EP2366818B1 - Dispositif pour régler automatiquement la tension d'alimentation de fil de broches à quatre torsions - Google Patents

Dispositif pour régler automatiquement la tension d'alimentation de fil de broches à quatre torsions Download PDF

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Publication number
EP2366818B1
EP2366818B1 EP20110154974 EP11154974A EP2366818B1 EP 2366818 B1 EP2366818 B1 EP 2366818B1 EP 20110154974 EP20110154974 EP 20110154974 EP 11154974 A EP11154974 A EP 11154974A EP 2366818 B1 EP2366818 B1 EP 2366818B1
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EP
European Patent Office
Prior art keywords
yarn
unwinder
automatically adjusting
inner balloon
tension
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.)
Not-in-force
Application number
EP20110154974
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German (de)
English (en)
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EP2366818A1 (fr
Inventor
Fabio D'agnolo
Giovanni Ghinami
Roberto Badiali
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Savio Macchine Tessili SpA
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Savio Macchine Tessili SpA
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Publication of EP2366818A1 publication Critical patent/EP2366818A1/fr
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Publication of EP2366818B1 publication Critical patent/EP2366818B1/fr
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Classifications

    • D—TEXTILES; PAPER
    • D01—NATURAL OR MAN-MADE THREADS OR FIBRES; SPINNING
    • D01H—SPINNING OR TWISTING
    • D01H7/00—Spinning or twisting arrangements
    • D01H7/02—Spinning or twisting arrangements for imparting permanent twist
    • D01H7/88—Hollow-spindle arrangements
    • D—TEXTILES; PAPER
    • D01—NATURAL OR MAN-MADE THREADS OR FIBRES; SPINNING
    • D01H—SPINNING OR TWISTING
    • D01H13/00—Other common constructional features, details or accessories
    • D01H13/10—Tension devices
    • D01H13/104—Regulating tension by devices acting on running yarn and not associated with supply or take-up devices
    • D01H13/106—Regulating tension by devices acting on running yarn and not associated with supply or take-up devices for double-twist spindle

Definitions

  • the present invention refers to a four-twist spindle for twisting machines and in particular to a device for adjusting the tension in the yarn for feeding a four-twist spindle, as known from EP 2, 028, 300 A .
  • the twisting spindle for multiple twists of textile yarns and threads comprises a basket support 10 that contains a feeding reel 11 and which is held still using, for example, stationary magnets M.
  • the reel 11 is prepared separately using doubled yarns wound in a doubler machine on a reel which is then brought to the twisting frame.
  • the four-twist spindle further comprises two parts rotating in the opposite direction, respectively a more inner upper rotating part 15 and a lower rotating part 16, both arranged beneath the fixed reel-bearing basket 10, the rotating parts 15 and 16 being coaxial to each other and with respect to the axis of the spindle, and an unwinder and transmission element 20 arranged above the reel 11.
  • the yarn F which is unwound by the reel first passes through the unwinder element 20 which ends with the transmission element 21 arranged above the reel, then descends towards the inner upper rotating part 15 defining - around the reel - an inner balloon B, enters in said upper rotating part 15 with the radial conduit 28, it is deflected by the roller 29 and traverses an axial passage 30 provided in said inner upper rotating part 15.
  • the yarn Upon reaching the exit of said passage 30, arranged on the rotational axis of the spindle, the yarn traverses a second transmission element 31, integral with the lower rotating part 16, and thus a radial passage 32 provided within said lower rotating part 16, exits from the latter and rises defining an outer balloon B', reaching a final transmission element 33 and lastly it is conveyed to pick-up means at an upper position.
  • pick-up means not shown in the figure for the sake of simplicity, draw at a constant and predetermined speed - and collect in a reel - the yarn which was processed in the four-twist spindle.
  • the yarn receives two twist actions which sum-up and, more precisely receives two twists for each revolution of each of the two rotating parts 15 and 16.
  • the lower rotating part 16 is supported by a stationary bearing 14 which supports the entire four-twist spindle and it is actuated by outer motion transmission means, for example through a pulley 17 coaxial to the spindle which receives the rotary motion with a transmission belt.
  • the lower rotating part 16 in turn transmits motion to the upper rotating part 15, for example through an epicycloidal transmission device 18, according to the abovementioned patent application EP 1.726.693 on behalf of the applicant, to which reference shall be made for further details.
  • Such epicycloidal device 18 is contained within a fixed box part 19, also held locked with fixed magnets mounted on the bottom of the basket 10.
  • an unwinder device 20 which receives the doubled yarn F from the reel 11.
  • Such unwinder 20 is mounted on the inner shaft 13 of the basket 10 with the interposition of a roller bearing 22.
  • the entire unwinder 20 is rotated by the same doubled yarn F which is spiral unwound by the reel 11, passes into the end ring of the rotating arm 23 and enters into the axial cavity 24 of the unwinder 20 which re-ascends the unwinder itself up to the bell-shaped transmission element 21 arranged at its top.
  • the linear unwinding speed is determined by the draw exerted by the pick-up unit arranged downstream, which also determines the hourly quantity of twisted yarn production.
  • an element 25 for tensioning the yarn is arranged within the cavity 24 .
  • an elastic piston 26 having a spring therein which presses the doubled yarn F against two annular seats 27 arranged at the two upper and lower rounded ends of the piston 26.
  • Such tensioner 25 corresponds to the need that both ends of the doubled yarn F reach the transmission 21 perfectly parallel and having a certain tension. In the undesired case that, during the preliminary doubling operation of the yarn F, one of the two ends results slack and in the twisting there is a slot of the yarn projecting, this would represent an unacceptable defect of the twisted yarn.
  • the tensioner 25 is therefore an equalizer of the doubled yarn F in order to prevent going beyond a possible slack end present in the doubled yarns.
  • One characteristic of the spindle consists in the fact that the yarn, for at least one part of its course, can form free balloons B and B' that are not delimited externally.
  • the four-twist spindle receives its single rotational drive from the axial shaft of the lower rotating part 16, for example through the pulley 17 to rotate at 10,000 rpm.
  • the epicycloidal transmission device 18 transmits motion to the upper rotating part 15 with a speed of about 50%: the upper part in turn rotates, for example, at 5000 rpm.
  • the yarn F Since, as mentioned previously, during its run the yarn F receives two twists for each revolution of each of the two rotating parts, for each work minute the doubled yarn that passes receives 10,000 revolutions twice from the rotating part 16 and 5000 revolutions twice from the rotating part 15, i.e. 30,000 total rpm. If regarding the yarn F a twisting of 600 twists per linear meter is required, in the four-twist spindle it is thus possible to process 50 metres of yarn F per minute, by actuating the device downstream of the pick-up with a draw of 50 m/min.
  • the prevailing part of the tensions present on the yarn is however due to the centrifugal force of the balloons of the yarn which rotate at a high speed, and the technical problem regarding the stability of the balloon derives not so much from the value of the yarn tension but from its irregularity due to the unwinding of the yarn F from the feeding reel 11.
  • the tension of the yarn F depends, besides from the centrifugal force of the balloon, also on the unwinding geometry, i.e. from the angles that the yarn F being unwound obtains with the arm 23 and with the reel 11. These angles vary both depending on the unwinding point and depending on the diameter of the reel 11.
  • the yarn F is removed from the reel 11 immobile in its basket, from which, for example, 50 metres per minute are unwound.
  • the angular coordinate of the pick-up point of the yarn on the reel rotates at a speed which increases slowly proportionally to the consumption of the reel 11, while the level of the pick-up point has a top-bottom excursion and vice versa, thus periodically varying the length of the section of yarn that runs between the pick-up point and the end ring of the rotating arm 23, as well as the angular displacement between them.
  • the unwinding speed of the yarn at 50 m/min corresponds to a few tenths of turns unwound per minute: the yarn F slowly rotates around the reel with spiral progression.
  • the abovementioned 50 m/min of linear speed of the unwinding yarn reach hundreds of turns unwound per minute: the yarn F rotates quickly around the reel 11 still with spiral progression and with an analogous tension pulse.
  • the arm 23 and the entire unwinder 20 rotate at a pulsating speed and, due to their inertia, they give an amplifying effect of the resisting tension pulsation of the yarn F during its unwinding.
  • the yarn F upon exit from the axial duct 24 of the unwinder 20 the yarn F lies on the transmission device 21 and it is deflected downwards by the draw exerted by the upper rotating part 15 and starts to form the inner balloon B driven into rotation at a high speed, for example 5000 rpm.
  • the bell-shaped transmission device 21 of figure 1 and 2 receives the yarn from the axial duct 24 of the unwinder 20 - which rotates in the opposite direction with respect to the rotation of the balloon B at a reduced speed, between a few tenths of rpm at the beginning of the reel 11 and a few hundreds of rpm.
  • the relative rotational speed - between the two sections of the yarn respectively arriving from the end ring of the arm 23 of the unwinder 20 and exiting from the bell-shaped transmission 21 - is the sum of the two rotational speeds.
  • the yarn not only slides on the bell-shaped element at a speed of tens of metres/min in the longitudinal direction, but also rotates by sliding on the bell-shaped element itself drawn by the balloon B, which for example rotates at 5000 rpm: due to the friction between the yarn and the surface of the bell-shaped element 21, the bell-shaped transmission element 21 is drawn by the yarn and it tends to rotate at a speed close to that of the balloon.
  • the trend of the instantaneous tension of the yarn over time in its path for re-ascending towards the upper transmission 21 is shown - by way of example - by the solid line TI of figure 3 , from the beginning to the end of the reel 11.
  • the trend of the average tension of the yarn is instead shown by the dash and dot line TM.
  • the instantaneous tension pulsates irregularly and averagely increasing from the beginning to the end. Such overall tension is the result of all the forces and resistances offered by the yarn and by the system in motion from the pick-up point up to the entrance into the radial conduit 28.
  • the inner balloon B has not a compensating pulley due to lack of space and the geometry of the system. Due to the reasons outlined above the yarn of the inner balloon B naturally has a pulsating tension which causes the instability of the balloon. Due to such reason, the inner balloon B continuously varies its shape and size. The tension of the inner balloon B cannot be too high or too low. Extremely low tensions can cause interferences between the two balloons B and B', but the greatest hazard lies in the excess of tension. An excess of tension of the descending balloon B can reduce the winding of the reserve of the second balloon B' around the surface 36 moving it to the condition of instability.
  • the double-twist spindle has a lower compensating pulley capable of absorbing the tension and length variation of the outer balloon which re-ascends upwards, varying the development angle of the balloon rotating around such pulley.
  • a double-twist spindle provided with a lubricating liquid dispenser on the processed yarn.
  • an upper bell-shaped deflecting element in which however the yarn enters rotating from above and descends axially into the central cavity.
  • Such upper bell-shaped element cannot rotate, due to the fact that it is fixed in position using O-rings, in turn held in peripheral grooves, which also serve as sealing elements for the lubricating liquid.
  • the guide of the feeding yarn arranged on a rotating arm which follows the unwinding of the yarn from the feeding reel is also provided. However, such arm is idle and it is not provided with any braking device. No braking device, neither for the upper fixed bell-shaped element nor for the unwinder arm, is described in such documents in that it is a double-twist spindle which does not require it.
  • the tension of unwinding of the yarn from the reel 11 is not regular. Therefore, as previously explained, the unwinding tension averagely increases from the beginning to the end of the reel, same case applying to the speed of rotation of the unwinder, which may vary from the initial 50-100 rpm to the final 500-600 rpm, increasing by 3-4 times, according to the ratio between the initial and final diameters of the reel.
  • the periodical excursion of the pick-up point of the yarn F from the reel 11 generates, as mentioned, a tension pulse due to the unwinding geometry; due to its inertia, the unwinder 20 has the harmful effect of amplifying such tension pulse.
  • the arm 23 of the unwinder 20 is subjected to an acceleration, passes the pick-up point of the yarn and, given the absence of the yarn to pull it, rotates free due to its inertia, while when the reel 11 surpasses the lower pick-up point, the opposite occurs i.e. the pick-up point of the yarn passes the arm 23 of the unwinder 20 and rotates it again.
  • the yarn F should transmit an additional rotary torque thereto to return it to the operating speed: these effects of surpassing and restarting the drawing of the unwinder 20 therefore generate further tearings on the yarn F which sum to the tension pulses leading to unwanted effects.
  • the reduction of the diameter of the reel 11 causes the increase of the average unwinding tension and the average rotational speed of the unwinder 20, while the unwinding tension variations between the upper and the lower part of the reel 11 cause sudden periodic accelerations and decelerations of the rotary motion of the unwinder 20.
  • the technical problem regards the braking of the system to reduce such speed variations caused by the unwinder 20 and the effect on the tension pulses correlated thereto, so as to avoid excessive tension variations with ensuing interferences of the balloons B and B' and unwanted breakages.
  • Document EP 2.028.301 describes a technical solution which introduces on the path for the re-ascending of the yarn a thread tightener which operates by varying the length of the path of the yarn between the end ring of the rotating arm 23 and the bell-shaped transmission element 21 arranged at the top of the unwinder 20.
  • Document EP 2.028.300 instead provides for making the bell-shaped transmission element 21 idle with respect to the unwinder 20 and providing the unwinder with a magnetic brake arranged on the fixed part.
  • Such brake allows reducing the angular speed variations of the unwinder 20 due to the non-constant draw of the yarn picked up by the reel 11, but induces a supplementary and constant tension in the yarn.
  • the present invention aims at providing a device for braking the system capable of overcoming the performance offered by the prior art devices and capable of allowing controlling the trend and tension of the inner balloon B at the point where the yarn picked up from the reel 11 arrives at the bell-shaped transmission element 21 and constitutes the beginning of said balloon, causing a friction effect of the bell-shaped transmission element 21 on the unwinder 20 and thus modulating the relative rotational speed between said elements.
  • the device according to the invention meets the needs of reducing the tension variations of the yarn entering the inner balloon B due to the tension pulses of unwinding the yarn from the feeding reel and the rotary speed of the unwinder, which are inherent to the system and thus not eliminable.
  • the unwinder device 50 according to the present invention, and illustrated in figure 4 , is made according to the present description regarding the lower part, i.e. the arm 23, the inner axial cavity 24 with tensioner 25 of the yarn F, which consists in an elastic piston 26 which presses the yarn against two annular seats 27 arranged at the two upper and lower rounded ends of the piston 26.
  • a preferred embodiment of the present invention provides that in the reel-bearing basket 10 a reel 11 is arranged with a winding direction of the doubled yarn F preferably matching the direction of rotation of the inner balloon B, so that the unwinding thereof during the spindle functioning is opposite with respect to the rotation of the inner balloon B.
  • a ball bearing 52 is inserted, fitted at the top of the body 53 that contains the axial cavity 24 for ensuring the independence of rotation of the bell-shaped transmission element 51 with respect to the underlying unwinder 50, which rotate in opposite direction with respect to each other summing the rotational speed of the inner balloon B and the angular speed of unwinding the reel 11, which corresponds to the rotational speed of the unwinder 50.
  • a distinctive characteristic of the present invention lies in the introduction of a braking element between the body of the unwinder and the upper bell-shaped deflecting element which reduces the tension pulses and relative speed due to the unwinding of the feeding yarn.
  • annular gasket 60 is inserted in the space available between the deflecting element 51 and the unwinder 50, free to execute small axial and radial movements with respect to said two elements: it can thus rotate at speeds different than those of the unwinder 50 and of the bell-shaped deflecting element 51.
  • Such annular gasket 60 due to its weight, lies with its lower face on the top of the body 53, and in particular on the upper face of the ring 54 for locking the bearing 52, and it can have - due to the radial movement freedom thereof - a more or less extensive contact with the inner face of the bell-shaped deflecting element 51.
  • the braking effect induced by the annular gasket 60 is exerted both on the unwinder 50 and on the deflecting element 51, when such gasket 60 rotates at a speed different from such elements.
  • the intensity of the braking effect of the gasket 60 on the unwinder 50 directly depends on the difference of speed between them, also considering the relative direction of rotation. Same case applies to the braking effect exerted by the gasket 60 on the bell-shaped deflecting element 51.
  • the annular gasket 60 is made using material resistant to wear, with low coefficients of friction, low density and high elasticity. It can be made with felt of natural and synthetic fibres, or with polymer-based plastic materials, sintered or foamed, for example with fluorinated polymers such as teflon or with polyolefin such as polyethylene.
  • the annular gasket 60 can be made in open form or closed form.
  • the left closed form is more suitable with the gaskets made of softer material while, when the gasket is made of stiffer material, in the right open form the gasket is interrupted with a cut 61, made in its circumference, so as to allow easy assembly and replacement thereof.
  • the gasket 60 as the rotary speed of the deflecting element 51 increases, is drawn thereby by friction and centrifuged against the inner surface of the deflecting element 51.
  • this leads to two effects: due to the centrifugal thrust there increases both the contact area of the upper edge of the gasket 60 against the inner surface of the deflecting element 51 and the number of fibres of the felt or of particles of plastic material that are at contact against the inner surface of the deflecting element 51.
  • the result is that the braking action caused on the deflecting element 51 and on the unwinder 50 increases as the relative speed of the deflecting element 51 and of the ring 54 increases. Higher speeds correspond to greater braking force and vice versa.
  • the inner surface of the bell-shaped deflecting element 51 and upper surface of the ring 54 must be sufficiently smooth, preferably with roughness not exceeding 1.2 micrometres, so as to limit the wear on the annular gasket 60.
  • the bell-shaped deflecting element 51 rotates at variable speeds which are caused by the speed of the inner balloon B, which generally rotates at 4000-5000 rpm; the unwinder 50 rotates at lower speeds, not exceeding 500-600 rpm.
  • the speeds of said two elements 50 and 51 are opposite and thus they sum with respect to the ring gasket 60.
  • the bell-shaped deflecting element 51 does not rotate at a constant speed: the speed thereof depends on the tension of the yarn. As mentioned above, due to the friction between the yarn and the outer surface of the deflecting element 51, generated by the tension of the yarn, the deflecting element 51 is drawn by the yarn and tends to rotate at a speed close to that of the balloon.
  • the tension of the yarn is high - like in the case of large counts under processing, or high pick-up speed, or at the end of the reel - the friction between the yarn and deflecting element 51 increases, the torque transmitted from the yarn to the deflecting element 51 increases and the deflecting element 51 rotates at a speed closer to that of the balloon B, even in the presence of the increasing braking exerted by the annular gasket 60.
  • the bell-shaped deflecting element 51 slides with respect to the rotating yarn of the balloon and reduces speed thereof, rotating at a speed considerably lower than that of the balloon B, due to the braking effect exerted by the annular gasket 60.
  • the outer surface of the rotary bell-shaped deflecting element 51 is made with a discrete coefficient of friction, so that the yarn rotated at the speed of the balloon B, which for example rotates at 5000 rpm, exerts an efficient drawing on the bell-shaped deflecting element 51.
  • Values of coefficient of friction for the outer surface of the bell-shaped deflecting element 51 comprised between 0.1 and 0.3 are generally suitable for providing the invention.
  • the kinetic energy for drawing the deflecting element 51 is provided by the rotation of the balloon of the yarn, in turn generated by the drive system which keeps the spindle rotating at a constant speed.
  • the unwinder 50 it is forced to follow the unwinding of the yarn.
  • the tension to which the unwinder is subjected corresponds to the torque that must be provided to it to keep it in rotation to overcome the resistance due to frictions.
  • the yarn In the transient phases, as explained previously, during the deceleration of the unwinder, the yarn should transmit an additional rotary torque thereto to return it to the operational speed.
  • the functioning of the braking system constituted by the annular gasket 60 slack and interposed between the deflecting element 51 and the unwinder 50 can be explained as follows.
  • the degree of braking action depends on the sum of the two rotational speeds and on the friction of the gasket 60: the gasket 60, free to move radially and lying on the upper surface of the ring 54, has an upper edge lying against the inner surface of the deflecting element 51, and thus the braking action occurs through the relative sliding between two rotating parts.
  • the friction action between these counter-rotating components has the effect of dissipating kinetic energy and thus causing the braking action.
  • the kinetic energy dissipated during the braking action is obviously provided by the rotation of the balloon of the yarn, in turn generated by the drive system which keeps the spindle rotating constantly. Then, given that the bell-shaped deflecting element 51 still rotates at speeds much higher than those of the unwinder 50, its kinetic energy is always greater than that of the unwinder and the braking action is mainly exerted on the unwinder 50.
  • the rotary accelerations of the bell-shaped deflecting element 51 and of the unwinder 50 caused by an increase of tension of the yarn F, produce an increase of the sum of the two rotary speeds and, hence, due to the friction of the annular gasket 60 the braking action on the two counter-rotating elements increases.
  • the rotary decelerations of the bell-shaped deflecting element 51 and of the unwinder 50 caused by the reduction of tension of the yarn F, produce a reduction of the sum of the two rotational speeds and, hence, due to the friction of the annular gasket 60 the braking action on the two counter-rotating elements reduces.
  • the unwinder 50 rotates at a low speed and the average tension of the yarn is low, the bell-shaped deflecting element 51 thus rotates at a lower speed with respect to the rotation of the balloon B: the braking action of the system - which is proportional to the sum of the speeds - is thus low.
  • the unwinder 50 rotates at high speed and the average tension of the yarn is high, the bell-shaped deflecting element 51 thus rotates at a high speed drawn by the rotation of the balloon B: the braking action of the system - which is proportional to the sum of the speeds - is thus high.
  • the interposition of the annular gasket 60 between the unwinder 50 and the bell-shaped deflecting element 51 thus has the effect of reducing abrupt variations of the rotation of the unwinder 50 and thus reducing excessive tension variations which can generate interferences of the balloons and breakage of the yarn.
  • the braking system according to the invention is applied to the bell-shaped deflecting element 51 with respect to the unwinder 50 and it is of the adjusting and self-compensating type: it is of the adjusting type due to the fact that its average braking action increases as the diameter of the feeding reel 11 reduces; it is self-compensating due to the fact that it counters the speed variations of the unwinder 50 in the transients, which cause abrupt tension variations and unwanted breaking of the yarn.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Textile Engineering (AREA)
  • Spinning Or Twisting Of Yarns (AREA)
  • Emergency Protection Circuit Devices (AREA)
  • Coupling Device And Connection With Printed Circuit (AREA)
  • Control Of Voltage And Current In General (AREA)

Claims (15)

  1. Dispositif pour régler automatiquement la tension d'entrée de fil à l'intérieur du ballon interne (B) dans des broches à quatre torsions, dans lequel un fil retors (F) pour l'alimentation dans la broche à quatre torsions (10) est déroulé d'une bobine d'alimentation fixe (11) à travers un dérouleur rotatif (50) équipé d'un bras radial (23) tournant suivant le déroulement du fil d'alimentation (F), dans lequel le dérouleur rotatif (50) a une cavité axiale interne (24) pour la remontée du fil (F) qui arrive de l'anneau d'extrémité du bras rotatif (23) et qui passe à travers ladite cavité jusqu'à un élément de déviation de transmission en forme de cloche (51), à partir duquel commence le ballon interne (B) de la broche à quatre torsions (10), dans lequel un tel élément de déviation en forme de cloche (51) est rendu indépendant par rapport au dérouleur (50) au-dessous, l'indépendance de rotation de l'élément en forme de cloche (51) étant obtenue avec un palier à bille (52), installé au sommet du corps (53) qui contient la cavité axiale (24), caractérisé en ce que, entre le corps du dérouleur (50) et l'élément de déviation en forme de cloche (51) est agencé un élément de freinage qui consiste en un joint annulaire (60), disposé sur le dessus du dérouleur (50) et en contact avec l'élément de déviation en forme de cloche (51).
  2. Dispositif pour régler automatiquement la tension d'entrée de fil à l'intérieur du ballon interne (B) dans des broches à quatre torsions selon la revendication 1, caractérisé en ce que la direction d'enroulement de la bobine (11) de fil retors (F) correspond à la direction de rotation du ballon interne (B), de manière que son déroulement durant le fonctionnement de la broche soit dans le sens opposé à la rotation du ballon interne (B).
  3. Dispositif pour régler automatiquement la tension d'entrée de fil à l'intérieur du ballon interne (B) dans des broches à quatre torsions selon la revendication 1, caractérisé en ce que le joint annulaire (60) travaille, respectivement, avec sa face inférieure constamment en appui sur la face supérieure de l'anneau (54) pour bloquer le palier (52) sur le dérouleur (50) et, du côté opposé, avec sa face supérieure en contact avec la face intérieure de l'élément de déviation en forme de cloche (51).
  4. Dispositif pour régler automatiquement la tension d'entrée de fil à l'intérieur du ballon interne (B) dans des broches à quatre torsions selon la revendication 1, caractérisé en ce que le joint annulaire (60) n'a pas de contraintes axiales et est radialement labile par rapport au dérouleur (50).
  5. Dispositif pour régler automatiquement la tension d'entrée de fil à l'intérieur du ballon interne (B) dans des broches à quatre torsions selon la revendication 1, caractérisé en ce que le joint annulaire (60) est centrifugé contre la surface intérieure de l'élément de déviation (51).
  6. Dispositif pour régler automatiquement la tension d'entrée de fil à l'intérieur du ballon interne (B) dans des broches à quatre torsions selon la revendication 5, caractérisé en ce que le joint annulaire (60) centrifugé contre la surface intérieure de l'élément de déviation (51) a un contact et un nombre de points de contact contre la surface intérieure de l'élément de déviation en forme de cloche (51) augmentant lorsque la somme des vitesses de rotation de l'élément de déviation en forme de cloche (51) et du dérouleur (50) augmente.
  7. Dispositif pour régler automatiquement la tension d'entrée de fil à l'intérieur du ballon interne (B) dans des broches à quatre torsions selon la revendication 6, caractérisé en ce que l'augmentation de la surface de contact et du nombre de points de contact du joint annulaire (60) contre la surface intérieure de l'élément de déviation en forme de cloche (51) et contre la face supérieure de l'anneau de blocage (54) du dérouleur (50) entraîne une force de frottement augmentant lorsque la somme des vitesses relatives des deux éléments (50) et (51) augmente.
  8. Dispositif pour régler automatiquement la tension d'entrée de fil à l'intérieur du ballon interne (B) dans des broches à quatre torsions selon la revendication 1, caractérisé en ce que le joint annulaire (60) est réalisé à partir de feutre de fibres naturelles ou synthétiques.
  9. Dispositif pour régler automatiquement la tension d'entrée de fil à l'intérieur du ballon interne (B) dans des broches à quatre torsions selon la revendication 1, caractérisé en ce que le joint annulaire (60) est réalisé avec des matières plastiques à base de polymère.
  10. Dispositif pour régler automatiquement la tension d'entrée de fil à l'intérieur du ballon interne (B) dans des broches à quatre torsions selon la revendication 9, caractérisé en ce que le joint annulaire (60) est réalisé avec des polymères fluorés.
  11. Dispositif pour régler automatiquement la tension d'entrée de fil à l'intérieur du ballon interne (B) dans des broches à quatre torsions selon la revendication 9, caractérisé en ce que le joint annulaire (60) est réalisé avec des polymères oléfines.
  12. Dispositif pour régler automatiquement la tension d'entrée de fil à l'intérieur du ballon interne (B) dans des broches à quatre torsions selon la revendication 1, caractérisé en ce que les surfaces intérieures de l'élément de déviation en forme de cloche (51) et la surface supérieure de l'anneau de blocage (54) ont une rugosité inférieure à 1,2 micromètres.
  13. Dispositif pour régler automatiquement la tension d'entrée de fil à l'intérieur du ballon interne (B) dans des broches à quatre torsions selon la revendication 1, caractérisé en ce que les valeurs de coefficient de frottement de la surface extérieure de l'élément de déviation en forme de cloche (51) avec le fil (F) sont entre 0,1 et 0,3.
  14. Dispositif pour régler automatiquement la tension d'entrée de fil à l'intérieur du ballon interne (B) dans des broches à quatre torsions selon la revendication 1, caractérisé en ce que le joint annulaire (60) est réalisé sous forme fermée.
  15. Dispositif pour régler automatiquement la tension d'entrée de fil à l'intérieur du ballon interne (B) dans des broches à quatre torsions selon la revendication 1, caractérisé en ce que le joint annulaire est réalisé sous forme ouverte, en effectuant une découpe (61) dans sa circonférence.
EP20110154974 2010-02-22 2011-02-18 Dispositif pour régler automatiquement la tension d'alimentation de fil de broches à quatre torsions Not-in-force EP2366818B1 (fr)

Applications Claiming Priority (1)

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ITMI2010A000274A IT1398310B1 (it) 2010-02-22 2010-02-22 Dispositivo di autoregolazione della tensione del filo di alimentazione dei fusi a quattro torsioni

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EP2366818A1 EP2366818A1 (fr) 2011-09-21
EP2366818B1 true EP2366818B1 (fr) 2012-12-19

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CN106757577A (zh) * 2016-12-31 2017-05-31 山西海利普电子科技有限公司 一种用于环锭纺纱机的主动旋转式吊锭
CN109112685B (zh) * 2018-09-07 2019-11-12 苏州涵轩信息科技有限公司 一种球式张力器
CN109930253A (zh) * 2019-04-04 2019-06-25 杭州长翼纺织机械有限公司 一种一步法复合捻线机
CN112853556A (zh) * 2021-01-25 2021-05-28 浙江日发纺机技术有限公司 一种四倍捻锭子张力调节装置

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62110931A (ja) 1985-11-11 1987-05-22 Murata Mach Ltd 二重撚糸機における潤滑液の塗布装置
JPS63162877A (ja) 1986-12-26 1988-07-06 Toshiba Corp 結晶性グラフアイトの製造方法
JPS63162877U (fr) * 1987-04-09 1988-10-24
IT1295565B1 (it) 1997-06-05 1999-05-13 Agnolo Armando D Fuso per torsioni multiple
JPH11323675A (ja) * 1998-05-11 1999-11-26 Murata Mach Ltd 多重撚糸機
EP1045053A1 (fr) 1999-04-05 2000-10-18 Murata Kikai Kabushiki Kaisha Ailette et méthode pour l'entrainer
JP2001226839A (ja) * 2000-02-08 2001-08-21 Murata Mach Ltd 単錘駆動型多重撚糸機
CN1554814A (zh) * 2003-12-27 2004-12-15 刘光容 纺纱机中的纱线倍捻加捻机构及其倍捻加捻方法
CN100412248C (zh) * 2004-10-29 2008-08-20 绍兴县华裕纺机有限公司 纱线四倍捻加捻装置
ITMI20050974A1 (it) 2005-05-26 2006-11-27 Savio Macchine Tessili Spa Fuso a quattro torsioni per macchine di ritorcitura o simili
ITMI20071578A1 (it) * 2007-08-01 2009-02-02 Savio Macchine Tessili Spa Dispositivo di controllo e riduzione del le pulsazioni di tensione nell'alimentaz ione dei fusi a quattro torsioni
ITMI20071579A1 (it) 2007-08-01 2009-02-02 Savio Macchine Tessili Spa Dispositivo di compensazione delle pulsazioni di tensione nei fusi a quattr o torsioni

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CN102162158B (zh) 2014-12-17
IT1398310B1 (it) 2013-02-22
EP2366818A1 (fr) 2011-09-21
CN102162158A (zh) 2011-08-24
ITMI20100274A1 (it) 2011-08-23

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