EP1948855B1 - Metier a filer a anneaux pourvu de systemes d'etirage - Google Patents

Metier a filer a anneaux pourvu de systemes d'etirage Download PDF

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Publication number
EP1948855B1
EP1948855B1 EP06818513.1A EP06818513A EP1948855B1 EP 1948855 B1 EP1948855 B1 EP 1948855B1 EP 06818513 A EP06818513 A EP 06818513A EP 1948855 B1 EP1948855 B1 EP 1948855B1
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EP
European Patent Office
Prior art keywords
frame
drawing frame
ring spinning
rotor
drafting
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
EP06818513.1A
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German (de)
English (en)
Other versions
EP1948855A2 (fr
Inventor
Peter Mann
Hermann Güttler
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.)
Saurer Spinning Solutions GmbH and Co KG
Original Assignee
Saurer Germany GmbH and Co KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from DE200510054818 external-priority patent/DE102005054818A1/de
Priority claimed from DE200510054826 external-priority patent/DE102005054826B4/de
Priority claimed from DE200510054817 external-priority patent/DE102005054817A1/de
Application filed by Saurer Germany GmbH and Co KG filed Critical Saurer Germany GmbH and Co KG
Publication of EP1948855A2 publication Critical patent/EP1948855A2/fr
Application granted granted Critical
Publication of EP1948855B1 publication Critical patent/EP1948855B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • D—TEXTILES; PAPER
    • D01—NATURAL OR MAN-MADE THREADS OR FIBRES; SPINNING
    • D01H—SPINNING OR TWISTING
    • D01H1/00—Spinning or twisting machines in which the product is wound-up continuously
    • D01H1/14—Details
    • D01H1/20—Driving or stopping arrangements
    • D01H1/22—Driving or stopping arrangements for rollers of drafting machines; Roller speed control

Definitions

  • the invention relates to a ring spinning machine with drafting systems, which have a plurality of draw rolls.
  • terminal coupling gear can be very long drafting with, for example, 750 and more jobs in the central region of the workstations torsional sagging of the drafting rollers occur that can cause at least distortion in the yarn produced.
  • a drafting arrangement has become known in which at least one of the drafting sub-rollers is driven at more than two driving locations along its length.
  • drives are helical or helical gear or linear motors ( FIGS. 1 to 3 ) intended. It is obvious that the wheels (27, 29, 31) shown in the drafting system in a small mutual, determined by the processed fiber length distance space found. This is very expensive.
  • the invention was therefore based on the object to provide a device by means of which in a simple manner between the ends of very long drafting rollers whose torsion preventing or at least reducing torques can be initiated.
  • a preferred embodiment provides that the drafting of a short base ring spinning machine, in which no torsion occurs in the drafting system, is provided with a drafting device main drive device, which covers the torque requirement of this drafting system. At each ring spinning machine, which has a greater length than the base ring spinning machine, the additional torque requirement for speed-accurate drive of the drafting rollers is covered by a corresponding number of drafting roller auxiliary drive devices.
  • the drive motors of the drafting roller auxiliary drive devices can be designed as rotary field magnets, as speed-controlled or speed-controlled asynchronous motors or as synchronous motors or reluctance motors.
  • rotary field magnets and variable-speed asynchronous motors offer the advantage that in many cases they do not require a function-dependent change in the application of feed energy.
  • draw roller auxiliary drive devices can be easily inserted at any points in a drafting, they can be provided in any and each draw roll in different numbers. They can be equipped with low power, which accommodates their narrow design.
  • the gearboxes of the drafting roller auxiliary drive devices can be designed to be identical for all drafting rollers.
  • the speeds of the input roller and the output roller are usually very different, it may be advantageous to maintain at least for these two drafting rollers draw roller auxiliary drive devices with gearbox with different reduction ratios.
  • the center roller which has to move the straps, which has to overcome high resistance when sliding over the deflecting edges of the Riemchenkafige, equipped with draw roller auxiliary drive devices.
  • draw roller auxiliary drive devices it is advisable to provide on all drafting rollers of a drafting system with draw roller auxiliary drive devices. The rotational speeds of the drafting rollers driven by these drafting roller auxiliary drive devices are then still determined by the drafting system main drive device.
  • the intention is to run the draw roller auxiliary drive devices on the arrival and departure of the drafting system drive speed up and down run. This avoids distortion errors during start-up and at the outlet of the drafting system.
  • the drafting rollers are not driven by a gear train, but by separate, exactly speed-controlled (synchronous) motors, have a power supply device that feed these motors with the appropriate frequencies.
  • the drive motors of the draw roller auxiliary drive devices are subjected to frequencies corresponding to or derived from the frequencies of the associated draw roller motors. Since in this case the exact, causing the delays speeds of the drafting rollers are determined by the synchronous drive motors of the drafting rollers, is sufficient in most cases the use of Asynchronous motors on the draw roller auxiliary drive devices to reduce their torsion by introducing torque sufficiently.
  • draw roller auxiliary drive devices may also be equipped with synchronous or reluctance motors.
  • the draft roller and the center roller are driven by separate synchronous motors on drafting systems, while the input roller is driven by gear translation of the center roller, since the bias between input roller and center roller is rarely changed.
  • the drive motors of the draw roller auxiliary drive devices of the output and center rollers could be acted upon by frequencies derived from the (master) frequencies of the master motor of the center roller.
  • a drafting roller to torsion i. to balance it at least approximately. This can be done by the number of draw rollers associated with a draw roller auxiliary drive devices, by the action of the draw roller auxiliary drive devices with electrical energy, in particular their feed frequency or supply voltage or by the transmitted torque.
  • supply frequency or supply voltage can also be adapted to the operating state of a draw roller: it can be temporarily increased during startup of a machine or higher at higher speeds.
  • draw roller auxiliary drive devices can be easily inserted at any points and / or in any number in a drafting system, they can be equipped with low power, which accommodates their narrow design. They can also be executed uniformly - they can be used in larger numbers if the torque requirement is higher.
  • a draw roller auxiliary drive device is thus preferably arranged between the second and third riffelfeld lying to the right or left of a punch.
  • the free allocation to drafting rollers also makes it possible, if several drafting rollers are to be provided with such drafting roller auxiliary drive devices, to insert them between staggered workstations of the drafting rollers.
  • the drafting roller auxiliary drive devices must be mounted so as to receive the reaction momentum of the transmitted energy.
  • they are therefore fastened to the punches or the roller bearing carriage assigned to the punches. As a result, it is unnecessary that they must be readjusted when changing the roll distance.
  • the possible plurality of drafting roller auxiliary drive devices along the drafting rollers can also reduce the diameters of the drafting rollers, if desirable, without the risk of increased torsion with the adverse consequences thereof.
  • draw roller auxiliary drive devices have transfer members between a drive member and a draw roller, they may be housed in a closed housing for protection against runoff of the draw roller auxiliary drive devices and contamination of the machined material.
  • the stretch roller auxiliary drive devices may be used as drive motors in the form of synchronous motors, which may also be designed as reluctance motors, or of variable speed asynchronous motors.
  • maximizing the axial length of both the stator and rotor causes both components to fully occupy the clearance between two adjacent corrugated fields by eliminating bearings provided on either side of the stator and rotor or by making these bearings as narrow as possible form.
  • Minimizing the outside diameter of the stand implies that it takes full advantage of the smallest pitch available for adjacent draw rolls. This is possible because the diameter of the draw roll roller carrying the draw roll motor is reduced in the region in which the runner is mounted on it. As a result, not only the electromotive components can be moved further inward, but also those of the stator. Since the inclination of the drafting roller for torsion by the stretched roller motors used is avoided or reduced.
  • the drafting rollers in drafting systems have an extremely low impact for textile technology reasons. Out-of-roundness in the course of the drafting rollers would lead to periodic distortion errors and impair the quality of the yarn produced until it is useless. The straightening of the draw rolls to exact concentricity without impact represents a separate operation in their production.
  • one of the draw roll sections may comprise a cylindrical stud on which the runner may be secured. When a thread connects to this pin with which the draw roll section can be screwed into the subsequent draw roll section, the runner is clamped on this pin.
  • the stator of the drafting roller motor preferably has no bearings. It is attached to a fixed component, which is a carrier of the drafting equipment, a carrier the carrying and loading arms or a strap turn bar can act. It is preferably a component which contains a bearing of the draw roll to which the draw roll motor is assigned.
  • the stand can be arranged on a punch of the drafting system or on a roller carriage of one of the output roller upstream drafting rollers.
  • stator and rotor require a precise axial position of the two motor parts to each other.
  • the stand is adjustable to the runner and adjustable attached to the component.
  • a Einstelllehre is proposed in a further embodiment of the invention, by means of which the stator is aligned very precisely to the rotor and fastened in this position on the component provided for this purpose.
  • two identical setting gauges are provided, which are insertable from both end sides of the engine forth in the annular gap between the stator and rotor.
  • the annular gap between the stator and rotor can be provided with a seal.
  • the motor is arranged at a greater distance from the punch or a roller carriage and, accordingly, its attachment has a large projection, the motor can be provided on one side with a support bearing. It does not have the task to store the engine, but only to prevent accidental unilateral loading of the stand comes into contact with the runner.
  • bearings are arranged in the rotary gap between the stator and rotor, which can be made weak, since no radial or axial forces occur between the stator and rotor.
  • This offers the advantage that the stand does not have to be fixed and does not need to be adjusted and can not touch the runner.
  • the stand only has to be supported on a non-rotatable component in order to apply the reaction to the torque. This may be, for example, to the support bar of Unterriemchen-tension brackets.
  • FIGS. 1 to 3 The drawings show the starting areas of three drafting rollers A2, A3 and A4 from a drafting system A1, which extend even further to the right. They are stored in punches A5 at regular intervals. In the embodiments of the Figures 1 and 2 they are drivingly connected to one another in a form-locking manner at their left end by a drafting device main drive device A6 in the form of a change gear train A8 driven by an electric motor A7.
  • the change-gear transmission gives the drafting rollers angular accuracy to the revolutions, in order to reach between the rollers the default draft stages.
  • the drive motor A7 is energized from the network A9.
  • the grid also powers a power supply A10 which powers drive motors A11 of draw roller auxiliary drive devices A12.
  • the draw roller auxiliary drive devices engage and transmit torque to transfer rollers A13 on the lower rollers A2, A3, A4.
  • the power supply device 10 is connected via separate lines A14, A15, A16 to the drive motors A11, so that they can act on these with different supply voltage and / or supply frequency.
  • the drafting roller auxiliary drive devices A12 exert only torque on the drafting rollers. In the simplest embodiment, therefore, they can be rotary field magnets which assist the rotational movement imparted to the drafting rollers by the gearbox A8 and thereby reduce the torsion of the rollers. Greater or lesser torque can be achieved by different supply voltage and / or supply frequency.
  • the speed sensor A17, A18, A19 whose outputs are connected to the power supply device A10.
  • it can act on the drive motors A11 of the draw roller auxiliary drive devices A12 speed-controlled, so that they drive the draw rolls at the intended speed.
  • the population of the various drafting rollers A2, A3, A4 may be different with drafting roller auxiliary drive devices A12. It is believed that the torsion of the middle lower roll A3 is higher than that of the others, as it must tow the slips that are slidingly guided over deflections. It is therefore, for example, provided on every second punch A5 with a draw roller auxiliary drive devices A12, while the other bottom rollers, for example, only on every third punch such.
  • the draw rolls A2, A3, A4 each have a synchronous motor A20, A21, A22 as drafting main drive device A6.
  • the power supply device A10 feeds this synchronous motors with those supply frequencies, are driven by the drafting rollers exactly with the intended speeds. With these frequencies, the drive motors A11 of the drafting roller auxiliary drive devices A12 designed as synchronous motors are also acted upon here and driven synchronously.
  • FIG. 4 In FIG. 4 are sections of three bottom rollers B1, B2 and B3 of a drafting B4 shown, which are mounted in a punch B5. To the right of the punch is a support and loading arm B6 recognizable in which three upper roller twins B7, B8 and B9 are mounted, which press on the lower rollers. To the left of the punch is another support and loading arm B6 recognizable, whose upper coil twins are however broken away. In the main drafting zone between the lower rollers B2 and B3 a Riemchen turn rail B10 is located.
  • FIG. 5 can be seen below the output roller pair B3 / B9 via an arm B11 of the drive motor B12 a draw roller auxiliary drive device B13 attached to the punch B5.
  • the drive motor drives via a spur gear B14 designed as StirnradVorgelege transmission member B15, the other spur gear B16 sits on the lower roller B3.
  • the transfer member engages a portion of the lower roller B3, which lies between the twin upper roller B9 of the left support and loading arm B6 and the twin top roller of the next support and load arm, not shown, left. This prevents the transmission member B15 from coming into contact with a support and loading arm B6.
  • the spur gear B14 / B16 of a draw roller auxiliary drive device B13 is advantageously accommodated in a dust-tight housing B17.
  • the draw roller auxiliary drive device B13 assigned to the middle roller pair B2 / B8 is fastened to the right of the punch B5 on the roller carriage assigned to this roller pair and engages the bottom roller B2 in addition to the twin top roller B8. Thereby, it is avoided that the transfer members B15 of the two draw roller auxiliary drive devices B13 associated with each other adjacent lower rollers interfere with each other when the roller pairs B2 / B8 and B3 / B9 are brought close to each other at a small distance.
  • the draw roller auxiliary drive device B13 assigned to the input roller pair B1 / B7 is again arranged to the left of the punch B5 on the roller carriage assigned to this roller pair.
  • the arrangement on the roller carriage has the advantage that the draw roller auxiliary drive devices B13 migrate with an adjustment of the roll spacing and require no special adjustment.
  • the transfer members B15 of the draw roller auxiliary drive devices B13 are designed so narrow that they can engage between adjacent Riffelfeldern B18 a draw roller to this without a rifflange and thus a job of the drafting would have to be omitted.
  • the drafting roller auxiliary drive devices B13 can be inserted as a result of their narrow construction between virtually any desired work stations of a drafting system, there is the advantage that they can be made small and with low power. A required performance can be achieved by appropriate number of pieces.
  • draw roller auxiliary drive devices B13 to be attached to a lower roller B1, B2, B3 can be adjusted in their number of units to the tendency of the draw roller to torsion. There is no use of full-performance drafting roller auxiliary drive devices.
  • the distance between two work stations of a drafting system B4 corresponding to the pitch T of the ring spinning machine is too small to allow engagement of the transfer member B15 of a drafting roller auxiliary drive device B13.
  • the distances between three working points of the drafting system are reduced on the one hand to a distance t 2 and increased to a distance t 1 .
  • the draw rolls auxiliary driving device B13 may be mounted between the corrugating fields B18.
  • the attack of the drafting roller auxiliary drive device B13 is advantageously carried out at the connection points of the roller sections. As can be seen from FIG. B6, not every connection point has to be equipped with an auxiliary drive device.
  • FIG. 7 the increase in the distance can be distributed over two adjacent Riffelfeldabrepresented.
  • the distance 3T of three rifling fields is divided into two reduced distances t 4 and a more extended distance t 3 , in which a wider draw roller auxiliary drive device B13 is arranged.
  • Two threads B20 run obliquely to the thread guides B21.
  • the draw roller motor C1 is inserted between two rifling fields C2, C3 of two sections C4, C5 of a lower roller C6 of a drafting system.
  • This can be any lower roller of a drafting system.
  • the axial length L of the drafting roller motor is so small that the given pitch T of the work stations of the drafting system and the ring spinning machine need not be increased.
  • the drafting roller motor C1 has a rotor C7 and a stator C8.
  • the runner C7 is mounted on the draw roller C6. This can - as in FIG. 8 indicated by the fact that the roller portion C4 has a cylindrical pin C9 with subsequent threaded pin C10, by means of which it can be screwed into a bore of the roller portion C5.
  • the bush-shaped rotor then lies on the cylindrical pin C9 and is clamped between the roller sections C4, C5.
  • FIG. 9 a solution is shown in which the drum-shaped rotor has on both sides of two retaining pins C11, by means of which it can be inserted or screwed non-positively into bores of the adjacent roller sections C4 and C5.
  • the rotor C7 can also be divided in an axis-parallel plane and be placed and fastened on the area between two Riffelfeldern C2, C3.
  • the runner C7 is so long that its end faces abut directly on the subsequent Riffelfeldern C2, C3.
  • the available space between the adjacent Riffelfeldern is thus maximally utilized by the torque-applying parts stator C8 and rotor C7.
  • the stand C8 has no bearings. It has a tab C12, by means of which it is usually fastened via a spacer C13 indicated by only with their center lines C14 screws to a non-rotatable member C15 which is connected to a bearing C16 of the lower roller C6.
  • this involves the punch of the drafting system or roller carriages which are displaceable on this punch and which also contain bearings of drafting rollers.
  • the connection with a roller carriage has the advantage that the connection of the stator to the component does not have to be readjusted when a draw roller is displaced when changing roller distances.
  • the stand can also be connected to another, stationary, non-rotatable component.
  • the drafting system can be provided with a separate holding device for the stands C8.
  • the draw roller motor C1 itself, as mentioned, does not have its own bearings.
  • the traveler C7 is mounted on the rotary draw roll C6, the stand C8 is fixed to a component C15 which is advantageously in firm contact with a bearing C16 of the draw roll C6 associated with the draw roll motor.
  • the draw rolls of ring spinning machines have such a small impact that even in this way a very narrow gap between the stator C8 and rotor C7 is possible and an accurate concentricity of the drafting roller motor is ensured.
  • FIG. 13 For example, illustrated setting gauge C17 provided. It has a handle C18 and on a circular arm C19 three offset by 120 °, the course of the gap C20 between stator 8C and rotor C7 corresponding, wedge-shaped tabs C21. These tabs will, as in FIG. 12 indicated, pressed in the direction of the arrow P in the gap C20 and thereby center the stand to the runner.
  • two setting gauges are provided, whose tabs C21 can be inserted from both sides into the column C20. In the thus achieved coaxial position of the stator to the rotor former can be attached to the stationary or rotationally fixed component C15.
  • seals C22 can be provided around the two gaps C20 between stator C8 and rotor C7.
  • the seals are preferably formed as a felt ring and can lie in grooves C23 of the stator or the rotor.
  • the drafting roller motor C1 can not be arranged directly next to the punching element C15, since there is a corrugated field there. He can attack between the two by the first top roller twins C24 next to the punch operated jobs on a drafting roller C6 and sits on the short spacer C13. However, since he often intervenes in the area of the axes of the upper roller twins C24 or the Oberwalzentrag- and loading arm C25, he often has to be moved into an intermediate riffler field on. For this purpose, a long spacer C26 is required, which can project the drafting roller engine far.
  • a clearance bearing C27 may be provided between the stator C8 and the rotor C7, which prevents touching sensitive parts of the drafting roller motor in case of unintentional one-sided loading of the stator C8.
  • the spacer bearing C27 is not used to support the rotor C7 in the stator or the stator 8 on the rotor, but only to comply with the distance or gap C20 between the stator and rotor.
  • the spacer bearing C27 is shown as a ball bearing.
  • the distance bearing can also be designed as a sliding bearing. Due to its arrangement in the gap C20 between stator C8 and rotor C7, it requires no bearing plate and can even be kept so narrow that it does not extend the length of the engine significantly.
  • FIG. 10 shows an embodiment in which two bearings C28 are provided in the gap C20 between the rotatable with the draw roll C6 runners C7 and the non-rotatably supported stand C8. Since the forces occurring between rotor and stator are small, the bearings can be made narrow and accordingly reduce the achievable torque only slightly.
  • the stator C8 mounted on the rotor C7 must be supported on a non-rotatable component in order to apply the reaction force of the drafting roller motor C1.
  • this is the handrail C29 of the strapping clamp C30.
  • the tab C12 on the stand engages around the support bar like a fork. When displacing the draw roller C6, the tab C12 remains engaged with the support bar C29.
  • the embodiment may be such that the stator C8 has narrow terminal sheet-shaped end shields C31 in which are also arranged narrow bearings C32 running on the drafting roller C6.
  • the end shields C31 are so narrow that they do not reduce the electromotive forces between stator C8 and rotor C7.
  • it may be provided to reduce the diameter of the cylindrical pin C9 on which the rotor C7 is mounted.
  • the diameter of the drafting roller motor C1 is expanded to some extent inwardly, the components of the rotor slip inwards and those of the stator can also be expanded inwards.
  • the outer diameter of the stator 8 is kept at a minimum level and yet maximizes the torque output by the drafting roller motor C1.
  • the invention can be practiced with all types of electric motors suitable for driving drafting rollers: synchronous and reluctance motors, variable speed or non-speed controlled asynchronous motors, stepping motors, rotary solenoids.
  • the feeding of their stand is done for speed adjustment, preferably with controlled frequency.
  • the stator includes field windings, the rotor permanent magnets, which are not shown in detail in the figures, rotor C7 and stator C8 are indicated in the figures only by hatching.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Textile Engineering (AREA)
  • Spinning Or Twisting Of Yarns (AREA)
  • Shaping Metal By Deep-Drawing, Or The Like (AREA)

Claims (19)

  1. Metier à filer à anneaux comprenant des trains d'étirage à plusieurs cylindres d'étirage dont les cylindres supérieurs prennent la forme de cylindres jumeaux chargés par des bras de support et de chargement et où chaque cylindre d'étirage possède plusieurs dispositifs d'entraînement auxiliaires espacés mutuellement, caractérisé en ce que l'espacement (t1) entre deux postes de travail voisins dans le sens longitudinal du train d'étirage (B4), dans lequel un dispositif d'entraînement auxiliaire (B13) s'engage dans un cylindre inférieur (B3), est augmenté de telle sorte, et l'espacement (t2) avec le poste de travail voisin suivant du train d'étirage est diminué de telle sorte, que l'espacement total entre les trois postes de travail voisins correspond au double de l'espacement normal (T) entre deux postes de travail.
  2. Metier à filer à anneaux comprenant des trains d'étirage à plusieurs cylindres d'étirage dont les cylindres supérieurs prennent la forme de cylindres supérieurs jumeaux chargés par des bras de support et de chargement et où chaque cylindre d'étirage possède plusieurs dispositifs d'entraînement auxiliaires espacés les uns des autres, caractérisé en ce que l'espacement (t3) entre deux postes de travail voisins dans le sens longitudinal du train d'étirage (B4), dans lequel un dispositif d'entraînement auxiliaire (B13) s'engage dans un cylindre inférieur (B3), est augmenté de telle sorte, et l'espacement (t4) entre les deux postes de travail voisins du train d'étirage est diminué de telle sorte, que l'espacement total entre les quatre postes de travail voisins correspond au triple de l'espacement normal (T) entre deux postes de travail.
  3. Metier à filer à anneaux selon la revendication 1 ou 2 caractérisé en ce que les dispositifs d'entraînement auxiliaires (B13) des cylindres d'étirage entre les postes de travail s'engagent dans les cylindres d'étirage (B1, B2, B3) disposés en quinconce dans le sens longitudinal du metier à filer.
  4. Metier à filer à anneaux selon l'une des revendications 1 à 3 comprenant des supports de palier servant à entreposer les cylindres d'étirage et des chariots pour cylindre d'étirage, caractérisé en ce que les dispositifs d'entraînement auxiliaires (B13) des cylindres d'étirage sont fixés aux supports de palier (B5) et aux chariots pour cylindre d'étirage pouvant coulisser dans les supports de palier.
  5. Metier à filer à anneaux selon la revendication 4 caractérisé en ce que les dispositifs d'entraînement auxiliaires (B13) de cylindres d'étirage voisins (B1/B2, B2/B3) sont disposés alternativement à droite et à gauche sur un support de palier (B5) et sur le chariot pour cylindre d'étirage pouvant coulisser dans le support de palier.
  6. Metier à filer à anneaux selon une ou plusieurs des revendications 1 à 5 caractérisé en ce que les dispositifs d'entraînement auxiliaires (B13) des cylindres d'étirage et/ou leurs organes de transmission (B15) sur les cylindres d'étirage (B1, B2, B3) sont logés dans un boîtier (B17) encapsulant, de préférence hermétique à la poussière.
  7. Metier à filer à anneaux comprenant un moteur de cylindre d'étirage, avec stator et rotor, destiné à être disposé sur et entre les cylindres d'étirage, caractérisé en ce que le moteur de cylindre d'étirage est logé entre deux pièces ondulées (C2, C3) d'un cylindre d'étirage (C6) voisines et dans l'espacement d'un cylindre d'étirage voisin ainsi que par l'absence de flasques, de sorte que le rotor (C7) du moteur de cylindre d'étirage (C1) est fixé directement sur le cylindre d'étirage (C6) auquel il est affecté et le stator (C8) du moteur (C1) est fixé et appuyé contre un élément fixe en rotation (C15, C29) du train d'étirage.
  8. Metier à filer à anneaux selon la revendication 7 caractérisé en ce que le rotor (C7) du moteur de cylindre d'étirage (C1) est fixé directement sur le cylindre d'étirage (C6) auquel il est affecté et le moteur de cylindre d'étirage (C1) possède seulement un palier (C27) dans l'intervalle de rotation (C20) servant à maintenir l'écart entre le stator (C8) et le rotor (C7) afin d'éviter que ces derniers ne se touchent.
  9. Metier à filer à anneaux selon la revendication 7 caractérisé en ce que le rotor (C7) du moteur de cylindre d'étirage (C1) est fixé directement sur le cylindre d'étirage (C6) auquel il est affecté et le moteur de cylindre d'étirage (C1) possède, dans l'intervalle (C20) entre le stator (C8) et le rotor (C7), des paliers (C28) qui servent à entreposer le stator sur le rotor et où le moteur de cylindre d'étirage est appuyé contre un élément fixe en rotation (C29) du train d'étirage.
  10. Metier à filer à anneaux selon la revendication 7 caractérisé en ce que le rotor (C7) du moteur de cylindre d'étirage (C1) est fixé directement sur le cylindre d'étirage (C6) auquel il est affecté et en ce que le cylindre d'étirage présente un diamètre (d) réduit dans la zone où le rotor est fixé sur lui.
  11. Metier à filer à anneaux selon la revendication 10 caractérisé en ce que une section de la chaîne de cylindre (C4) du cylindre d'étirage (C6) entre deux pièces ondulées (C2, C3) possède un logement cylindrique (C9) servant à fixer le rotor (C7) du moteur de cylindre d'étirage (C1) et peut être vissée dans une section de cylindre (C5) s'y raccordant au moyen d'un filetage (C10) rejoignant le logement cylindrique.
  12. Metier à filer à anneaux selon la revendication 10 caractérisé en ce que le rotor (C7) du moteur de cylindre d'étirage (C1) possède des goujons dépassant des deux côtés enfichables dans les sections de chaîne de cylindre (C4, C5) rejoignant les alésages.
  13. Metier à filer à anneaux selon la revendication 8 caractérisé en ce que l'élément fixe en rotation (C15) contient un palier (C16) pour le cylindre d'étirage (C6).
  14. Metier à filer à anneaux selon la revendication 9 caractérisé en ce que l'élément fixe en rotation est un support (C15) du train d'étirage ou un chariot de cylindre entreposé dans un support.
  15. Metier à filer à anneaux selon la revendication 8 caractérisé en ce que l'élément est une barre (C29) qui tient l'étrier tendeur (C30) de la courroie inférieure.
  16. Metier à filer à anneaux selon la revendication 8 caractérisé en ce que l'élément fixe en rotation prend la forme d'un rail orientable de courroie inférieure.
  17. Metier à filer à anneaux selon la revendication 7 caractérisé en ce que le rotor (C7) et le stator (C8) occupent aussi complètement que possible l'écart libre entre deux pièces ondulées (C2, C3) d'un cylindre d'étirage (C6) voisines.
  18. Metier à filer à anneaux selon la revendication 8 caractérisé en ce que le stator (C8) du moteur (C1) sur l'élément (C15) possédant un palier (C16) du cylindre d'étirage (C6) peut être déplacé et réglé de manière coaxiale par rapport au rotor.
  19. Metier à filer à anneaux selon une ou plusieurs des revendications 7 à 18 caractérisé en ce que des joints d'étanchéité (C22) sont disposés dans les intervalles (C20) existant entre le stator (C8) et le rotor (C7) afin d'empêcher l'infiltration de poussière et de fibres à l'intérieur du moteur (C1).
EP06818513.1A 2005-11-15 2006-11-14 Metier a filer a anneaux pourvu de systemes d'etirage Not-in-force EP1948855B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE200510054818 DE102005054818A1 (de) 2005-11-15 2005-11-15 Streckwalzen-Motor
DE200510054826 DE102005054826B4 (de) 2005-11-15 2005-11-15 Ringspinnmaschine mit Streckwerken
DE200510054817 DE102005054817A1 (de) 2005-11-15 2005-11-15 Ringspinnmaschine mit Streckwerken
PCT/EP2006/010889 WO2007057148A2 (fr) 2005-11-15 2006-11-14 Metier a filer a anneaux pourvu de systemes d'etirage

Publications (2)

Publication Number Publication Date
EP1948855A2 EP1948855A2 (fr) 2008-07-30
EP1948855B1 true EP1948855B1 (fr) 2018-08-29

Family

ID=37685137

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06818513.1A Not-in-force EP1948855B1 (fr) 2005-11-15 2006-11-14 Metier a filer a anneaux pourvu de systemes d'etirage

Country Status (3)

Country Link
EP (1) EP1948855B1 (fr)
JP (1) JP5189492B2 (fr)
WO (1) WO2007057148A2 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015010854A1 (de) 2015-08-19 2017-02-23 Saurer Germany Gmbh & Co. Kg Spinnmaschine mit einer Vielzahl nebeneinander angeordneter Streckwerke
DE102018102232A1 (de) * 2018-02-01 2019-08-01 Saurer Spinning Solutions Gmbh & Co. Kg Doppelseitige Ringspinnmaschine mit Streckwerken
IT201900003983A1 (it) 2019-03-19 2020-09-19 Marzoli Machines Textile Srl Filatoio a cintino

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2641434B2 (de) * 1976-09-15 1979-04-26 Zinser Textilmaschinen Gmbh, 7333 Ebersbach Lange Spinnmaschine
DE4014608C1 (en) * 1990-05-07 1991-11-14 Zinser Textilmaschinen Gmbh, 7333 Ebersbach, De Slow running direct drive for spinning machine - incorporates multiphase slip-ring rotor engine where stator coils have 1st frequency converter and rotor coils have 2nd frequency converter
DE10040420A1 (de) * 2000-08-18 2002-02-28 Rieter Ag Maschf Streckwerksanordnung für Spinnmaschinen

Also Published As

Publication number Publication date
JP5189492B2 (ja) 2013-04-24
WO2007057148A2 (fr) 2007-05-24
JP2009516085A (ja) 2009-04-16
EP1948855A2 (fr) 2008-07-30
WO2007057148A3 (fr) 2007-07-26

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