EP2730686B1 - Open-end spinning rotor - Google Patents

Open-end spinning rotor Download PDF

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Publication number
EP2730686B1
EP2730686B1 EP13004898.6A EP13004898A EP2730686B1 EP 2730686 B1 EP2730686 B1 EP 2730686B1 EP 13004898 A EP13004898 A EP 13004898A EP 2730686 B1 EP2730686 B1 EP 2730686B1
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EP
European Patent Office
Prior art keywords
rotor
cylindrical bore
open
end spinning
accordance
Prior art date
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Revoked
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EP13004898.6A
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German (de)
French (fr)
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EP2730686A1 (en
Inventor
Heinz-Georg Wassenhoven
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Saurer Spinning Solutions GmbH and Co KG
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Saurer Germany GmbH and Co KG
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Publication of EP2730686A1 publication Critical patent/EP2730686A1/en
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    • D—TEXTILES; PAPER
    • D01—NATURAL OR MAN-MADE THREADS OR FIBRES; SPINNING
    • D01H—SPINNING OR TWISTING
    • D01H4/00—Open-end spinning machines or arrangements for imparting twist to independently moving fibres separated from slivers; Piecing arrangements therefor; Covering endless core threads with fibres by open-end spinning techniques
    • D01H4/04—Open-end spinning machines or arrangements for imparting twist to independently moving fibres separated from slivers; Piecing arrangements therefor; Covering endless core threads with fibres by open-end spinning techniques imparting twist by contact of fibres with a running surface
    • D01H4/08—Rotor spinning, i.e. the running surface being provided by a rotor
    • D01H4/10—Rotors

Definitions

  • the invention relates to an open-end spinning rotor comprising a rotor shaft, a rotor cup and a coupling device which releasably connects the rotor shaft and the rotor cup.
  • the coupling device has locking means for axially locking the rotor cup, transmission means for the positive transmission of torque from the rotor shaft to the rotor cup, and additionally centering means for centering the rotor shaft and the rotor cup.
  • the centering means comprise a cylindrical bore and a corresponding guide lug, which is insertable into the cylindrical bore.
  • Spinning rotors used in open-end rotor spinning machines must be interchangeable as needed, for example when worn or to produce another type of yarn on the rotor spinning machine. Depending on the type of storage, it may make the change of open-end spinning rotors difficult or even impossible if the rotor cup and the rotor shaft are permanently connected to each other. Therefore, a number of considerations have already been made as to how the connection between rotor cup and rotor shaft can be made detachable. In addition to the simple interchangeability of the rotor cup is the safe connection during operation of the spinning rotor in the foreground. It should be noted that the spinning rotor is operated at speeds of 150,000 revolutions per minute and more. There are known rotor spinning machines, which reach up to 200,000 revolutions per minute.
  • the cylindrical bore should enclose the guide lug without play.
  • a backlash-free connection is not possible due to the ever-present manufacturing tolerances.
  • a game between the cylindrical bore and the guide lug will always be necessary.
  • imbalance forces that can damage the drive and / or the bearing of the spinning rotor can arise at the high rotational speeds with which the spinning rotor rotates.
  • the unbalance is caused by the misalignment between rotor cup and rotor shaft.
  • the DE 10 2009 048 295 A1 also discloses a spinning rotor having a rotor cup and a rotor shaft. These are detachably connected to each other.
  • the rotor shaft has a bore and the rotor cup a stub shaft, which is insertable into the bore.
  • a spring element is arranged to be tensioned during insertion of the stub shaft into the bore so that a torque is transmitted from the rotor shaft to the rotor cup.
  • a non-positive torque transmission does not have the required reliability. To imbalance forces makes the Scripture no statement.
  • the EP 0 808 923 A1 discloses an open-end spinning rotor, consisting of a rotor cup and a receiving this receiving part over which the rotor cup is stored and driven. Rotortasse and carrier part are connected by a clip connection. A part of the clip connection is received via an elastic element. As a result, the necessary deformability of the clip connection for assembly is achieved.
  • the elastic element is also intended to damp vibrations generated by an unbalance of the rotor mass. An axial offset of rotor cup and carrier part or rotor shaft can not be prevented by the disclosed construction.
  • the DE 38 15 182 A1 discloses various coupling devices for releasably connecting rotor shaft and rotor cup. It is proposed, inter alia, consisting of an elastic material centering, which is mounted between an attached to the rotor cup coupling pin and connected to the rotor shaft coupling shell.
  • the diameter of the coupling pin is significantly smaller than the diameter of the coupling shell.
  • the space between pin and shell is filled exclusively by the elastic centering. It is doubtful that the centering accuracy required for modern rotor spinning machines can be achieved in this way.
  • the spinning rotor of EP 1 156 142 B1 develop so that the rotor cup can be easily replaced and at the same time a reliable centering of rotor cup and rotor shaft is achieved.
  • the cylindrical bore and the guide lug on a clearance fit and the centering means comprise a resilient arrangement which is located between the cylindrical bore and the guide lug.
  • the game between the cylindrical bore and the guide lug is smaller than 0.1 mm according to the invention. In this area, one can assume that the centering can be reliably enabled by means of the elastic arrangement.
  • the centering is improved the less the clearance between the bore and guide approach.
  • the production cost increases the tighter the chosen tolerances are.
  • the tolerances are chosen so that the clearance between the cylindrical bore and the guide lug is less than 0.01 mm. Such tolerances can be produced realistically and the centering by the elastic arrangement is optimal.
  • the extent of the elastic arrangement in the axial direction of the cylindrical bore is greater than 0.8 times the diameter of the cylindrical bore.
  • the manufacturing accuracy of the elastic arrangement is limited. This is especially true when the elastic assembly is integrally formed and has a greater length. Therefore, advantageously, the extension of the elastic assembly in the axial direction of the cylindrical bore is less than 2.4 times the diameter of the cylindrical bore.
  • the elastic assembly comprises an elastic member. It is possible to use only a single elastic element. That is, the elastic assembly is integrally formed.
  • the elastic arrangement comprises a second elastic element, which is arranged in the axial direction of the cylindrical bore spaced from the first elastic element.
  • the elastic element may be formed, for example, as a tolerance sleeve.
  • the tolerance sleeve may be formed as a corrugated band and consist of spring band steel.
  • the elastic element may also be formed as an O-ring.
  • O-rings are used axially spaced from each other.
  • two tolerance sleeves it is also possible to use two tolerance sleeves in this way.
  • the centering can be improved if in the cylindrical bore or the guide lug there is a circumferential recess in which the elastic element is inserted.
  • the Fig. 1 and the Fig. 2 show a spinning rotor 1 with a coupling device 3 as in the prior art, for example, from the above-cited EP 1 156 142 B1 known.
  • the two figures are intended to explain the problems which are overcome by the present invention.
  • the FIGS. 1 and 2 Both show the same spinning rotor 1, so that this will be described only once.
  • the spinning rotor 1 comprises a rotor cup 2 and a rotor shaft 4, which are connected to one another via a coupling device 3.
  • the rotor shaft 4 is mounted in a suitable, not shown storage and connected to a drive, not shown.
  • the drive sets the rotor shaft 4 and thus the spinning rotor 1 in rotation.
  • the rotor cup 2 has an approach.
  • the approach is divided into a cylindrical guide projection 7 and a positive locking element 9.
  • the positive-locking element 9 is formed as an external polygon.
  • the rotor shaft 4 has a cylindrical bore 8, which corresponds to the cylindrical guide projection 7.
  • the rotor shaft 4 has a form-locking element 10 which is designed as an internal polygon and which corresponds with the form-fitting element 9.
  • the interlocking elements 9 and 10 create a positive connection between the rotor cup 2 and the rotor shaft 4, so that a torque can be transmitted.
  • the rotor shaft 4 has a magnet 5, which adjoins the polygonal socket on. The magnet 5 exerts an attraction on the ferromagnetic approach of the rotor cup 2.
  • the magnetic attraction forces are sufficient.
  • Fig. 1 are also the axes 16 and 17 located.
  • the axis 16 is the axis of symmetry of the rotor cup 2.
  • the axis 17 illustrates the axis of symmetry of the rotor shaft 4. Due to the play between the cylindrical bore 8 and the guide projection 7, the axes on an offset e. This offset e leads to an imbalance of the spinning rotor. This imbalance can be up to 200,000 min -1 lead to damage of the bearing or of the drive at rotational speeds.
  • the axes are offset parallel to each other.
  • Fig. 2 shows the same spinning rotor 1 as Fig.
  • the axes 16 and 17 are not offset from each other in parallel, but rotor shaft 4 and rotor cup 2 are tilted against each other.
  • the axes 16 and 17 of rotor cup 2 and rotor shaft 4 have an angular offset.
  • the angular offset also arises due to the clearance between the rotor shaft 4 and rotor cup 2 and leads to an imbalance of the system with the disadvantages described above.
  • the Fig. 3 shows a spinning rotor 1a according to the invention.
  • the rotor cup 2 with the rotor cup 2 of FIGS. 1 and 2 identical.
  • the rotor shaft 4a has, corresponding to the rotor shaft 4, a cylindrical bore 8, an internal polygon 10 and a magnet 5 for the axial locking of the rotor cup 2.
  • the coupling device 3a of the spinning rotor 1a still differs from the coupling device 3 of the spinning rotor 1.
  • two O-rings 13 and 14 are additionally arranged.
  • two recesses 18 and 19 are provided, in which the O-rings 13 and 14 are inserted.
  • the two O-rings form an elastic arrangement.
  • the extent of the elastic arrangement in the axial direction of the cylindrical bore is in Fig. 3 denoted by l a .
  • the diameter of the cylindrical bore 8 is denoted by d. If the extent l a in relation to the diameter d is sufficiently large, an angular offset between the axes of the rotor cup 2 and the rotor shaft 4 a can be prevented.
  • the extent l a must be at least 80% of the diameter d.
  • FIGS. 4 and 5 show an alternative embodiment of the present invention.
  • the difference between the spinning rotor 1b and the spinning rotor 1a lies in the fact that the coupling device 3b has a different elastic arrangement.
  • the rotor shaft 4b has on the circumference of the cylindrical bore 8 a recess 20b.
  • a tolerance sleeve 15b is applied.
  • Fig. 5 a section through the tolerance sleeve along the section line AA.
  • the Fig. 5 shows that the tolerance sleeve 15b is formed as a corrugated band.
  • the corrugated band can be made of spring band steel.
  • the elastic arrangement consists of the elastic element, namely the tolerance sleeve 15b.
  • the length l b of the tolerance sleeve 15b corresponds to the extent of the elastic arrangement in the axial direction of the cylindrical bore.
  • the length l b is also chosen here in relation to the diameter d of the cylindrical bore 8 so that an angular offset is avoided.
  • the spinning rotor 1c includes a rotor cup 2c, a clutch device 3c and a rotor shaft 4c.
  • the rotor shaft 4 does not have a cylindrical bore 8, but the rotor cup 2c has a cylindrical bore 8c.
  • the rotor shaft 4c has a guide lug 7c corresponding thereto. In the guide projection 7c, a circumferential recess 20c is introduced.
  • the tolerance sleeve 15c can be arranged to center the rotor cup 2c and rotor shaft 4c.
  • the rotor shaft 4c has a positive-locking element 11.
  • the rotor cup 2c comprises a form-fitting element 12 corresponding thereto
  • Fig. 7 shows the section BB with the two form-fitting elements 11 and 12.
  • the positive-locking elements 11 and 12 have a circular cylindrical shape with two flat surfaces on the circumference. Other shapes are possible.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Textile Engineering (AREA)
  • Spinning Or Twisting Of Yarns (AREA)

Description

Die Erfindung betrifft einen Offenend-Spinnrotor, der einen Rotorschaft, eine Rotortasse und eine Kupplungseinrichtung, die den Rotorschaft und die Rotortasse lösbar verbindet, umfasst. Die Kupplungseinrichtung weist Arretierungsmittel zur axialen Arretierung der Rotortasse, Übertragungsmittel zur formschlüssigen Übertragung eines Drehmomentes von dem Rotorschaft auf die Rotortasse und zusätzlich Zentriermittel zur Zentrierung von Rotorschaft und Rotortasse auf. Die Zentriermittel umfassen eine zylindrische Bohrung und einen dazu korrespondierenden Führungsansatz, der in die zylindrische Bohrung einführbar ist.The invention relates to an open-end spinning rotor comprising a rotor shaft, a rotor cup and a coupling device which releasably connects the rotor shaft and the rotor cup. The coupling device has locking means for axially locking the rotor cup, transmission means for the positive transmission of torque from the rotor shaft to the rotor cup, and additionally centering means for centering the rotor shaft and the rotor cup. The centering means comprise a cylindrical bore and a corresponding guide lug, which is insertable into the cylindrical bore.

In Offenend-Rotorspinnmaschinen eingesetzte Spinnrotoren müssen bei Bedarf, zum Beispiel bei Verschleiß oder um einen anderen Garntyp auf der Rotorspinnmaschine zu fertigen, gewechselt werden können. Je nach Art der Lagerung kann es den Wechsel der Offenend-Spinnrotoren erschweren oder gar unmöglich machen, wenn die Rotortasse und der Rotorschaft unlösbar miteinander verbunden sind. Deshalb wurden bereits eine Vielzahl von Überlegungen angestellt, wie die Verbindung zwischen Rotortasse und Rotorschaft lösbar gestaltet werden kann. Neben der einfachen Austauschbarkeit der Rotortasse steht die sichere Verbindung während des Betriebes des Spinnrotors im Vordergrund. Dabei ist zu beachten, dass der Spinnrotor bei Drehzahlen von 150.000 Umdrehungen pro Minute und mehr betrieben wird. Es sind Rotorspinnmaschinen bekannt, die bis zu 200.000 Umdrehungen pro Minute erreichen.Spinning rotors used in open-end rotor spinning machines must be interchangeable as needed, for example when worn or to produce another type of yarn on the rotor spinning machine. Depending on the type of storage, it may make the change of open-end spinning rotors difficult or even impossible if the rotor cup and the rotor shaft are permanently connected to each other. Therefore, a number of considerations have already been made as to how the connection between rotor cup and rotor shaft can be made detachable. In addition to the simple interchangeability of the rotor cup is the safe connection during operation of the spinning rotor in the foreground. It should be noted that the spinning rotor is operated at speeds of 150,000 revolutions per minute and more. There are known rotor spinning machines, which reach up to 200,000 revolutions per minute.

Eine Möglichkeit einer solchen lösbaren Verbindung ist in der EP 1 156 142 B1 beschrieben. Diese wird mittels einer Kupplungsvorrichtung realisiert, die aus einer Magnetlagerung zur axialen Arretierung von Rotorschaft und Rotortasse und einer mechanischen Verdrehsicherung, die über Formschluss jede relative Rotationsbewegung zwischen Rotorschaft und Rotortasse verhindert, besteht. In den Rotorschaft ist eine Aufnahmehülse mittels einer Presspassung eingelassen. Die Aufnahmehülse weist in axialer Richtung hintereinander einen Permanentmagneten, einen Innenmehrkant und eine zylindrische Bohrung auf. Die Rotortasse weist einen Achsstummel beziehungsweise einen Ansatz aus ferromagnetischem Material mit einem Außenmehrkant, der mit dem Innenmehrkant korrespondiert, und einem Führungsansatz, der mit der zylindrischen Bohrung korrespondiert, auf.One possibility of such a detachable connection is in the EP 1 156 142 B1 described. This is realized by means of a coupling device, which consists of a magnetic bearing for axial locking of the rotor shaft and rotor cup and a mechanical anti-rotation, which prevents any relative rotational movement between the rotor shaft and rotor cup over positive engagement exists. In the rotor shaft a receiving sleeve is inserted by means of a press fit. The receiving sleeve has in the axial direction one behind the other a permanent magnet, a polygonal socket and a cylindrical bore. The rotor cup has a stub axle or a projection of ferromagnetic material with an outer polygon, which corresponds to the internal polygon, and a guide lug corresponding to the cylindrical bore, on.

Die zylindrische Bohrung soll den Führungsansatz spielfrei umschließen. Eine solche spielfreie Verbindung ist aufgrund der immer vorhandenen Fertigungstoleranzen jedoch nicht möglich. Um die Austauschbarkeit der Rotortasse zu gewährleisten, wird also immer ein Spiel zwischen der zylindrischen Bohrung und dem Führungsansatz nötig sein. Aber selbst bei einem geringen Spiel, dass sich im Bereich weniger hundertstel Millimeter bewegt, können bei den hohen Drehzahlen, mit denen der Spinnrotor rotiert, Unwuchtkräfte entstehen, die den Antrieb und/oder die Lagerung des Spinnrotors schädigen können. Die Unwucht entsteht dabei durch den Achsversatz zwischen Rotortasse und Rotorschaft.The cylindrical bore should enclose the guide lug without play. However, such a backlash-free connection is not possible due to the ever-present manufacturing tolerances. In order to ensure the interchangeability of the rotor cup, so a game between the cylindrical bore and the guide lug will always be necessary. But even with a small clearance that moves in the range of a few hundredths of a millimeter, imbalance forces that can damage the drive and / or the bearing of the spinning rotor can arise at the high rotational speeds with which the spinning rotor rotates. The unbalance is caused by the misalignment between rotor cup and rotor shaft.

Die DE 10 2009 048 295 A1 offenbart ebenfalls einen Spinnrotor mit einer Rotortasse und einem Rotorschaft. Diese sind lösbar miteinander verbunden. Der Rotorschaft weist eine Bohrung auf und die Rotortasse einen Wellenstumpf, der in die Bohrung einführbar ist. In einer Umfangsnut des Wellenstumpfes oder der Bohrung ist ein Federelement angeordnet, dass beim Einführen des Wellenstumpfes in die Bohrung so gespannt werden soll, dass ein Drehmoment von dem Rotorschaft auf die Rotortasse übertragen wird. Es hat sich jedoch gezeigt, dass eine solche kraftschlüssige Drehmomentübertragung nicht die erforderliche Zuverlässigkeit aufweist. Zu Unwuchtkräften macht die Schrift keine Aussage.The DE 10 2009 048 295 A1 also discloses a spinning rotor having a rotor cup and a rotor shaft. These are detachably connected to each other. The rotor shaft has a bore and the rotor cup a stub shaft, which is insertable into the bore. In a circumferential groove of the stub shaft or the bore, a spring element is arranged to be tensioned during insertion of the stub shaft into the bore so that a torque is transmitted from the rotor shaft to the rotor cup. However, it has been found that such a non-positive torque transmission does not have the required reliability. To imbalance forces makes the Scripture no statement.

Die EP 0 808 923 A1 offenbart einen Offenend-Spinnrotor, bestehend aus einer Rotortasse und einem diese aufnehmenden Trägerteil, über das die Rotortasse gelagert und angetrieben wird. Rotortasse und Trägerteil sind durch eine Klipsverbindung miteinander verbunden. Ein Teil der Klipsverbindung ist über ein elastisches Element aufgenommen. Dadurch wird die nötige Verformbarkeit der Klipsverbindung für die Montage erreicht. Das elastische Element soll außerdem Schwingungen, die durch eine Unwucht der Rotorasse erzeugt werden, dämpfen. Ein Achsversatz von Rotortasse und Trägerteil beziehungsweise Rotorschaft kann durch die offenbarte Konstruktion nicht verhindert werden.The EP 0 808 923 A1 discloses an open-end spinning rotor, consisting of a rotor cup and a receiving this receiving part over which the rotor cup is stored and driven. Rotortasse and carrier part are connected by a clip connection. A part of the clip connection is received via an elastic element. As a result, the necessary deformability of the clip connection for assembly is achieved. The elastic element is also intended to damp vibrations generated by an unbalance of the rotor mass. An axial offset of rotor cup and carrier part or rotor shaft can not be prevented by the disclosed construction.

Die DE 38 15 182 A1 offenbart verschiedene Kupplungseinrichtungen zum lösbaren Verbinden von Rotorschaft und Rotortasse. Es wird unter anderen eine aus elastischem Werkstoff bestehende Zentrierscheibe vorgeschlagen, die zwischen einem an der Rotortasse angesetzten Kupplungszapfen und einer mit dem Rotorschaft verbundenen Kupplungsschale angebracht ist. Der Durchmesser des Kupplungszapfens ist deutlich kleiner als der Durchmesser der Kupplungsschale. Der Zwischenraum zwischen Zapfen und Schale wird ausschließlich durch die elastische Zentrierscheibe ausgefüllt. Es ist zu bezweifeln, dass die für moderne Rotorspinnmaschinen erforderliche Zentriergenauigkeit auf diese Weise erreicht werden kann.The DE 38 15 182 A1 discloses various coupling devices for releasably connecting rotor shaft and rotor cup. It is proposed, inter alia, consisting of an elastic material centering, which is mounted between an attached to the rotor cup coupling pin and connected to the rotor shaft coupling shell. The diameter of the coupling pin is significantly smaller than the diameter of the coupling shell. The space between pin and shell is filled exclusively by the elastic centering. It is doubtful that the centering accuracy required for modern rotor spinning machines can be achieved in this way.

Es ist daher die Aufgabe der vorliegenden Erfindung, den Spinnrotor der EP 1 156 142 B1 so weiterzuentwickeln, dass die Rotortasse leicht ausgetauscht werden kann und gleichzeitig eine zuverlässige Zentrierung von Rotortasse und Rotorschaft erreicht wird.It is therefore the object of the present invention, the spinning rotor of EP 1 156 142 B1 develop so that the rotor cup can be easily replaced and at the same time a reliable centering of rotor cup and rotor shaft is achieved.

Die Aufgabe wird erfindungsgemäß durch die kennzeichnenden Merkmale des Anspruches 1 gelöst. Vorteilhafte Weiterbildungen der Erfindung sind Gegenstand der Unteransprüche.The object is achieved by the characterizing features of claim 1. Advantageous developments of the invention are the subject of the dependent claims.

Zur Lösung der Aufgabe weist die zylindrische Bohrung und der Führungsansatz eine Spielpassung auf und die Zentriermittel umfassen eine elastische Anordnung, die sich zwischen der zylindrischen Bohrung und dem Führungsansatz befindet.To solve the problem, the cylindrical bore and the guide lug on a clearance fit and the centering means comprise a resilient arrangement which is located between the cylindrical bore and the guide lug.

Als Passung wird bekanntermaßen die maßliche Beziehung zwischen zwei gepaarten, toleranzbehafteten Teilen bezeichnet, wobei beide Teile das gleiche Nennmaß aufweisen, jedoch Lage und Größe der Toleranzfelder unterschiedlich sein können. Wenn die vorgegebenen Toleranzen im gesamten Toleranzfeld ein Spiel erlauben, spricht man von einer Spielpassung. Spielpassungen sind leicht zu fertigen und in der ISO-Norm ISO 286 genormt. Definitionsgemäß haben also die zylindrische Bohrung und der Führungsansatz das gleiche Nennmaß. Die Abweichungen liegen in einem engen Toleranzfeld. Die elastische Anordnung, die zwischen der zylindrischen Bohrung und dem Führungsansatz angeordnet ist, muss also nur einen geringen Abstand überbrücken. Die elastische Anordnung kann also in Verbindung mit der Spielpassung eine zuverlässige Zentrierung erreichen. Ein Versatz der Achsen von Rotortasse und Rotorschaft wird weitestgehend vermieden. Die einfache Austauschbarkeit der Rotortasse ist gewährleistet. Zum einen ist ein Spiel zwischen Bohrung und Führungsansatz vorhanden. Zum anderen sind die von der eleatischen Anordnung ausgeübten Kräfte gering, da sie nur der Zentrierung dienen und kein Drehmoment übertragen werden muss. Die Kräfte können also bei einem Wechsel der Rotortasse leicht überwunden werden.As a known fit, the dimensional relationship between two paired, tolerance-bearing parts is referred to, wherein both parts have the same nominal size, but the position and size of the tolerance fields can be different. If the given tolerances allow a clearance in the entire tolerance field, this is called a clearance fit. Game fits are easy to manufacture and standardized in the ISO standard ISO 286. By definition, therefore, the cylindrical bore and the guide lug have the same nominal size. The deviations are within a narrow tolerance range. The elastic arrangement, which is arranged between the cylindrical bore and the guide projection, so only has to bridge a small distance. The elastic arrangement can thus achieve a reliable centering in conjunction with the clearance. An offset of the axes of rotor cup and Rotor shaft is largely avoided. The simple interchangeability of the rotor cup is guaranteed. On the one hand there is a match between bore and guiding approach. On the other hand, the forces exerted by the Eleatic arrangement are low because they only serve for centering and no torque must be transmitted. The forces can thus be easily overcome when changing the rotor cup.

Das Spiel zwischen der zylindrischen Bohrung und dem Führungsansatz ist erfindungsgemäß kleiner als 0,1mm. In diesem Bereich kann man davon ausgehen, dass die Zentrierung mittels der elastischen Anordnung zuverlässig ermöglicht werden kann.The game between the cylindrical bore and the guide lug is smaller than 0.1 mm according to the invention. In this area, one can assume that the centering can be reliably enabled by means of the elastic arrangement.

Es versteht sich, dass die Zentrierung verbessert wird je geringer das Spiel zwischen Bohrung und Führungsansatz ist. Zum anderen steigt der Fertigungsaufwand desto enger die gewählten Toleranzen sind. Gemäß einer bevorzugten Ausführungsform werden die Toleranzen so gewählt, dass das Spiel zwischen der zylindrischen Bohrung und dem Führungsansatz kleiner ist als 0,01mm. Solche Toleranzen lassen sich realistisch fertigen und die Zentrierung durch die elastische Anordnung ist optimal.It is understood that the centering is improved the less the clearance between the bore and guide approach. On the other hand, the production cost increases the tighter the chosen tolerances are. According to a preferred embodiment, the tolerances are chosen so that the clearance between the cylindrical bore and the guide lug is less than 0.01 mm. Such tolerances can be produced realistically and the centering by the elastic arrangement is optimal.

Gemäß einer weiteren vorteilhaften Ausführungsform ist die Ausdehnung der elastischen Anordnung in axialer Richtung der zylindrischen Bohrung größer als das 0,8-fache des Durchmessers der zylindrischen Bohrung. Genau wie bei einem Versatz, bei dem die Achsen von Rotortasse und Rotorschaft parallel zueinander verschoben sind, kann ein Winkelversatz, bei dem sich die Achsen von Rotortasse und Rotorschaft unter einem Winkel schneiden, Unwuchtprobleme hervorrufen. Wenn die elastische Anordnung die beschriebene Längsausdehnung aufweist, kann außerdem ein Winkelversatz zwischen den Achsen von Rotortasse und Rotorschaft vermieden werden.According to a further advantageous embodiment, the extent of the elastic arrangement in the axial direction of the cylindrical bore is greater than 0.8 times the diameter of the cylindrical bore. As with an offset where the rotor cup and rotor shaft axes are displaced parallel to each other, an angular misalignment in which the rotor cup and rotor shaft intersect at an angle can cause imbalance problems. In addition, when the elastic assembly has the longitudinal extent described, angular misalignment between the rotor cup and rotor shaft axes can be avoided.

Auch die Fertigungsgenauigkeit der elastischen Anordnung ist begrenzt. Das gilt insbesondere, wenn die elastische Anordnung einstückig ausgebildet ist und eine größere Länge aufweist. Deshalb ist vorteilhafterweise die Ausdehnung der elastischen Anordnung in axialer Richtung der zylindrischen Bohrung kleiner als das 2,4-fache des Durchmessers der zylindrischen Bohrung.The manufacturing accuracy of the elastic arrangement is limited. This is especially true when the elastic assembly is integrally formed and has a greater length. Therefore, advantageously, the extension of the elastic assembly in the axial direction of the cylindrical bore is less than 2.4 times the diameter of the cylindrical bore.

Gemäß einer Ausführungsform der vorliegenden Erfindung umfasst die elastische Anordnung ein elastisches Element. Es ist möglich, nur ein einzelnes elastisches Element zu verwenden. Das heißt, dass die elastische Anordnung einstückig ausgebildet ist.According to an embodiment of the present invention, the elastic assembly comprises an elastic member. It is possible to use only a single elastic element. That is, the elastic assembly is integrally formed.

Es ist auch möglich, dass die elastische Anordnung ein zweites elastisches Element umfasst, das in axialer Richtung der zylindrischen Bohrung beabstandet von dem ersten elastischen Element angeordnet ist. Durch die Verwendung von zwei Elementen kann mit vergleichsweise kurzen elastischen Elementen eine größere Ausdehnung der elastischen Anordnung in axialer Richtung der zylindrischen Bohrung realisiert werden. Die beiden elastischen Elemente können identisch ausgebildet sein.It is also possible that the elastic arrangement comprises a second elastic element, which is arranged in the axial direction of the cylindrical bore spaced from the first elastic element. By using two elements can be realized with relatively short elastic elements, a greater extent of the elastic arrangement in the axial direction of the cylindrical bore. The two elastic elements can be identical.

Das elastische Element kann zum Beispiel als Toleranzhülse ausgebildet sein. Die Toleranzhülse kann als gewelltes Band ausgebildet sein und aus Federbandstahl bestehen.The elastic element may be formed, for example, as a tolerance sleeve. The tolerance sleeve may be formed as a corrugated band and consist of spring band steel.

Das elastische Element kann auch als O-Ring ausgebildet sein. Verzugsweise werden zwei O-Ringe axial beabstandet zueinander verwendet. Es ist natürlich auch möglich, zwei Toleranzhülsen in dieser Weise zu verwenden.The elastic element may also be formed as an O-ring. Preferably, two O-rings are used axially spaced from each other. Of course, it is also possible to use two tolerance sleeves in this way.

Die Zentrierung kann verbessert werden, wenn in der zylindrischen Bohrung oder dem Führungsansatz ein umlaufender Einstich vorhanden ist, in dem das elastische Element eingesetzt ist.The centering can be improved if in the cylindrical bore or the guide lug there is a circumferential recess in which the elastic element is inserted.

Die Erfindung wird nachfolgend anhand eines in den Zeichnungen dargestellten Ausführungsbeispiels näher erläutert.The invention will be explained in more detail with reference to an embodiment shown in the drawings.

Es zeigen:

Fig. 1
einen Spinnrotor mit einer Kupplungseinrichtung gemäß dem Stand der Technik und einem axialen Versatz von Rotortasse und Rotorschaft;
Fig. 2
der Spinnrotor gemäß Fig. 1 mit einem Winkelversatz zwischen Rotortasse und Rotorschaft;
Fig. 3
einen erfindungsgemäßen Spinnrotor mit O-Ringen;
Fig. 4
einen erfindungsgemäßen Spinnrotor mit einer Toleranzhülse;
Fig. 5
ein Schnittbild der Toleranzhülse aus Fig. 4;
Fig. 6
einen erfindungsgemäßen Spinnrotor mit einer alternativen Kupplungseinrichtung;
Fig. 7
ein Schnittbild der Kupplungseinrichtung aus Fig. 6.
Show it:
Fig. 1
a spinning rotor with a coupling device according to the prior art and an axial offset of rotor cup and rotor shaft;
Fig. 2
the spinning rotor according to Fig. 1 with an angular offset between rotor cup and rotor shaft;
Fig. 3
a spinning rotor according to the invention with O-rings;
Fig. 4
a spinning rotor according to the invention with a tolerance sleeve;
Fig. 5
a sectional view of the tolerance sleeve Fig. 4 ;
Fig. 6
a spinning rotor according to the invention with an alternative coupling device;
Fig. 7
a sectional view of the coupling device Fig. 6 ,

Die Fig. 1 und die Fig. 2 zeigen einen Spinnrotor 1 mit einer Kupplungseinrichtung 3 wie im Stand der Technik zum Beispiel aus der eingangs zitierten EP 1 156 142 B1 bekannt. Anhand der beiden Figuren sollen die Probleme erläutert werden, die durch die vorliegende Erfindung behoben werden. Die Figuren 1 und 2 zeigen beide den gleichen Spinnrotor 1, so dass dieser im Folgenden nur einmal beschrieben wird. Der Spinnrotor 1 umfasst eine Rotortasse 2 und einen Rotorschaft 4, die über eine Kupplungseinrichtung 3 miteinander verbunden sind. Der Rotorschaft 4 ist in einer geeigneten, nicht dargestellten Lagerung gelagert und mit einem nicht dargestellten Antrieb verbunden. Der Antrieb versetzt den Rotorschaft 4 und damit den Spinnrotor 1 in Drehung. Die Rotortasse 2 weist einen Ansatz auf. Der Ansatz ist unterteilt in einen zylindrischen Führungsansatz 7 und ein Formschlusselement 9. In der vorliegenden Darstellung ist das Formschlusselement 9 als Außenmehrkant ausgebildet. Der Rotorschaft 4 weist eine zylindrische Bohrung 8 auf, die mit dem zylindrischen Führungsansatz 7 korrespondiert. Im Anschluss an die zylindrische Bohrung 8 weist der Rotorschaft 4 ein als Innenmehrkant ausgebildetes Formschlusselement 10 auf, das mit dem Formschlusselement 9 korrespondiert. Die Formschlusselemente 9 und 10 schaffen eine formschlüssige Verbindung zwischen der Rotortasse 2 und dem Rotorschaft 4, so dass ein Drehmoment übertragen werden kann. Zur axialen Arretierung der Rotortasse 2 weist der Rotorschaft 4 einen Magneten 5, der sich an den Innenmehrkant anschließt, auf. Der Magnet 5 übt eine Anziehungskraft auf den ferromagnetischen Ansatz der Rotortasse 2 aus. Zur axialen Arretierung sind die magnetischen Anziehungskräfte ausreichend.The Fig. 1 and the Fig. 2 show a spinning rotor 1 with a coupling device 3 as in the prior art, for example, from the above-cited EP 1 156 142 B1 known. The two figures are intended to explain the problems which are overcome by the present invention. The FIGS. 1 and 2 Both show the same spinning rotor 1, so that this will be described only once. The spinning rotor 1 comprises a rotor cup 2 and a rotor shaft 4, which are connected to one another via a coupling device 3. The rotor shaft 4 is mounted in a suitable, not shown storage and connected to a drive, not shown. The drive sets the rotor shaft 4 and thus the spinning rotor 1 in rotation. The rotor cup 2 has an approach. The approach is divided into a cylindrical guide projection 7 and a positive locking element 9. In the present illustration, the positive-locking element 9 is formed as an external polygon. The rotor shaft 4 has a cylindrical bore 8, which corresponds to the cylindrical guide projection 7. Subsequent to the cylindrical bore 8, the rotor shaft 4 has a form-locking element 10 which is designed as an internal polygon and which corresponds with the form-fitting element 9. The interlocking elements 9 and 10 create a positive connection between the rotor cup 2 and the rotor shaft 4, so that a torque can be transmitted. For axial locking of the rotor cup 2, the rotor shaft 4 has a magnet 5, which adjoins the polygonal socket on. The magnet 5 exerts an attraction on the ferromagnetic approach of the rotor cup 2. For axial locking, the magnetic attraction forces are sufficient.

In Fig. 1 sind außerdem die Achsen 16 und 17 eingezeichnet. Bei der Achse 16 handelt es sich um die Symmetrieachse der Rotortasse 2. Die Achse 17 veranschaulicht die Symmetrieachse des Rotorschaftes 4. Aufgrund des Spiels zwischen der zylindrischen Bohrung 8 und dem Führungsansatz 7 weisen die Achsen einen Versatz e auf. Dieser Versatz e führt zu einer Unwucht des Spinnrotors. Diese Unwucht kann bei Drehzahlen bis zu 200.000 min-1 zu Schädigungen des Lagers oder des Antriebes führen. In Fig. 1 sind die Achsen parallel zueinander versetzt. Fig. 2 zeigt den gleichen Spinnrotor 1 wie Fig. 1. Die Achsen 16 und 17 sind jedoch nicht parallel zueinander versetzt, sondern Rotorschaft 4 und Rotortasse 2 sind gegeneinander gekippt. Anders ausgedrückt, die Achsen 16 und 17 von Rotortasse 2 und Rotorschaft 4 weisen einen Winkelversatz auf. Auch der Winkelversatz entsteht durch das Spiel zwischen Rotorschaft 4 und Rotortasse 2 und führt zu einer Unwucht des Systems mit den oben beschriebenen Nachteilen.In Fig. 1 are also the axes 16 and 17 located. The axis 16 is the axis of symmetry of the rotor cup 2. The axis 17 illustrates the axis of symmetry of the rotor shaft 4. Due to the play between the cylindrical bore 8 and the guide projection 7, the axes on an offset e. This offset e leads to an imbalance of the spinning rotor. This imbalance can be up to 200,000 min -1 lead to damage of the bearing or of the drive at rotational speeds. In Fig. 1 the axes are offset parallel to each other. Fig. 2 shows the same spinning rotor 1 as Fig. 1 , However, the axes 16 and 17 are not offset from each other in parallel, but rotor shaft 4 and rotor cup 2 are tilted against each other. In other words, the axes 16 and 17 of rotor cup 2 and rotor shaft 4 have an angular offset. The angular offset also arises due to the clearance between the rotor shaft 4 and rotor cup 2 and leads to an imbalance of the system with the disadvantages described above.

Die Fig. 3 zeigt einen erfindungsgemäßen Spinnrotor 1a. In dem dargestellten Ausführungsbeispiel ist die Rotortasse 2 mit der Rotortasse 2 der Figuren 1 und 2 identisch. Der Rotorschaft 4a weist entsprechend dem Rotorschaft 4 eine zylindrische Bohrung 8, einen Innenmehrkant 10 und einen Magneten 5 zur axialen Arretierung der Rotortasse 2 auf. Die Kupplungseinrichtung 3a des Spinnrotors 1a unterscheidet sich dennoch von der Kupplungseinrichtung 3 des Spinnrotors 1. Im Bereich der zylindrischen Bohrung 8 des Rotorschaftes 4a sind zusätzlich zwei O-Ringe 13 und 14 angeordnet. Entlang des Umfangs der zylindrischen Bohrung 8 sind zwei Einstiche 18 und 19 vorhanden, in die die O-Ringe 13 und 14 eingelegt sind. Die beiden O-Ringe 13 und 14 sorgen in Verbindung mit einer Spielpassung zwischen der zylindrischen Bohrung 8 und dem korrespondierenden Führungsansatz 7 für eine zuverlässige Zentrierung von Rotortasse 2 und Rotorschaft 4a. Die beiden O-Ringe bilden eine elastische Anordnung. Die Ausdehnung der elastischen Anordnung in axialer Richtung der zylindrischen Bohrung ist in Fig. 3 mit la bezeichnet. Der Durchmesser der zylindrischen Bohrung 8 ist mit d bezeichnet. Wenn die Ausdehnung la im Verhältnis zum Durchmesser d ausreichend groß ist, kann auch ein Winkelversatz zwischen den Achsen der Rotortasse 2 und des Rotorschaftes 4a verhindert werden. Erfindungsgemäß muss dazu die Ausdehnung la mindestens 80% des Durchmessers d betragen.The Fig. 3 shows a spinning rotor 1a according to the invention. In the illustrated embodiment, the rotor cup 2 with the rotor cup 2 of FIGS. 1 and 2 identical. The rotor shaft 4a has, corresponding to the rotor shaft 4, a cylindrical bore 8, an internal polygon 10 and a magnet 5 for the axial locking of the rotor cup 2. The coupling device 3a of the spinning rotor 1a still differs from the coupling device 3 of the spinning rotor 1. In the region of the cylindrical bore 8 of the rotor shaft 4a, two O-rings 13 and 14 are additionally arranged. Along the circumference of the cylindrical bore 8, two recesses 18 and 19 are provided, in which the O-rings 13 and 14 are inserted. The two O-rings 13 and 14, in conjunction with a clearance fit between the cylindrical bore 8 and the corresponding guide projection 7 for a reliable centering of rotor cup 2 and rotor shaft 4a. The two O-rings form an elastic arrangement. The extent of the elastic arrangement in the axial direction of the cylindrical bore is in Fig. 3 denoted by l a . The diameter of the cylindrical bore 8 is denoted by d. If the extent l a in relation to the diameter d is sufficiently large, an angular offset between the axes of the rotor cup 2 and the rotor shaft 4 a can be prevented. According to the invention, the extent l a must be at least 80% of the diameter d.

Die Figuren 4 und 5 zeigen eine alternative Ausführungsform der vorliegenden Erfindung. Der Unterschied des Spinnrotors 1b zum Spinnrotor 1a liegt dabei darin, dass die Kupplungseinrichtung 3b eine andere elastische Anordnung aufweist. Der Rotorschaft 4b weist am Umfang der zylindrischen Bohrung 8 einen Einstich 20b auf. An dem Einstich 20b ist eine Toleranzhülse 15b angelegt. Um den Aufbau der Toleranzhülse 15b zu verdeutlichen, zeigt Fig. 5 einen Schnitt durch die Toleranzhülse entlang der Schnittlinie A-A. Die Fig. 5 zeigt, dass die Toleranzhülse 15b als gewelltes Band ausgebildet ist. Das gewellte Band kann aus Federbandstahl gefertigt sein. Im Ausführungsbeispiel der Fig. 4 besteht die elastische Anordnung aus dem elastischen Element, nämlich der Toleranzhülse 15b. Die Länge lb der Toleranzhülse 15b entspricht hier der Ausdehnung der elastischen Anordnung in axialer Richtung der zylindrischen Bohrung. Die Länge lb ist auch hier im Verhältnis zum Durchmesser d der zylindrischen Bohrung 8 so gewählt, dass ein Winkelversatz vermieden wird. Alternativ ist es auch möglich, statt der einen Toleranzhülse 15b zwei entsprechend kürzere Toleranzhülsen zu verwenden, die beabstandet zueinander angeordnet sind.The FIGS. 4 and 5 show an alternative embodiment of the present invention. The difference between the spinning rotor 1b and the spinning rotor 1a lies in the fact that the coupling device 3b has a different elastic arrangement. The rotor shaft 4b has on the circumference of the cylindrical bore 8 a recess 20b. At the groove 20b, a tolerance sleeve 15b is applied. To illustrate the structure of the tolerance sleeve 15b, shows Fig. 5 a section through the tolerance sleeve along the section line AA. The Fig. 5 shows that the tolerance sleeve 15b is formed as a corrugated band. The corrugated band can be made of spring band steel. In the embodiment of Fig. 4 the elastic arrangement consists of the elastic element, namely the tolerance sleeve 15b. The length l b of the tolerance sleeve 15b corresponds to the extent of the elastic arrangement in the axial direction of the cylindrical bore. The length l b is also chosen here in relation to the diameter d of the cylindrical bore 8 so that an angular offset is avoided. Alternatively, it is also possible, instead of the one tolerance sleeve 15b, to use two correspondingly shorter tolerance sleeves, which are arranged at a distance from one another.

Für die vorliegende Erfindung ist es im Prinzip unerheblich, wie die Rotortasse in axialer Richtung arretiert wird und wie die formschlüssige Verbindung zur Übertragung des Drehmoments realisiert ist. Zur Veranschaulichung zeigt die Fig. 6 eine alternative Ausführung der vorliegenden Erfindung. Der Spinnrotor 1c umfasst eine Rotortasse 2c, eine Kupplungseinrichtung 3c und einen Rotorschaft 4c. Anders als in den vorherigen Ausführungsbeispielen weist nicht der Rotorschaft 4 eine zylindrische Bohrung 8 auf, sondern die Rotortasse 2c weist eine zylindrische Bohrung 8c auf. Der Rotorschaft 4c weist einen dazu korrespondierenden Führungsansatz 7c auf. In dem Führungsansatz 7c ist ein umlaufender Einstich 20c eingebracht. So kann zwischen dem Führungsansatz 7c und der zylindrischen Bohrung 8c die Toleranzhülse 15c angeordnet werden, um Rotortasse 2c und Rotorschaft 4c zu zentrieren. Im Anschluss an den Führungsansatz 7c weist der Rotorschaft 4c ein Formschlusselement 11 auf. Die Rotortasse 2c umfasst ein dazu korrespondierendes Formschlusselement 12. Die Fig. 7 zeigt den Schnitt B-B mit den beiden Formschlusselementen 11 und 12. Die Formschlusselemente 11 und 12 haben eine kreiszylindrische Form mit zwei ebenen Flächen auf dem Umfang. Andere Formen sind möglich.For the present invention, it is in principle irrelevant how the rotor cup is locked in the axial direction and how the positive connection for transmitting the torque is realized. To illustrate, the Fig. 6 an alternative embodiment of the present invention. The spinning rotor 1c includes a rotor cup 2c, a clutch device 3c and a rotor shaft 4c. Unlike in the previous embodiments, the rotor shaft 4 does not have a cylindrical bore 8, but the rotor cup 2c has a cylindrical bore 8c. The rotor shaft 4c has a guide lug 7c corresponding thereto. In the guide projection 7c, a circumferential recess 20c is introduced. Thus, between the guide projection 7c and the cylindrical bore 8c, the tolerance sleeve 15c can be arranged to center the rotor cup 2c and rotor shaft 4c. Following the guide projection 7c, the rotor shaft 4c has a positive-locking element 11. The rotor cup 2c comprises a form-fitting element 12 corresponding thereto Fig. 7 shows the section BB with the two form-fitting elements 11 and 12. The positive-locking elements 11 and 12 have a circular cylindrical shape with two flat surfaces on the circumference. Other shapes are possible.

Zur axialen Arretierung weist der Rotorschaft 4c zwei Verriegelungskörper 6 auf, die mittels des elastischen Elementes 21 und bei Drehung des Spinnrotors durch die Fliehkraft in die umlaufende v-förmige Nut 22 der Rotortasse 4c gedrückt werden. Die axiale Arretierung ist in der nicht vorveröffentlichten DE 10 2012 008 693.8 genauer beschrieben.For axial locking, the rotor shaft 4c on two locking body 6, which are pressed by the centrifugal force in the circumferential v-shaped groove 22 of the rotor cup 4c by means of the elastic element 21 and upon rotation of the spinning rotor. The axial locking is in the not previously published DE 10 2012 008 693.8 described in more detail.

Claims (12)

  1. An open-end spinning rotor (1 a, 1 b, 1 c), comprising a rotor shaft (4a, 4b, 4c), a rotor cup (2, 2c) and a coupling device (3a, 3b, 3c), which detachably connects the rotor shaft (4a, 4b, 4c) and the rotor cup (2, 2c) with one another, wherein the coupling device (3a, 3b, 3c) has a locking mechanism (5, 6) for axial locking of the rotor cup (2, 2c), means of transmission (9, 10, 11, 12) for positive transfer of a torque from the rotor shaft (4a, 4b, 4c) to the rotor cup (2, 2c) and additional centring aids for centring the rotor shaft (4a, 4b, 4c) and rotor cup (2, 2c), wherein the centring aid comprises a cylindrical bore (8, 8c) and a corresponding guide projection (7, 7c), which can be inserted into the cylindrical bore (8, 8c),
    characterised in that
    the cylindrical bore (8, 8c) and the guide projection (7, 7c) have a clearance fit, the clearance between the cylindrical bore (8, 8c) and the guide projection (7, 7c) is smaller than 0.1 mm, and the centring aids comprise an elastic configuration (13, 14, 15b, 15c), which is arranged between the cylindrical bore (8, 8c) and the guide projection (7, 7c).
  2. The open-end spinning rotor in accordance with Claim 1, characterised in that the clearance between the cylindrical bore (8, 8c) and the guide projection (7, 7c) is smaller than 0.01 mm.
  3. The open-end spinning rotor in accordance with one of the foregoing claims, characterised in that the extension (la, lb) of the elastic configuration (13, 14, 15b, 15c) is greater in an axial direction of the cylindrical bore (8, 8c) than 0.8 times the diameter (d) of the cylindrical bore (8, 8c).
  4. The open-end spinning rotor in accordance with Claim 3, characterised in that the extension (la, lb) of the elastic configuration in an axial direction of the cylindrical bore (8, 8c) is smaller than 2.4 times the diameter (d) of the cylindrical bore (8, 8c).
  5. The open-end spinning rotor in accordance with one of the foregoing claims, characterised in that the elastic configuration comprises an elastic element (13, 15b, 15c).
  6. The open-end spinning rotor in accordance with Claim 5, characterised in that the elastic element is designed as a tolerance bush (15b, 15c).
  7. The open-end spinning rotor in accordance with Claim 6, characterised in that the tolerance bush (15b, 15c) is designed as a corrugated band.
  8. The open-end spinning rotor in accordance with Claim 7, characterised in that the corrugated band consists of a spring steel strip.
  9. The open-end spinning rotor in accordance with Claim 5, characterised in that the elastic element is designed as an O-ring (13, 14).
  10. The open-end spinning rotor in accordance with one of Claims 5 to 9, characterised in that a circumferential recess (18, 19, 20) is provided for in the cylindrical bore (8, 8c) and/or the guide projection (7, 7c), into which the elastic element (13, 14, 15b, 15c) is inserted.
  11. The open-end spinning rotor in accordance with one of claims 5 to 10, characterised in that the elastic configuration comprises a second elastic element (14), which is configured at a distance from the first elastic element (13) in an axial direction of the cylindrical bore.
  12. The open-end spinning rotor in accordance with Claim 11, characterised in that the first elastic element (13) and the second elastic element (14) are designed identically.
EP13004898.6A 2012-11-10 2013-10-11 Open-end spinning rotor Revoked EP2730686B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012022092.8A DE102012022092A1 (en) 2012-11-10 2012-11-10 Open-end spinning rotor

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EP2730686B1 true EP2730686B1 (en) 2015-12-16

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DE102016122595A1 (en) 2016-11-23 2018-05-24 Maschinenfabrik Rieter Ag Rotor cup and open-end spinning rotor with a rotor cup

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DE102016123698A1 (en) * 2016-12-07 2018-06-07 Saurer Germany Gmbh & Co. Kg Spinning rotor for an open-end spinning device and open-end spinning device
DE102017129152A1 (en) 2017-12-07 2019-06-13 Maschinenfabrik Rieter Ag Opening roller for an open-end spinning device and open-end spinning device
CN110424073A (en) * 2019-08-10 2019-11-08 苏州当峰纺织有限公司 A kind of spinning apparatus on open-end spinning frame

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IN2013MU03291A (en) 2015-07-10
EP2730686A1 (en) 2014-05-14
CN103806144A (en) 2014-05-21
DE102012022092A1 (en) 2014-05-15
CN103806144B (en) 2017-04-26

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