EP0088993B1 - Verseileinrichtung für Verseilmaschinen, insbesondere Vorverdrall- und Abzugeinrichtung - Google Patents

Verseileinrichtung für Verseilmaschinen, insbesondere Vorverdrall- und Abzugeinrichtung Download PDF

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Publication number
EP0088993B1
EP0088993B1 EP83102286A EP83102286A EP0088993B1 EP 0088993 B1 EP0088993 B1 EP 0088993B1 EP 83102286 A EP83102286 A EP 83102286A EP 83102286 A EP83102286 A EP 83102286A EP 0088993 B1 EP0088993 B1 EP 0088993B1
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EP
European Patent Office
Prior art keywords
support frame
rotor support
rotation
drafting
axis
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP83102286A
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German (de)
English (en)
French (fr)
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EP0088993A1 (de
Inventor
Theodor Preussner
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Individual
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Individual
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Publication date
Priority claimed from DE19823209169 external-priority patent/DE3209169A1/de
Priority claimed from DE19823226572 external-priority patent/DE3226572A1/de
Application filed by Individual filed Critical Individual
Priority to AT83102286T priority Critical patent/ATE13563T1/de
Publication of EP0088993A1 publication Critical patent/EP0088993A1/de
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Publication of EP0088993B1 publication Critical patent/EP0088993B1/de
Expired legal-status Critical Current

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    • D—TEXTILES; PAPER
    • D07—ROPES; CABLES OTHER THAN ELECTRIC
    • D07B—ROPES OR CABLES IN GENERAL
    • D07B3/00—General-purpose machines or apparatus for producing twisted ropes or cables from component strands of the same or different material
    • D07B3/08—General-purpose machines or apparatus for producing twisted ropes or cables from component strands of the same or different material in which the take-up reel rotates about the axis of the rope or cable or in which a guide member rotates about the axis of the rope or cable to guide the rope or cable on the take-up reel in fixed position and the supply reels are fixed in position
    • D07B3/10—General-purpose machines or apparatus for producing twisted ropes or cables from component strands of the same or different material in which the take-up reel rotates about the axis of the rope or cable or in which a guide member rotates about the axis of the rope or cable to guide the rope or cable on the take-up reel in fixed position and the supply reels are fixed in position with provision for imparting more than one complete twist to the ropes or cables for each revolution of the take-up reel or of the guide member
    • D—TEXTILES; PAPER
    • D07—ROPES; CABLES OTHER THAN ELECTRIC
    • D07B—ROPES OR CABLES IN GENERAL
    • D07B7/00—Details of, or auxiliary devices incorporated in, rope- or cable-making machines; Auxiliary apparatus associated with such machines
    • D07B7/02—Machine details; Auxiliary devices
    • D—TEXTILES; PAPER
    • D07—ROPES; CABLES OTHER THAN ELECTRIC
    • D07B—ROPES OR CABLES IN GENERAL
    • D07B2207/00—Rope or cable making machines
    • D07B2207/40—Machine components
    • D07B2207/409—Drives

Definitions

  • the invention relates to a stranding device for stranding machines, in particular a pre-twist and take-off device as a ballast for single or multiple impact machines, with a rotary drive rotor support frame and a rotary drive take-off disc mounted transversely to the axis of rotation and longitudinal axis of the rotor support frame, in which the cable elements on an entry stranding point in the longitudinal axis is fed to the rotor support frame and the rope on the rotor support frame is guided to the take-off disk and, after being wrapped around it, through the longitudinal axis through the rotor support frame.
  • 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.
  • the initially matching from layer to layer - ie balanced - incoming wire lengths are no longer correct for the subsequent second stroke, because then the inner compared to the outer wire layers have a relatively large excess length.
  • the multi-layer ropes from outer to inner layers, i.e. H. Relative excess length towards the core wire tends to form loops and thus leads to fluctuations or increases in the rope diameter.
  • pre-swirl devices are already used to meet only the requirements mentioned under a) (see »Wirhtwelt « 7/1977, page 270, Fig. 7, and page 271, 4th to 6th paragraph of the article »Comparison of processes Single- and double-stroke cutting «by AC Osman). These facilities run quickly. however, they only have simple drag discs without their own deduction.
  • the strand must also be pulled through the pre-twist device from the take-off in the double striking machine. The tensile stress in the strand is not substantially reduced after leaving the swirl device, but rather by the centrifugal force additionally generated in the device and not compensated by it even increased considerably.
  • a driven take-off disk which is wrapped several times by the stranded wire, is indispensable for gentle pre-stranding in high-speed operation.
  • the rope tension on the take-off disk is reduced very quickly, so that the tension force in the running rope run after the take-off disk is considerably smaller than in the running rope run.
  • the known pre-twist and take-off devices of the type specified at the outset are unsuitable for high-speed double-stroke product speeds because the usual drive of the take-off disk takes place via a toothed belt drive which is mounted completely eccentrically to the machine axis of rotation.
  • the complete toothed belt transmission is arranged outside the impact rotor designed as a frame support.
  • a trigger disk diameter for example, 180 mm
  • corresponding frame support dimensions and an impact rotor speed of 4000 or more revolutions per minute such a construction would lead to an unbearable centrifugal load on the rotor support frame. In addition, this would result in a completely indisputable short service life for the roller bearings involved.
  • a trigger disk which is driven not only about its axis of rotation but also about the axis of rotation of the rotor support frame, is a guided gyroscope that is forced to rotate by its guide frame (rotor support frame).
  • the forced precession produces a strong gyroscopic effect, the gyroscopic moment, as a result of inertial forces.
  • the invention has for its object to provide a stranding device of the type specified, which can be used in particular as a pre-twist and take-off device as a ballast for single or multiple impact machines and in particular for double impact machines and in which the desired particularly high rotational speeds and thus impact rates are achieved can reach an intolerable level without the described adverse effects of the gyroscopic and centrifugal forces.
  • the rotor support frame should thus be relieved of the effects of the centrifugal and centrifugal forces as completely as possible, at least as far as possible, even at the highest possible rotational speeds and impact rates.
  • the aim is to achieve the simplest, most compact and, above all, reliable device with a long service life. Above all, the difficulties in the design and storage of the trigger disk should be countered in this regard.
  • a rotational element driven in the opposite direction of rotation is rotatably mounted coaxially with it on the axis of rotation of the trigger disc and the shape, dimensions, masses and rotational speeds of the trigger disc and of the rotary element as well as those rotating with them Components are chosen such that the respective product of mass moment of inertia and angular velocity of the rotating units is at least approximately the same size, and that the trigger plate and the rotating element are each mounted on the common axis of rotation with the aid of an associated hollow shaft and the hollow shafts additionally against those of the rotor support frame
  • Directional centrifugal forces are rotatably supported on the common axis of rotation and that the product of the total mass of the components associated with the trigger plate and the distance from their common center of gravity from the longitudinal axis of the rotor support frame ns is at least approximately equal to the product of the total mass of the component assigned to the rotating element and the distance from their common center of gravity from the longitudinal axis of the rotor support
  • the gyro moment generated by the unit containing the pull-off disk is compensated with the resulting gyroscopic forces by the gyro moment generated with the counter-rotating unit containing the rotating element, so that the described strong and harmful gyroscopic forces do not affect the rotor support frame.
  • 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.
  • the design of the counter-rotating drives for the trigger disk and the counter-rotating element is of particular importance.
  • a particularly favorable design with corresponding compensation effects is achieved according to one embodiment of the invention in that the trigger plate and the rotating element are each driven in rotation by means of a belt drive with a pulley, in particular toothed belt drive, located on the rotor support frame, and a planetary gear is arranged in this way at the rope exit end of the rotor support frame that the sun gear is rotatable about the longitudinal axis of the rotor support frame with a hollow shaft receiving the rope in the rope exit end of the rotor support frame and the opposing planet wheels, which are designed as pulleys, are mounted on a common axis of rotation which runs parallel to the axis of rotation of the pulling disk and the rotating element, and that the planet wheels are dimensioned with their rotating components in shape, dimension, mass and rotational speeds such that the respective product of the moment of inertia
  • the sun gear and planet gears have the intermeshing bevel gear teeth, to which the respective pulley is connected in the case of the planet gears. Due to its arrangement according to the invention, the planetary gear used for the drive already has, in principle, an extraordinarily symmetrical structure, and the opposite drive movement for the pull-off disk and the counter-rotating element is generated without the interposition of further drive elements via the planet gears.
  • the basic structure of the planetary gear in turn leads to a symmetrical arrangement with respect to the rotor support frame.
  • a configuration and arrangement which is advantageous for the compact design on the one hand and for the desired compensation effect for the gyroscopic torques and especially for the centrifugal forces on the other hand is achieved in a further embodiment of the invention in that the trigger disk and the counter-rotating element each comprise a disk-shaped fastening flange and a side of it protruding, directed to the other mounting flange circumferential ring body, wherein the circumferential ring body of the trigger disc forms the winding surface (the pull ring) for the rope and the circumferential ring body of the rotating element engages under the circumferential ring body of the trigger disk.
  • the trigger plate and the rotating element thus run largely into one another and can therefore be moved close together, which promotes the compensating effect for the centrifugal forces.
  • the design as a circumferential ring body arranged on the disk-shaped fastening flange enables shapes which are particularly favorable for the compensation effect to be achieved and the masses required in each case are pressed into one another.
  • the mass of the associated Um forming the main mass of the counter-rotating element Catch ring body largely enclosed by the circumferential ring body of the trigger disk, which is particularly beneficial for the compensation of centrifugal forces.
  • Materials, shape and cross-sectional shapes of the circumferential ring bodies and also of the fastening flanges can be optimally selected for the desired compensation effect on the one hand and for the desired compact design on the other hand.
  • the nesting of the opposing components also shortens the entire extraction device, which in turn leads to a reduction in the centrifugal forces to be compensated.
  • a design which is expedient with regard to the described compensation effects and desired compact arrangements is achieved in a further embodiment of the invention in that the trigger disk and the rotating element and their associated annular pulley are each fastened to the associated hollow shaft and each hollow shaft is attached to its end face located to the rotor support frame a tie rod is rotatably supported by a combined radial and axial bearing, each tie rod is coaxially inserted, in particular screwed, into a common support axis forming the axis of rotation, and that each tie rod is connected to the facing rotor support frame wall.
  • a closed force flow forming unit of the entire trigger device is created, which is then fixed to the rotor support frame wall with simple connecting means.
  • 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.
  • the tie rods are expediently fastened in the rotor support frame wall with a screw connection which can be adjusted in the longitudinal direction.
  • 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.
  • the configuration of the mounting according to the invention which is described with reference to the mounting of the pull-off disk and the rotating element, can also be used with a corresponding advantage on the common axis of rotation.
  • Another embodiment of the invention has for its object to further develop and improve the stranding device according to the main patent so that any uncontrolled course of the rope on the take-off disk is avoided with the possible consequence of insufficient take-off or rope tear and instead a correct and clean guidance of the rope the trigger plate is reached.
  • the described compensation of centrifugal and centrifugal forces should continue to be fully guaranteed. Overall, therefore, the achievement of very high speeds and thus stroke rates should be further promoted.
  • this is achieved in a first step above all by the fact that on a further axis of rotation running transversely to the rotational and longitudinal axis of the rotor support frame, a second extraction disk with an associated rotation element driven in the opposite direction to it is mounted on the rotor support frame and the second Trigger disk and associated rotating element and the associated components are all designed, dimensioned and arranged like the corresponding elements of the first trigger disk with their rotating element, the rope, the trigger disk is guided alternately over both trigger disks and the winding surface of at least one of the trigger disks for rope guidance is provided with circumferential guide grooves .
  • transmission gears are used according to the invention for the rotary drive of the individual rotating elements, the result is a relatively short arrangement of the drive and the extractor disks with their respective rotating elements. This could lead to only a short cable guide starting from the second take-off disk to the exit point of the rotor support frame.
  • a transmission gear is switched on between the planet gears of the drive system and their gears as well as the gears of the drive pulley and the associated rotating element , and there are these counter-rotating transmission gears like the planet gears on a common axis of rotation, which runs parallel to the axis of rotation of the planet gears, and there are also the transmission gears like the planet gears with their rotating components in shape, dimension, mass and rotational speeds such that the respective product of mass moment of inertia and angular velocity of the structural units rotating against one another is at least approximately the same size, and on their common axis of rotation against the F directed towards the rotor support frame lending forces supported rotatably.
  • the connected gears lead to the desired opposite directions of rotation, and there is a significantly increased distance between the actual drive system with the planet gears and the drive disk facing this with its rotating element, which can be used for rope guidance with a relatively large radius of curvature, and so on overall to achieve a gentle rope guide.
  • the rope is also continuously the nickel direction and the trigger plate alternately guided over the trigger plates. This results in a rope guide on the trigger disks in the form of an 8.
  • these circumferential grooves of the pulling disks are offset with respect to one another in the axial direction, preferably by half the groove spacing.
  • 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.
  • the device according to the invention is used as a pre-twist and take-off device with a downstream winding device for the rope, which has a circumferential, coaxially arranged rotor element, along which the rope grained by the pre-twist and take-off device is guided along the common axis of rotation, and one of the Rotor element revolving winding drum, so in a further embodiment of the invention, the rotary drive for the rotor support frame and the rotary drive for the take-off disks of the pre-twist and take-off device, as well as the rotary drive for the rotor element of the winding device are derived from a common main drive motor in constant coupling by mechanical positive drive.
  • an adjustable gear can be switched on in a further embodiment of the additional invention between the main drive motor and the rotary drive for the trigger disks, here the planetary gear, for. B. a step or continuously variable transmission.
  • 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.
  • the rotor support frame 1 is driven via a drive wheel or a drive pulley 3 for rotation about its longitudinal axis, e.g. B. by a suitable belt drive, as indicated by the arrow 4.
  • the drive pulley 3 also forms the entry stranding point 5 for the rope elements 6, which are twisted into the rope 7.
  • the cable 7 is guided through the hollow bearing shaft 8 of the rotor support frame into it and is guided to the take-off disk, which is generally designated 10, via a plurality of cable pulleys 9 mounted on the inside of the rotor support frame.
  • the rope After wrapping the take-off pulley, the rope is returned to the longitudinal axis of the rotor support frame 1 via a further plurality of rope pulleys 9, which are mounted on the inner wall of the rotor support frame 1, and is guided outwards through the hollow bearing shaft 11 in a manner to be described.
  • the end of the rotor support frame 1 directed towards the bearing shaft 11 is referred to below as the rope exit end of the rotor support frame.
  • 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.
  • a rotational element which is rotated in the opposite direction to the direction of rotation of the extraction disk 10 and is generally designated 13 in FIG. 1.
  • the components rotating with the rotating element 13 are arranged towards the other side of the axis of rotation, directed downwards in FIG. 1.
  • a pulley 14 is connected to the take-off pulley 10 and a pulley 15 to the rotating element 13.
  • a planetary gear arranged at the rope exit end of the rotor support frame 1 serves for the counter-rotating rotation drive of the take-off disk 10 with 14 and rotation element 13 with 15.
  • the sun gear 16 is rotatably supported about the longitudinal axis of the rotor support frame 1 by means of a hollow shaft 17 in the hollow bearing shaft 11 of the rotor support frame 1 and is driven by a suitable drive pulley 18, for. B. a belt drive indicated by the arrow 19.
  • the cable 7 is guided to the outside by the sun gear 16 and its hollow shaft 17. With the sun gear (bevel gear) 16 mesh the two planet gears (bevel gears) 20 and 21, which thus, as indicated by the arrows, are driven in opposite directions.
  • the planet gears 20 and 21 are also designed as pulleys and are in drive connection via the belts, in particular toothed belts 22, with the pulleys 14 and 15 of the take-off pulleys 10 and the rotary element 13.
  • the planet gears 20 and 21 are rotatably mounted on a common axis of rotation 23.
  • the axes of rotation 12 and 23 are fastened in the rotor support frame wall in a rotationally fixed manner using suitable fastening means, as is initially shown schematically in each case at 24.
  • the shape, the dimensions, the masses and the rotational speeds of the take-off disk 10 and of the rotary element 13 and of the respective components rotating with them are selected such that the respective product of the moment of inertia and the angular velocity of the rotating units is at least approximately the same size.
  • the product of the total mass of the components assigned to the trigger plate 10 and the distance from their common center of gravity from the longitudinal axis of the rotor support frame 1 is at least approximately equal to the product of the Total mass of the components assigned to the rotating element 13 and the distance from their common center of gravity from the longitudinal axis of the rotor support frame 1, which means that the sum of the static mass moments is zero.
  • a corresponding dimensioning rule applies to the planet gears 20 and 21 with their components rotating together with them as counter-rotating units.
  • 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.
  • FIG. 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 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 .
  • a suitable screw connection 35 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.
  • the hollow shaft 36 is mounted on the common axis of rotation and support 12 via a combined radial and axial bearing 38.
  • the bearing 38 is supported in the axial direction on the large-sized head of a tie rod 39, which, as shown clearly in FIG. 2, is screwed into the common axis of rotation and support 12 and, like the tie rod 32, against rotation, for. B. is secured by a pin 40 or the like.
  • the counter-rotating unit from 33, 34, 15, 36 is thus supported by the tie rod 39 so that it can rotate in the axial direction on the common axis of rotation and support 12.
  • the common rotation and support axis 12 is connected to the rotor support frame via the two tie rods 32 and 39 by a suitable adjustable screwing device, which is generally designated 24, as clearly shown in FIG. 2.
  • the arrows 41 indicate the counter-rotating drive and thus rotational movement of the extraction disk 10 with its associated components and of the counter-rotating element 13 with its rotating components.
  • the I ig. 2 described with regard to the trigger device special storage via the hollow shaft, the combined radial and axial bearings and the tie rods is used in a corresponding manner in the storage of the planet gears 20 and 21 on their common axis of rotation 23.
  • the trigger plate 10 with its rotating construction. elements and the counter-rotating element 13 with its rotating components with opposite, but the same rotational speed.
  • Fig. 2 also shows particularly clearly that in order to achieve the described compensation effect in particular the shape, the dimensions and the mass, that is to say also the material, of the circumferential ring body 34 of the rotary element 13 can be selected in a particularly adaptable manner. The same also applies to the respective characteristic data of the circumferential ring body 26 of the take-off disk 10, which forms the pull ring for the rope.
  • Fig. 2 makes it clear that the desired compensation effect can be achieved by suitable "asymmetrical" selection of the characterizing data. Likewise, Fig. 2 makes it clear that the entire extraction device has a closed power flow with respect to its centrifugal forces over the common axis of rotation and support 12, so that all centrifugal forces occurring are absorbed within this closed system and cannot affect the rotor support frame 1.
  • a rotationally symmetrical, namely cylindrical, rotor support frame 1a is rotatably supported at both ends about its longitudinal axis in a suitable machine frame, which is indicated at 2.
  • the rotor support frame 1a is driven via a drive wheel or a drive disk 3 for rotation about its longitudinal axis, e.g. B. by a suitable belt drive, as indicated by the arrow 4.
  • the drive pulley 3 also forms the entry stranding point 5 for the rope elements 6, which are twisted into the rope 7.
  • the cable 7 is guided through the hollow bearing shaft 8 of the rotor support frame 1a into it and is guided via a plurality of cable pulleys 9 mounted on the inside of the rotor support frame to the pull-off disks, which are generally designated 10a and 10b.
  • the rope first runs onto the first take-off disk 10a facing it and is then repeatedly guided alternately over both take-off disks.
  • 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.
  • the rope 7 is returned to the longitudinal axis of the rotor support frame 1a via a further plurality of rope pulleys 9, which are mounted on the inner wall of the rotor support frame 1a, and is guided outward through the hollow bearing shaft 11 in a manner to be described.
  • the end of the rotor support frame 1a directed towards the bearing shaft 11 is referred to below as the rope exit end of the rotor support frame.
  • both the trigger disk 10a and the trigger disk 10b with their associated components are rotatably mounted on a common axis of rotation 12a or 12b in such a way that the components rotating therewith are to one side of the rotor support frame 1a extend towards, in Fig. 3 upwards.
  • a rotation element t which is rotated in opposite directions with respect to the direction of rotation of the respective associated extraction disc 10a or 10b, is also rotatably supported, which rotation elements are generally designated 13a and 13b in FIG. 3.
  • the components rotating with the rotation elements 13a and 13b are arranged towards the other side of the axis of rotation 12a and 12b, respectively, downward in FIG. 3.
  • Both trigger disks 10a and 10b are connected to a gear 14a and 14b.
  • Each rotary element 13a and 13b is connected to a gear wheel 15a and 15b, respectively.
  • a planetary gear arranged at the rope exit end of the rotor support frame 1a serves for the counter-rotating rotation drive of the extraction disks 10a and 10b on the one hand and of the rotation elements 13a and 13b on the other hand with their respectively assigned gear wheels 14a, 14b and 15a, 15b.
  • Whose sun gear 16 is rotatably supported about the longitudinal axis of the rotor support frame 1a by means of a hollow shaft 17 in the hollow bearing shaft 11 of the rotor support frame 1a and is driven by a suitable drive pulley 18, for. B. a belt drive indicated by the arrow 19.
  • the cable 7 is guided to the outside by the sun gear 16 and its hollow shaft 17.
  • the two planet gears 20 and 21 designed as bevel gears, which are thus driven in opposite directions.
  • the planet gears 20 and 21 are each connected to a gear 20a and 21a.
  • a transmission gear 20b or 21b is connected between the gears 20a and 21a of the planet gears 20 and 21 and the gears 14b and 15b of the second drive pulley 10b located to the drive system and its associated rotating element 13b.
  • the gearwheels 20a, 20b, 14b, 14a assigned to the extraction disks on the one hand and the gearwheels 21a, 21b, 15b and 15a assigned to the rotating elements are each driven in opposite directions to one another, as indicated by the arrows drawn on the gearwheels in FIG. 3.
  • the planet gears 20 and 21 with their gears 20a and 21 and the transmission gears 20b and 21b are each mounted on a common axis of rotation 23a and 23b.
  • the axes of rotation 12a, 12b, 23a and 23b are fastened in a rotationally fixed manner in the rotor support frame wall using suitable fastening means, as is shown schematically in each case at 24.
  • the shape, the dimensions, the masses and the rotational speeds of the extraction disks 10a and 10b as well as the rotating elements 13a and 13b and the respective components rotating with them are selected such that the respective product of the moment of inertia and angular velocity the units rotating around each other is at least approximately the same size.
  • the product of the total mass of the components assigned to the extraction disks 10a and 10b and the distance from their common center of gravity from the longitudinal axis of the rotor support frame 1a is at least approximately equal to the product of the total mass of the components assigned to the rotating element 13a or the rotating element 13b and the Distance from their common center of gravity from the longitudinal axis of the rotor support frame 1a, which means that the respective sum of the static mass moments is zero.
  • a corresponding dimensioning rule applies to the planet gears 20 and 21 with their gears 20a and 21a a with their components rotating with them as counter rotating components. The corresponding dimensioning rule also applies to the transmission gearwheels 20b and 21b with their components rotating together with them.
  • the planet gears 20 and 21 with their gears 20a and 21a, the transmission gears 20b and 21b, the extractor disks 14b and 14a and the rotation elements 13b and 13a are each driven at the same, but in opposite directions, speeds. Suitable ratios and reductions can, however, be selected depending on the application, while observing the design rule according to the invention. It is crucial that the design rule described in detail above and reproduced in the preceding is observed in each case.
  • the winding surface of at least one of the take-off disks 10a or 10b is provided with circumferential guide grooves for rope guidance, which are not shown in detail in order to simplify the drawing. These are known concentric grooves arranged next to one another and adapted to the respective application on the winding surface of the respective take-off disk.
  • a particularly precise cable guide on the winding surfaces of the pull-off disks can be achieved in that the winding surfaces of both pull-off disks 10a and 10b are provided with such circumferential guide grooves. It is expedient if the circumferential guide grooves of the pull-off disks 10a and 10b are offset in relation to one another in the axial direction, preferably by half the groove spacing, in order in this way to achieve a particularly favorable cable guide.
  • the axis of rotation 12b of the + second trigger disk 10b can also be inclined by a predetermined small angle with respect to the axis of rotation 12a of the first trigger disk 10a.
  • the toothing of the gears 14a, 14b and 20b and 15a, 15b and 21b are to be designed accordingly.
  • FIG. 5 shows a further embodiment of the invention largely schematically.
  • FIG. 5 first shows schematically at V the pre-swirl and extraction device described with reference to FIG. 3 with the rotor support frame 1a.
  • This pre-twist and take-off device V is followed by a winding device W.
  • This winding device is designed in a manner known per se as a so-called double-winder.
  • the rope 7 leaving the device V is fed coaxially to the winding device W.
  • This has a coaxially arranged revolving rotor element 42 and a winding drum 43 freely oscillating therein with the associated cable guide and laying devices, which are not identified in detail and are designed in a manner known per se.
  • the cable 7 is fed along the rotor element 42 through the longitudinal axis of the winding device W via the cable guide and laying devices (not shown) to the winding drum 43 in a manner known per se.
  • a double twist winder follows the pre-twist and take-off device V in the form of a so-called single twist stranding machine. With this overall arrangement, the individual rotational speeds are to be coordinated with one another in a predetermined manner.
  • the rotary drive for the rotor support frame 1 a and the rotary drive for the take-off disk within the rotor support frame 1 a, i.e. for the planetary gear with its drive disk 18 of the pre-twist and take-off device V, and the rotary drive for the rotor element 42 of the winding device W are in constant coupling by mechanical positive drive from derived from a common main drive motor, which is designated 44.
  • the main drive 3 motor 44 drives a pulley 46 via a shaft 45, which drives the drive pulley 3 for the rotor support frame 1 a via the belt 4.
  • the planetary drive system for the extraction disks of the rotor support frame 1 a is coupled to the shaft 45 of the main drive motor 44 via an adjustable gear 47 via the output shaft 48 and the pulley 49 and the belt 19 and the drive pulley 18.
  • a differential gear with its own motor can be provided as the adjustable gear 47.
  • 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.
  • 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.
  • the individual rotary drives are in constant coupling by means of a mechanical positive drive.
  • the embodiment described above can also be realized with the stranding device according to FIGS. 1 and 2 as a pre-twist and take-off device V.

Landscapes

  • Ropes Or Cables (AREA)
  • Tyre Moulding (AREA)
EP83102286A 1982-03-13 1983-03-09 Verseileinrichtung für Verseilmaschinen, insbesondere Vorverdrall- und Abzugeinrichtung Expired EP0088993B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT83102286T ATE13563T1 (de) 1982-03-13 1983-03-09 Verseileinrichtung fuer verseilmaschinen, insbesondere vorverdrall- und abzugeinrichtung.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3209169 1982-03-13
DE19823209169 DE3209169A1 (de) 1982-03-13 1982-03-13 Verseileinrichtung fuer verseilmaschinen, insbesondere vorverdrall- und abzugeinrichtung
DE3226572 1982-07-16
DE19823226572 DE3226572A1 (de) 1982-07-16 1982-07-16 Verseileinrichtung fuer verseilmaschinen, insbesondere vorverdrall- und abzugseinrichtung

Publications (2)

Publication Number Publication Date
EP0088993A1 EP0088993A1 (de) 1983-09-21
EP0088993B1 true EP0088993B1 (de) 1985-05-29

Family

ID=25800299

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83102286A Expired EP0088993B1 (de) 1982-03-13 1983-03-09 Verseileinrichtung für Verseilmaschinen, insbesondere Vorverdrall- und Abzugeinrichtung

Country Status (7)

Country Link
US (1) US4549394A (enrdf_load_stackoverflow)
EP (1) EP0088993B1 (enrdf_load_stackoverflow)
JP (1) JPS59500378A (enrdf_load_stackoverflow)
AU (1) AU556418B2 (enrdf_load_stackoverflow)
DD (1) DD208834A5 (enrdf_load_stackoverflow)
SU (1) SU1209038A3 (enrdf_load_stackoverflow)
WO (1) WO1983003268A1 (enrdf_load_stackoverflow)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102653928A (zh) * 2011-12-31 2012-09-05 江苏兴达钢帘线股份有限公司 一种捻股机平板过捻装置

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61124692A (ja) * 1984-11-20 1986-06-12 神鋼鋼線工業株式会社 ワイヤロ−プの撚り調整方法およびその装置
DE3808112A1 (de) * 1988-03-15 1989-09-21 Sevastopol Priborostroit Inst Einrichtung zur schraubenfoermigen zufuehrung von langerzeugnissen in eine verseilmaschine
US5540041A (en) * 1994-09-13 1996-07-30 Southwire Company Method of and apparatus for stress relieving multistranded cable
ES2169631B1 (es) * 1999-04-16 2003-11-01 Ohg Di Lesmo S P A Cabrestante rotativo para retorcer cabos.
JP4252957B2 (ja) * 2002-11-25 2009-04-08 株式会社ブリヂストン 撚り機、撚り線製造方法、プライ、及び空気入りタイヤ

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE500739A (enrdf_load_stackoverflow) * 1948-02-12
NL218132A (enrdf_load_stackoverflow) * 1957-03-30 1900-01-01
FR1390922A (fr) * 1963-04-12 1965-03-05 Geoffroy Delore Procédé pour transmettre un mouvement de rotation de l'une à l'autre des extrémités d'un élément filiforme, et machines à câbler pour la mise en oeuvre de ce procédé
AT286833B (de) * 1966-02-15 1970-12-28 E Vornbaeumen & Co Maschf Verfahren zur herstellung von spannungsfreien seilen oder litzen und schnellverseilmaschine zur durchfuehrung des verfahrens
US3396522A (en) * 1967-01-30 1968-08-13 Albert A. Biagini Stranding machine
US3388541A (en) * 1966-03-04 1968-06-18 Albert A. Biagini Method and apparatus for stranding wires, or the like
US3413793A (en) * 1966-04-29 1968-12-03 Western Electric Co Sheave capstan assembly for cable takeup apparatus
GB1263914A (en) * 1968-05-28 1972-02-16 British Insulated Callenders Improvements in or relating to a method of and apparatus for twisting together a plurality of elongated flexible elements
US4385486A (en) * 1979-10-22 1983-05-31 Tokusen Kogyo Kabushiki Kaisha Apparatus for manufacturing open cord
US4473995A (en) * 1983-02-01 1984-10-02 Southwire Company Concentric compressed double twist stranded cable

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102653928A (zh) * 2011-12-31 2012-09-05 江苏兴达钢帘线股份有限公司 一种捻股机平板过捻装置

Also Published As

Publication number Publication date
AU1228683A (en) 1983-10-24
US4549394A (en) 1985-10-29
WO1983003268A1 (en) 1983-09-29
SU1209038A3 (ru) 1986-01-30
EP0088993A1 (de) 1983-09-21
JPH0255555B2 (enrdf_load_stackoverflow) 1990-11-27
AU556418B2 (en) 1986-10-30
DD208834A5 (de) 1984-04-11
JPS59500378A (ja) 1984-03-08

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