the lower end of the pin 20 and the ball bearing remains, as indicated, a small distance. With the shaft of the upper ring flange 24 is connected to which the upper brake ring 13 by means of Studs 15 is attached. The lower brake ring 13 ′ is on the annular flange 21 ′ of the bearing pot 21 fastened by means of studs 15 '. The Ringnärtsch 21 'also serves to fasten the entire Arrangement - on the base plate 14 of the machine by means of the fastening screws 25.

The ring 26 forms a closed, tight annular space for receiving the two brake rings, so that this space with a lubricating liquid, for. B. be filled with a special oil mixture can. In the example shown, the ring 26 is made so wide that the brake rings including of the needle bearing 22 can run in 01. The brake disks 13 and 13 'can instead of a porous Sintered metal also consist of hardened steel, the friction surfaces of which are polished to a high gloss. To the

.40 To continue to secure brake rings against contamination, the ring flange 24 with the downwards inclined collar 24 'provided. This still has a 22 "approach to the ring flange by means of several, preferably to hold three lugs 27 and screws 28 distributed around the circumference on the base plate 14, when the drum 10 is withdrawn from the shaft 11 upwards. The use of special replaceable brake rings 13 and 13 'has the advantage that they can be used to achieve other braking

So conditions can be exchanged. But it is also possible to have the braking surfaces through the underside of the annular flange 24 "and through the top of the annular flange 21 '. The entire assembly requires an exact perpendicular position of the drum axis to the braking surfaces. Any minor discrepancies to compensate for this, can between the brake rings and the annular flange 24 or the Annular flange 21 'resilient means, e.g. B. a resilient oil-resistant rubber layer can be arranged.

The arrangement can also be used in the event that strand-shaped winding material is wound onto the drum be made so that one drives the bearing pot in deviation from FIG. 4 and the weight of the The drum is used to prevent slippage between the bearing pot and the drum during winding obtained and thus to keep the winding tension constant during the winding process without a special drive or a tension control device would be required. A related one Embodiment is shown in Fig. 5, in which

the parts that correspond to FIG. 4 are provided with the same reference numerals. Different 4, a pulley 29 is firmly attached to the bearing pot 21 in order to drive it. The bearing pot 21 is rotatably supported in a bushing 30 which is inserted into the annular disk attached to the base plate 14 3Ϊ is inserted. Furthermore, in contrast to FIG. 4, the ring 26 with the ring flange 21 ' and the bearing pot 21 made in one piece. The speed of the bearing pot can be controlled by the drive be chosen so that a suitable size slip between the built-in brake rings the bearing pot and the drum 10, which is firmly seated on the shaft 11, occurs. Instead of the pulley 29 other drive organs can also occur.

An improved design for driving a take-up drum is shown in FIG. After that the .Antrieb for the winding drum is installed between the base plate 14 and the brake rings. Of the. Drive takes place by means of the rope 32 via the pulley 33, which is held against the bearing pot by the Needle bearing 34 and down through the ball bearing 35 is supported. The ball bearing 35 is annular Recesses in the pulley 33 and the bearing plate 36, which in turn are attached to the base plate 14 is. The. Cable pulley 33 is connected to the lower brake ring 13 'by means of studs 15'. To at the. Lifting the winding drum 10 from the shaft 11, the brake rings and the pulley in To hold their position firmly, the retaining tab 37 and engaging in the pulley are on the annular flange 24 the bearing plate 36 and the base plate 14, the retaining clip 38 is provided, which is also in the rope. disk engages. The embodiment according to FIG. 6 has the advantage that the drive for the take-up drum! takes up little space. The drive can simultaneously drive the laying device for the strand-shaped winding material on the winding drum, can be used to achieve a uniform To ensure that the material to be stranded is wound onto the drum. For example, the rope 32 can over Another pulley run through which the Verlcgerolle in a known manner via a screw spindle in a reciprocating motion. ·

The invention can also be used for winding up strand-like winding material without a drive. This is explained below with reference to FIG. In this figure, a stirrup stranding is assumed, in which the veins of a vein group twisted together by rotating the pivot arm 40 will. The M-earth wires are routed over withdrawal disks (not shown), which increase the withdrawal speed determine, and then via the swivel arm 40 and the guide roller 41 on the Atifwickeltrommel 10 wrapped. Here, the winding drum is sub-synchronously closed by the brake rings 13 and 13 ' the pivot arm 40 braked. There is a winding up in which a separate drive of the The winding drum is not carried out by the shaft of the winding drum, but by the train of the : group of veins to be wound.

In FIGS. 8 and 9, the two cases of a winding drum with and without a drive are particularly illustrated. The inner circles 10 "mean the winding drum with the speed", and the outer dashed circles 40 "the rotation of the welding arm 40 with the speed n _v must be braked more or less according to the intended winding tension, which is particularly important to keep constant at the stranding point. As a result, as FIG. 8 indicates, winding takes place without a separate drive. Take-up drum. In the. 9, on the other hand, the take-up drum is driven over-synchronously via its own shaft, namely via the brake rings 13 and 13 '. From the respective position of the roller 41 on the swivel arm in FIGS. 8 and 9 it can be seen that. the winding drum with the speed ji * in the one case (Fig. 8) is driven passively by the wire train and in the other case (Fig. 9) actively generates the wire train.

10, 11, 12 show three exemplary embodiments for the use of winding drums without Drive for the production of twisted wire groups for telecommunication cables.

In the embodiment according to FIG. 10, a winding drum is used as a winding drum in the Production of a star quad used in an advantageous manner. Located on the upper wing 42 there are four supply spools 43 arranged in a star shape for the individual wires 44 and also four in a star shape arranged take-off disks 45. The wires 44 run from the supply drums 43 over the take-off disks 45 to the stranding nipple 46, which is structurally designed with the pivot arm 47, which is as lightweight as possible is united. At the end of the swivel arm

30 is the guide roller 48 for guiding the twisted spiral quad cable 49 to the winding drum 10. As a counterweight to the pivot arm and guide roller are used, the pivot arm 50 with deni sm end located additional weight 51, both arms. through which, cross brace 52 are connected. The swivel arm 47 is set in rotation by the drive motor 53 via the pulleys 54 and 55 at the desired speed in order to twist the wires together and wind the twisted star quad onto the drum IO. As a result of the arrangement of the brake rings 13 and 13 'and the braking produced by the weight of the drum, it is achieved according to the invention that the quad 49 winds up on the drum with constant tension. The motor 53 also drives the take-off disks 45 at the same time, as shown by the dashed line. The brake arrangement according to the invention, which does not require any additional braking and drive elements, allows the winding drum to be exchanged quickly. In the figure it is indicated that the winding drum including the brake rings is arranged on a movable and lockable base 56. After the drum has been fully wound, it is removed from the machine together with the mobile support 55, whereupon an empty drum is placed back into the machine. Machine is introduced. The winding drum and possibly also the mobile base can, as indicated by the arrows, be lowered and raised in the vertical direction in order to bring about a laying in layers when winding the quad.

In order to avoid any disturbing torsion of the cores during this stranding, the cores can get a pre-twist, which can be done by having the supply drums in a rotatable Yoke 57 is arranged, as indicated above in FIG. 10. In this case the Supply drums 43 the yokes 57 containing the supply drums.

11 shows an exemplary embodiment for stranding in pairs, in which the winding drums according to the invention are used as storage drums for the individual cores. Are located to each other to be twisted wires 58 on the \ ^r orratstrommcln 59 and 60 with the intermediate brake rings 13 and 13 '. The two drums rest on the movable base 56 with a frictionless thrust ball bearing 61 or another bearing that is as frictionless as possible between them. The wires 58 run over the guide rollers 63 attached to the frame 62 to the stranding nipple 64. The stranding frame 62 is driven by the motor 65 via the pulleys 66 and 67. Through the. When the twisting frame 62 is rotated, the two cores are twisted to form a pair in the twisting nipple 64. From here, the twisted pair 68 is pulled off by means of the pull-off disk 59 and then wound onto the winding drum 70. The drive motor 65 can, as the dashed line indicates, also drive the take-off pulley and, if necessary, the winding drum at the desired speed. The additional weight 71 serves as a counterbalance weight for the stranding frame 62 including the lower guide roller 63. With this arrangement, too, the braking of the core supply drums without additional brakes is particularly favorable without a special drive, in order to move the drums in a manner similar to the embodiment according to FIG. 10 to be able to change quickly. A particular advantage here is that the pulp value has an even effect on both cores as a result of the mutual braking.

The invention can advantageously also be used for the production of twisted wire groups, in particular star fours, in the rapid stranding process by means of a bow tube. According to a related embodiment shown in FIGS. 12 and 13 in a side view and at the interface AB in a top view, four cores are stranded into a star quad with the aid of supply or Ahlauftrnmtneln formed according to the invention and a bracket tube. The four storage drums 72 are mounted on the stationary base plate 73 with the interposition of the brake disks 13 and 13 '. The wires 74 run from the supply drums over the guide rollers 75 and guide rollers 76 and then through the opening 77 of the base plate and through the bracket tube 78. By rotating the bracket tube 78 around the base plate including the supply drums, the wires at the entry and exit of the bracket tube are carried along twisted into a star quad at twice the speed of rotation. This device can also be used for the production of twisted pairs or other wire groups.

14 and 15 show an exemplary embodiment of a high-speed stranding machine in which winding drums according to the invention are used both as storage drums for the individual cores and as winding drums for the twisted group of cores. The individual cores 80 are then pulled off the supply drums 81 by means of the take-off pulley 83 driven by the motor 82 and run over the guide roller 84 through the bracket tube 85 to the winding drum 86. The bracket tube 85 is set in rotation by the motor 82 via the pulleys 87, 88 and 89 and is mounted in bearings between the foundation 90 and the upper bearing surface of the supporting frame 91. Like the supply drums 81, the take-up drum 86 is also provided with the brake rings 13 and 13 'for the purpose of uniform braking. For the purpose of uniform winding of the twisted group of cores 92, the winding drum 86 is moved up and down, as indicated by the double arrow. The upward and downward movement occurs through the rotation of the chain 93, coupled to the take-off pulley 83, around the sprockets 94 and 95 a deflection sprocket 98 is guided and at the lower end of which the winding drum 86 is located. Corresponding to the rotation of the chain 93 , the fastening point 95 is moved back and forth and thus the winding drum 86 is moved up and down. This drive for the upward and downward movement of the drum 86 is shown separately in FIG. The vertical part of the chain which carries the winding drum 86 is expediently designed as a rigid rod which is guided in the bearing 99 and possibly in a further bearing. The chain transmission with the sprockets is then placed higher accordingly. Other laying devices of the usual type can also be used for the upward and downward movement of the winding drum. .

The use of trained according to the invention Wi ekel drum η in. Stranding machines for Production of twisted wire groups for telecommunication cables has an increased uniformity and Symmetry of the core groups produced and thus smaller couplings result. This is special Importance for the production of star fours for carrier frequency transmission.

16 to 18 are three advantageous examples of use of winding drums as well as' core supply drums as well as winding drums according to the invention for stranding machines shown.

16 shows a horizontal high-speed stranding machine for producing twisted pairs for telecommunication cables. The two core supply drums 100 with their brake rings 13/13 ' are stored in the drum carrier 101. During the offset process, the drum carrier 101 and the drums 100 maintain their position due to the low position of their center of gravity. The wires 102 run through the nipple 103 as a pre-twisted pair 104 over the guide rollers 105, which are attached to the stranding frame 106 , to the stranding nipple 107 and from there as a final twisted pair 104 'over the take-off disk 108 and laying roller 109 to the winding drum 110, which is also with the 'brake rings 13/13' is equipped. The drive motor 111 drives, on the one hand, the pulleys and 113 and, via the bevel gears 114 and 115, the stranding frame 106 and, on the other hand, the winding drum 110 . Furthermore, the drive motor can also drive the take-off pulley 108 and the laying roller 109. By the rotation of the stranding frame 106 is a double \ ^r erdrillung takes place, in the Yerseilnippeln 103 and 107th

Based on FIG. 16, FIG. 17 shows a standing high-speed stranding machine. The two wire drums 116 and 117 are arranged in a frame 118. The wires 119 run over the guide rollers fastened to the frame 118 to the stranding nipple 121 and from there as a pre-twisted pair 122 over the "guide rollers" 124 fastened in the stranding frame 123 to the second stranding nipple 125.

The finally twisted pair 122 'is

«09 Τ28Ί83

Claims (33)

role. 126, the haul-off disk 127, the laying roller 128 to the take-up drum 129. The Dei motor 130 drives, on the one hand, the rope pulley 123 via the pulleys 131 and 132 and, on the other hand, the winding drum 129 and possibly also the haul-off pulley 127. Here, too, there is a double twist, namely in the stranding nipples 121 and 125. In order to prevent the drum frame 118 from rotating at the same time as the stranding frame 123 rotates, the two frames are coupled to one another by means of a gear ratio. This gear ratio consists of the gear 134 attached to the frame carrier 133, onto which the gear 135 rotates around with the frame 123. The resulting rotation of the gear 135 is transmitted via the rod 136 and the gear 137 to the gear 138 connected to the drum frame 118. This gear ratio is designed and dimensioned so that the drum frame HS maintains its position in space. 18 shows the reverse case of a high-speed stranding machine for the production of star fours, the vein supply drums being stationary and the take-off disk including the winding drum being arranged in the stranding frame. The wires 139 run from their storage drums 140 through a fixed divider or guide disk 141 to the stranding nipple 142. From there they run as a pre-twisted star quad 143 over guide rollers 145 attached to the stranding frame 144 to the second stranding nipple 146 and then as a final twisted star quad 143 ' the take-off disk 147 and the laying roller 148 to the winding drum 149. The stranding frame 144 is through the. Motor 150 driven by stranding disks 151 and 152. The stranding frame contains the gear wheel 153 through which the take-up drum 149 and possibly also the take-off disk 147 are driven via the gear wheel 154 and the bevel gears 155 and 156. The invention is not limited to the specified execution options. For example, brake disks can also be used in place of brake rings. The stranding machines according to FIGS. 16 and 17 can also be used for star stranding, and the stranding machine according to FIG. 18 can also be used for stranding in pairs. In the embodiment according to FIG. 1S, the wire storage drums 149 are advantageously arranged in a star shape, as is also provided in a similar manner in FIG. In addition, the invention can also be used for other stranding and winding processes in cable technology, specifically wherever the tensile stress of the strand-like stranded or wound material must be kept constant during the winding process. An essential advantage of the invention can be seen in the simple structural design of the weight brake, which can be used for further structural simplifications of the stranding and winding machines, as shown in particular by the exemplary embodiments according to FIGS. 11 to 16. PATESTAXSfRtCHH: 1. Winding drum, the braking effect of which is regulated by the drum weight, in particular for strand-shaped winding material for electrical cables, in which the drum shaft with the firmly seated Drum is arranged perpendicular or inclined to the vertical, characterized in that that between the lower face of the. Drum and the support surface a horizontal or inclined to the horizontal braking surface in such a way What is effective is that when winding or unwinding the winding material with a constant. The specific brake pressure changes automatically so that the tensile stress is applied to the braking surface and keeping the braking surface constant remains constant in the winding material. 2. winding drum according to claim 1, characterized in that the values for the drum or winding dimensions and for the effective drum weights of the equation at least approximately correspond to the equation in which r _{a is} the radius of the outermost winding layer, r _{t is} the radius of the innermost winding layer, G _{a is} the gross weight and G _{e is} the tare weight of the drum. 3. Winding drum according to claim 1, characterized in that the mean radius r _{B of} the brake rings of the equation γ ft μ G _a μ G _e corresponds to the equation in which P is the tensile force in the strand-shaped winding material and μ is the coefficient of friction of the braking ring surfaces. 4. winding drum according to claim 1, characterized in that the upper brake ring with the The drum shaft is firmly connected in the direction of rotation, so that the drum is perpendicular to the standing wave attached and easily detachable connected to it, without the brakes to solve or open. 5. winding drum according to claim 4, characterized in that the on the drum shaft attached drum between a centering cone (18) provided on the shaft and a Centering cone (18 ') of the fastening nut is clamped. 6. winding drum according to claim 4, characterized in that the lower end of the drum shaft in a journal bearing (bearing pot 21) is rotatably supported. 7. winding drum according to claim 6, characterized in that the journal bearing as a needle bearing (22) is formed, which is carried by a thrust ball bearing (23). 8. winding drum according to claim 4 and the following claims, characterized in that that the brake rings (13/13 ') between an upper ring flange attached to the drum shaft (24) and a lower annular flange (21 ') connected to the bearing pot (21) of the journal bearing are arranged. 9. winding drum according to claim 8, characterized in that the brake rings on the annular flanges are attached interchangeably. 10. winding drum according to claim 9, characterized in that between the brake rings and the upper annular flange (24) and the lower annular flange (21 ') resilient means, z. B. a resilient oil-resistant rubber layer are arranged. 11. winding drum according to claim 8, characterized in that; that the upper ring flange (24) has a downwardly inclined collar (24 ') to protect the brake rings from contamination. 12. Wickeltronimel according to claim 11, characterized in that the downwardly inclined collar (24 ') with a shoulder (24 ") is given to the annular flange including the shaft when removing to hold the drum from the shaft. 13. Winding drum according to claim 8, characterized in that the brake rings in one are supported by the lower annular flange (21 ') formed annular space. 14. Wickeltronimel according to claim 13, characterized in that the annular space which the brake rings receives, with a lubricating liquid, e.g. B. a special oil mixture is filled. 15. Winding drum according to claim 1, characterized in that the brake rings consist of one porous sintered metal, such as sintered iron, exist with oil impregnation. 16. Winding drum according to claim 1, characterized in that the brake rings consist of one non-porous metal obtained by powder metallurgy, e.g. B. made of copper and iron powder, the lubricant in the form of colloidal Contains graphite. 17. Winding drum according to claim 1, characterized in that the brake rings made of hardened Made of steel, the friction surfaces of which are polished to a high gloss. 18. winding drum according to claim 1 as a winding drum with drive, characterized in that that the drive takes place via the rotatably arranged bearing pot (21) according to claim 6. 19. Winding drum according to claim 18, characterized by one placed on the bearing pot Pulley (29) or the like for the drive (Fig. 5). 20. winding drum according to claim 1 as a winding drum with drive, characterized in that that the drive in the form of a pulley (33) or the like. Between the base plate (14) and the brake rings (13/13 ') is installed (Fig. 6). 21. Wickeltronimel according to claim 20, characterized in that the pulley (33) against the Bearing pot (21) is supported by a needle bearing (34) and down by a ball bearing (35). 22. Winding drum according to claim 20, characterized in that the upper annular flange (24) a retaining bracket (37) engaging in the pulley (33) and on the base plate (14) or Bearing plate (36) a retaining tab (38) also engaging in the pulley is provided in order to the pulley and the upper ring flange with the brake rings when removing the drum to hold on to the wave. 23. Winding drum according to claim 1 as a winding drum, characterized in that the The drum mounted on the brake rings runs without a drive. 24. Winding drum according to claim 23 as a winding drum without a drive for Verseilmaschi- ncn, characterized in that the stranding is mounted around the rings on the brake by means of a Winding drum rotating swivel arm (40, 47) takes place (Fig. 7 and 10). 25. Winding drum according to claim 24, characterized in that the winding drum with the brake rings is arranged on an easily removable base (56). 26. Winding drum according to claim 25, characterized in that the base (56) in the horizontal plane is movable. ■ 27. Winding drum according to claim 24 or the following claims, characterized in that that the winding drum and possibly also the base (56) for the purpose of more uniform Winding up of the strand-shaped winding material (feed point of the winding material) up and down is arranged movably. 28. Winding drum according to claim 1 as a vein supply drum for stranding machines, characterized characterized in that several wire supply drums (59, 60) with brake rings inserted between them are arranged one above the other, so that the brake rings each time to brake two Drums are used (Fig. 11). 29. Winding drum according to claim 28, characterized in that the superimposed The drums rest on a bearing that is as smooth as possible, preferably a ball bearing (61). 30. Winding drum according to claim 1 as a supply or drain drum for the production of twisted Core groups, in particular star fours, characterized in that the storage drums (72) arranged on a fixed base plate (73), and the wires after diversion over Guide rollers (75) and guide rollers (76) through one around the base plate including storage drums rotating bracket tube (78) are guided (Fig. 12 and 13). 31. Winding drum according to claim 1, in particular as a winding drum for one on a stranding machine produced twisted wire group, characterized in that the drum (86) including the brake rings under the drum, freely suspended from the drum shaft is (Figs. 14, 15). 32. winding drum according to claim 30, characterized in that the freely suspended drum for the purpose of even winding up of the strand-shaped winding material at the winding point (feed point of the winding material) is arranged movable up and down. 33. winding drum with vertical drum shaft according to one of claims 1 to 32, characterized in that it is used as a vein supply drum and / or as a winding drum for the twisted core group is used in a stranding machine (Fig. 14 to 18). In addition 3 sheets of drawings