EP0146741B1 - Disc bearing - Google Patents
Disc bearing Download PDFInfo
- Publication number
- EP0146741B1 EP0146741B1 EP84113341A EP84113341A EP0146741B1 EP 0146741 B1 EP0146741 B1 EP 0146741B1 EP 84113341 A EP84113341 A EP 84113341A EP 84113341 A EP84113341 A EP 84113341A EP 0146741 B1 EP0146741 B1 EP 0146741B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- supporting
- shaft
- coating
- recess
- running surface
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Images
Classifications
-
- 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
- D01H4/12—Rotor bearings; Arrangements for driving or stopping
Definitions
- the invention relates to a support disk bearing for the shaft of an open-end spinning rotor which is mounted in a wedge gap formed by support disks and is driven directly by a tangential belt, an axial thrust being exerted on the shaft via the support disks in order to press it against an axial bearing, and the support disks Have a tread made of an elastic covering against which the shaft is pressed.
- the tread In operation, the tread is exposed to considerable stress due to the rapidly rotating shaft pressed against the tread with the pressure required for the drive, which is exacerbated by an existing imbalance and in particular also by the axial thrust on the shaft generated by the support disks. This stress leads to a relatively rapid wear and destruction of the tread and thus the rotor bearing. It is necessary to replace the support disks, which, due to the large number of spinning positions, incurs considerable costs for material, assembly and the loss of machine production time.
- An open-end spinning device with a support roller bearing is also known, in which the rotor shaft is guided between liners provided with support rings and is driven indirectly via one of these liners. The axial position of the rotor shaft is secured by the force of a permanent magnet (DE-A-2.206.264).
- a permanent magnet DE-A-2.206.264
- the object of the present invention is to improve a support disk bearing according to the preamble of claim 1 in such a way that the service life of the treads and thus the entire rotor bearing is increased.
- a shaft 1 of an open-end spinning rotor for which the support disk bearing is intended in particular, is mounted in the wedge gap of freely rotatable support disks 4 and 5 arranged in pairs on axes 2 and 3.
- the support disks 4 and 5 are provided on their circumference with an elastic covering, which consists of plastic, for example polyurethane, or also of another suitable material and forms a running surface 40, 50 for the shaft 1.
- a tangential belt 6 presses the shaft 1 with a predetermined pressure against the tread 40 and 50 and drives it.
- Such a bearing is generally known and therefore does not require any further explanation, in particular also not with regard to the axial thrust exerted on the shaft 1 via the support disks during operation, in order to press it against an axial bearing.
- the plastic covering is subjected to a high stress starting from the shaft 1 in this mounting, which leads to wear and destruction of the tread 40 and 50.
- the tread is interrupted by cutouts. These recesses can be designed and arranged in various ways.
- a groove-shaped recess is preferred, which runs in the direction of rotation of the support disks 4 and 5 and is arranged in the middle of the running surface 40 and 50 (FIG. 2).
- the shape of such an endless groove 7 can be different.
- the groove 7 can have, for example, a wedge-shaped, a rectangular, a semicircular or a trapezoidal shape.
- two further grooves 7 ′ running parallel to the central groove are provided in addition to the centrally arranged groove 7, so that the running surface 40 or 50 is interrupted on its circumference by a total of three recesses.
- the shaft 1 rests on the running surfaces 40 and 50 on both sides of the groove 7 and 7 ', whereby its line of contact, which can also become the contact surface when the shaft 1 is pressed against the elastic covering, bridges the groove freely.
- the support of the shaft 1 on both sides of the recess ensures that the shaft 1 rolls off smoothly.
- a groove 70 runs spirally over the circumference of the tread.
- the embodiment b shows a running surface which is interrupted by a plurality of grooves 71 arranged at an angle to the direction of rotation of the support disk and at a distance from one another. The angle and the width of the grooves 71 are chosen so that the shaft 1 is not selected in the grooves 71 so that the shaft 1 cannot fall into the grooves, but bridges them.
- the base body of the support disk is provided with a web 41 which extends into the vicinity of the running surface and forms a recess together with the elastic covering.
- the effect of the invention seems to be based on the fact that, as a result of the rotation of the support disks, an air flow is generated in the cutouts, which cools the elastic covering and thereby reduces wear caused by excessive heating, for better heat dissipation and thus for preventing Destruction of the covering leading to heat build-up, the recess must have an appropriate dimension.
- Experiments with a covering of 6 mm thickness have shown, for example, that a recess with a depth of approximately up to a third of the covering thickness is particularly effective. With the width of the recess, it should also be noted that effective ventilation and thus heat dissipation is guaranteed.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Textile Engineering (AREA)
- Spinning Or Twisting Of Yarns (AREA)
- Toys (AREA)
- Dynamo-Electric Clutches, Dynamo-Electric Brakes (AREA)
- Nozzles For Electric Vacuum Cleaners (AREA)
Description
Die Erfindung betrifft ein Stützscheibenlager für den in einem von Stützscheiben gebildeten Keilspalt gelagerten und von einem Tangentialriemen direkt angetriebenen Schaft eines Offenend-Spinnrotors, wobei über die Stützscheiben ein Axialschub auf den Schaft ausgeübt wird, um ihn gegen ein Axiallager zu drücken, und die Stützscheiben eine Lauffläche aus einem elastischen Belag haben, gegen die der Schaft gedrückt wird.The invention relates to a support disk bearing for the shaft of an open-end spinning rotor which is mounted in a wedge gap formed by support disks and is driven directly by a tangential belt, an axial thrust being exerted on the shaft via the support disks in order to press it against an axial bearing, and the support disks Have a tread made of an elastic covering against which the shaft is pressed.
Es ist bekannt, den Schaft eines Offenend-Spinnrotors in dem durch Stützscheiben gebildeten Keilspalt radial zu lagern und ihn dabei mittels eines Tangentialriemens gegen die Stützscheiben zu pressen (DE-A-2.112.913). Zur axialen Lagesicherung des Schaftes wird durch Schränkung der Achsen der Stützscheiben eine axiale Kraft auf den Schaft ausgeübt, die das freie Schaftende gegen ein Spurlager drückt. Die Stützscheiben sind mit Belägen aus dämpfendem Material, z.B. Kunststoff, versehen, um schädliche Schwingungen des mit hohen Drehzahlen umlaufenden Spinnrotors zu vermeiden und auch den Lärm zu mindern. Im Betrieb ist die Lauffläche durch den schnell rotierenden und mit dem für den Antrieb erforderlichen Druck an die Lauffläche gepreßten Schaft einer erheblichen Beanspruchung ausgesetzt, die durch eine vorhandene Unwucht und insbesondere auch durch den über die Stützscheiben erzeugten Axialschub auf den Schaft noch verstärkt wird. Diese Beanspruchung führt zu einem verhältnismäßig raschen Verschleiß und zur Zerstörung der Lauffläche und damit der Rotorlagerung. Es ist ein Austausch der Stützscheiben erforderlich, was bei der Vielzahl der Spinnstellen jedes Mal erhebliche Kosten für Material, Montage und durch Ausfall der Produktionszeit der Maschine verursacht.It is known to radially support the shaft of an open-end spinning rotor in the wedge gap formed by support disks and to press it against the support disks by means of a tangential belt (DE-A-2.112.913). To secure the shaft axially, an axial force is exerted on the shaft by setting the axes of the support disks, which force presses the free shaft end against a thrust bearing. The support discs are provided with coverings made of damping material, such as plastic, in order to avoid harmful vibrations of high Avoid speeds rotating spinning rotor and also to reduce the noise. In operation, the tread is exposed to considerable stress due to the rapidly rotating shaft pressed against the tread with the pressure required for the drive, which is exacerbated by an existing imbalance and in particular also by the axial thrust on the shaft generated by the support disks. This stress leads to a relatively rapid wear and destruction of the tread and thus the rotor bearing. It is necessary to replace the support disks, which, due to the large number of spinning positions, incurs considerable costs for material, assembly and the loss of machine production time.
Es ist ferner eine Offenend-Spinnvorrichtung mit einem Stützrollenlager bekannt, bei welcher der Rotorschaft zwischen mit Stützringen versehenen Laufbüchsen geführt und indirekt über eine dieser Laufbüchsen angetrieben ist. Die axiale Lage des Rotorschaftes wird durch die Kraft eines Permanentmagneten gesichert (DE-A-2.206.264). Für diese Lagerungs- und Antriebsart wird vorgeschlagen, die Beläge der auf den Laufbüchsen aufgepreßten Stützringe aus abriebfestem nichtmetallischem Werkstoff mit einer oder mehreren Ringnuten zu versehen, deren Breite und Tiefe sich in erster Linie nach der Breite der Stützflächen richten und während des Betriebes oder beim Abbremsen der Vorrichtung eine gute Wärmeabfuhr bewirken soll. Näheres über die Entstehung der Wärme und die entsprechende Ausbildung der Nut zur Wärmeabfuhr ist nicht angegeben.An open-end spinning device with a support roller bearing is also known, in which the rotor shaft is guided between liners provided with support rings and is driven indirectly via one of these liners. The axial position of the rotor shaft is secured by the force of a permanent magnet (DE-A-2.206.264). For this type of bearing and drive it is proposed to provide the linings of the support rings pressed onto the liners from abrasion-resistant, non-metallic material with one or more ring grooves, the width and depth of which depend primarily on the width of the support surfaces and during operation or when braking the device should cause good heat dissipation. No details are given on the generation of heat and the corresponding design of the groove for heat dissipation.
Aufgabe der vorliegenden Erfindung ist es, ein Stützscheibenlager gemäß dem Oberbegriff des Anspruches 1 dahingehend zu verbessern, daß die Standzeit der Laufflächen und damit der gesamten Rotorlagerung vergrößert wird.The object of the present invention is to improve a support disk bearing according to the preamble of claim 1 in such a way that the service life of the treads and thus the entire rotor bearing is increased.
Die Aufgabe wird erfindungsgemäß durch die Merkmale des Anspruches 1 gelöst.The object is achieved by the features of claim 1.
Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen beschrieben.Advantageous developments of the invention are described in the subclaims.
Die Erfindung wird nachstehend anhand der Zeichnungen näher erläutert. Es zeigt:
- Figur 1
- ein Stützscheibenlager für einen von einem Tangentialriemen angetriebenen Rotorschaft, von vorn gesehen;
- Figur 2
- Stützscheiben mit rillenförmigen Aussparungen in der Lauffläche, in der Draufsicht;
- Figur 3
- weitere Möglichkeiten der Unterbrechung der Lauffläche durch Aussparungen, in der Draufsicht und teilweise im Schnitt.
- Figure 1
- a support disc bearing for a rotor shaft driven by a tangential belt, seen from the front;
- Figure 2
- Support discs with grooved recesses in the tread, in top view;
- Figure 3
- further options for interrupting the tread by recesses, in plan view and partly in section.
Gemäß Figur 1 ist ein Schaft 1 eines Offenend-Spinnrotors, für den das Stützscheibenlager insbesondere bestimmt ist, im Keilspalt von paarweise auf Achsen 2 und 3 angeordneten, frei drehbaren Stützscheiben 4 und 5 gelagert. Die Stützscheiben 4 und 5 sind auf ihrem Umfang mit einem elastischen Belag versehen, der aus Kunststoff, beispielsweise aus Polyurethan, oder auch aus einem anderen geeigneten Material besteht und eine Lauffläche 40, 50 für den Schaft 1 bildet. Ein Tangentialriemen 6 preßt den Schaft 1 mit vorbestimmtem Druck gegen die Lauffläche 40 und 50 und treibt ihn an. Eine solche Lagerung ist allgemein bekannt und bedarf daher keiner näheren Erläuterung, insbesondere auch nicht hinsichtlich des im laufenden Betrieb über die Stützscheiben auf den Schaft 1 ausgeübten Axialschubes, um ihn gegen ein Axiallager zu drücken.According to FIG. 1, a shaft 1 of an open-end spinning rotor, for which the support disk bearing is intended in particular, is mounted in the wedge gap of freely
Wie bereits eingangs dargelegt, ist der Kunststoffbelag bei dieser Lagerung einer vom Schaft 1 ausgehenden hohen Beanspruchung ausgesetzt, die zu einem Verschleiß und zur Zerstörung der Lauffläche 40 und 50 führt. Um dem entgegenzuwirken und die Standzeit der Lauffläche 40 und 50 zu erhöhen, ist die Lauffläche durch Aussparungen unterbrochen. Dabei können diese Aussparungen in verschiedenartiger Weise ausgebildet und angeordnet sein.As already explained at the beginning, the plastic covering is subjected to a high stress starting from the shaft 1 in this mounting, which leads to wear and destruction of the
Bevorzugt wird jedoch eine rillenförmige Aussparung, die in Drehrichtung der Stützscheibe 4 und 5 verläuft und in der Mitte der Lauffläche 40 und 50 angeordnet ist (Figur 2). Die Form einer solchen endlosen Rille 7 kann unterschiedlich sein. Wie die Ausführungen a bis d in Figur 2 zeigen, kann die Rille 7 beispielsweise eine keilförmige, eine rechteckige, eine halbkreisförmige oder eine trapezförmige Form haben. Bei der Ausführung e in Figur 2 sind neben der mittig angeordneten Rille 7 noch zwei weitere parallel zur Mittelrille verlaufende Rillen 7' vorgesehen, so daß die Lauffläche 40 bzw. 50 auf ihrem Umfang durch insgesamt drei Aussparungen unterbrochen ist.However, a groove-shaped recess is preferred, which runs in the direction of rotation of the
Im Betrieb liegt der Schaft 1 auf den Laufflächen 40 und 50 auf beiden Seiten der Rille 7 bzw. 7' auf, wobei seine Berührungslinie, die bei höherem Anpreßdruck des Schaftes 1 an den elastischen Belag auch zur Berührungsfläche werden kann, die Rille frei überbrückt. Die Auflage des Schaftes 1 auf beiden Seiten der Aussparung gewährleistet, daß sich der Schaft 1 stoßfrei abrollt.In operation, the shaft 1 rests on the running
In Figur 3 sind weitere Möglichkeiten der Ausbildung von Aussparungen zur Unterbrechung der Lauffläche dargestellt. Aussparungen zur Unterbrechung der Lauffläche dargestellt. Bei der Ausführung a verläuft eine Rille 70 spiralförmig über den Umfang der Lauffläche. Die Ausführung b zeigt eine Lauffläche, die durch mehrere, in einem Winkel zur Drehrichtung der Stützscheibe und in einem Abstand zueinander angeordnete Rillen 71 unterbrochen ist. Der Winkel und die Breite der Rillen 71 wird so gewählt, daß der Schaft 1 nicht in die Rillen 71 wird so gewählt, daß der Schaft 1 nicht in die Rillen hineinfallen kann, sondern sie überbrückt. Durch den Verlauf der Rillen 71 wie auch der Rille 70 bei der Ausführung a in Figur 3 bis zum Rand der Lauffläche wird nach bisherigen Erkenntnissen der stoßfreie Lauf des Spinnrotors nicht beeinträchtigt, da in dem Bereich, in dem die Rille am Rand ausläuft, die Lauffläche für den Schaft genügend groß ist. Gegebenenfalls kann jedoch die Rille 71 oder 70 auch vor dem Laufflächenrand enden, falls sich dies als notwendig erweisen sollte.In Figure 3, other ways of forming recesses to interrupt the tread are shown. Cutouts to interrupt the tread are shown. In version a, a
Es ist ferner auch möglich, in den Grundkörper der Stützscheibe Rippen 8 aus Kunststoff im Abstand voneinander einzulassen, wodurch sich ebenfalls eine durch Aussparungen unterbrochene Lauffläche ergibt.It is also possible to insert ribs 8 made of plastic at a distance from one another in the base body of the support disk, which likewise results in a running surface interrupted by cutouts.
Bei der Ausführung e ist der Grundkörper der Stützscheibe mit einem Steg 41 versehen, der bis in die Nähe der Lauffläche heranreicht und zusammen mit dem elastischen Belag eine Aussparung bildet.In design e, the base body of the support disk is provided with a
Die Wirkung der Erfindung scheint darauf zu beruhen, daß infolge der Rotation der Stützscheiben ein Luftstrom in den Aussparungen erzeugt wird, der eine Kühlung des elastischen Belages bewirkt und dadurch einen durch zu hohe Erwärmung bedingten Verschleiß mindert, Zur besseren Wärmeableitung und damit zur Verhinderung eines zur Zerstörung des Belages führenden Wärmestaus muß die Aussparung eine entsprechende Abmessung haben. Bei Versuchen mit einem Belag von 6 mm Dicke hat sich beispielsweise ergeben, daß eine Aussparung mit einer Tiefe von etwa bis zu einem Drittel der Belagdicke besonders wirkungsvoll ist. Ebenso ist bei der Breite der Aussparung zu beachten, daß eine wirkungsvolle Belüftung und damit Wärmeableitung gewährleistet ist.The effect of the invention seems to be based on the fact that, as a result of the rotation of the support disks, an air flow is generated in the cutouts, which cools the elastic covering and thereby reduces wear caused by excessive heating, for better heat dissipation and thus for preventing Destruction of the covering leading to heat build-up, the recess must have an appropriate dimension. Experiments with a covering of 6 mm thickness have shown, for example, that a recess with a depth of approximately up to a third of the covering thickness is particularly effective. With the width of the recess, it should also be noted that effective ventilation and thus heat dissipation is guaranteed.
Claims (7)
- A supporting-disc bearing for the shaft of an open-end spinning rotor, which shaft is supported in a wedge-shaped gap formed by supporting discs and is driven directly by a tangential belt, an axial thrust being exerted on the shaft via the supporting discs in order to press it against an axial bearing, and the supporting discs having a running surface made of a resilient coating, against which the shaft is pressed, characterised in that the running surface (40, 50) of the coating is interrupted by at least one recess (7, 7') - which is bridged freely by the line of contact of the rotor shaft - so that ventilation is brought about in the recess (7, 7') in order to cool the resilient supporting-disc coating.
- A supporting-disc bearing according to Claim 1, characterised in that the recess has a depth of up to approximately one third of the coating thickness where the coating has a thickness of 6 mm.
- A supporting-disc bearing according to Claim 1 or 2, characterised in that the recess is formed by a continuous groove (7, 7').
- A supporting-disc bearing according to Claim 1 or 2, characterised in that the recess is formed by a groove (70) extending spirally over the periphery of the running surface (40, 50).
- A supporting-disc bearing according to Claim 1 or 2, characterised in that the recesses are formed by several grooves (71) arranged at an angle to the direction of rotation of the supporting discs (4, 5) and at a distance from one another.
- A supporting-disc bearing according to any one of Claims 1 to 5, characterised in that the running surface (40, 50) of the supporting discs (4, 5) is formed by coating ribs (8) arranged at a distance from one another.
- A supporting-disc bearing according to any one of Claims 1 to 5, characterised in that the basic body of the supporting disc (4, 5) is provided with a web (41) which extends into the vicinity of the running surface (40, 50) and forms a recess together with the coating.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE3342768 | 1983-11-25 | ||
| DE19833342768 DE3342768A1 (en) | 1983-11-25 | 1983-11-25 | SUPPORT DISC BEARING |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0146741A1 EP0146741A1 (en) | 1985-07-03 |
| EP0146741B1 true EP0146741B1 (en) | 1992-08-12 |
Family
ID=6215313
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP84113341A Expired - Lifetime EP0146741B1 (en) | 1983-11-25 | 1984-11-06 | Disc bearing |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP0146741B1 (en) |
| JP (1) | JPS60119231A (en) |
| CS (1) | CS274410B2 (en) |
| DE (2) | DE3342768A1 (en) |
| IN (1) | IN161367B (en) |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4676673A (en) * | 1983-07-05 | 1987-06-30 | Fritz Stahlecker | Bearing disk construction for supporting a spinning rotor shaft of an open-end spinning machine |
| DE8433579U1 (en) * | 1984-11-16 | 1985-04-18 | Stahlecker, Fritz, 7347 Bad Überkingen | SUPPORT DISC FOR A SUPPORT DISC BEARING FOR OE SPINNING ROTORS |
| DE3447600A1 (en) * | 1984-12-07 | 1986-06-12 | Fritz 7347 Bad Überkingen Stahlecker | Supporting-disc mounting for open-end spinning rotors |
| US4892422A (en) * | 1988-08-01 | 1990-01-09 | American Suessen Corporation | Support assembly for the rotor of an open end yarn spinning apparatus |
| DE19712916A1 (en) * | 1997-03-27 | 1998-10-01 | Novibra Gmbh | Support disc for open-ended spinning rotor |
| DE19824286A1 (en) * | 1998-05-29 | 1999-12-02 | Rieter Ingolstadt Spinnerei | Bearing for an open-end spinning rotor using support disks |
| DE10018440A1 (en) | 2000-04-13 | 2001-10-18 | Rieter Ingolstadt Spinnerei | Support disc for a support disc bearing for spinning rotors |
| PL1852530T3 (en) | 2006-05-06 | 2008-12-31 | Freudenberg Carl Kg | Support disk for the bearing of a rotor of a openend-spinningmachine and method of its manufacture |
| CN103343772A (en) * | 2013-07-18 | 2013-10-09 | 苏州天华有色金属制品有限公司 | Roller |
| DE102015114659A1 (en) * | 2015-09-02 | 2017-03-02 | Maschinenfabrik Rieter Ag | Support disc with spherical tread |
| DE102016108860A1 (en) * | 2016-05-13 | 2017-11-16 | Rieter Ingolstadt Gmbh | Support disc for a bearing for a shaft of an open-end spinning rotor and storage for a shaft of an open-end spinning rotor |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2112913A1 (en) * | 1971-03-17 | 1972-10-05 | Stahlecker Gmbh Wilhelm | Storage of a spinning turbine of an open-end spinning unit |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR1362081A (en) * | 1963-04-19 | 1964-05-29 | Socitex | Improvements to machines with rotating spindles, in particular machines for creping textile threads by false twist |
| DE1901453C3 (en) * | 1969-01-13 | 1982-12-02 | Wilhelm Stahlecker Gmbh, 7341 Reichenbach | Storage of a spinning turbine of an open-end spinning machine |
| DE2206237A1 (en) * | 1972-02-10 | 1973-08-23 | Skf Kugellagerfabriken Gmbh | Shaft bearing - with shell in pole plate to support ball and shaft |
| DE2206264B2 (en) * | 1972-02-10 | 1974-10-17 | Skf Kugellagerfabriken Gmbh, 8720 Schweinfurt | Drive for spinning organs for spindleless spinning |
| FR2223487A1 (en) * | 1973-03-29 | 1974-10-25 | Kugelfischer G Schaefer & Co | Friction disc to drive false twist spindle - having rolling surface with peripheral groove(s) |
| DE2801693A1 (en) * | 1978-01-16 | 1979-07-19 | Stahlecker Fritz | Open=end spinning rotor mounting - has contact point for shaft at centre of supporting disc cladding to reduce wear |
-
1983
- 1983-11-25 DE DE19833342768 patent/DE3342768A1/en not_active Ceased
-
1984
- 1984-11-06 DE DE8484113341T patent/DE3485867D1/en not_active Expired - Lifetime
- 1984-11-06 EP EP84113341A patent/EP0146741B1/en not_active Expired - Lifetime
- 1984-11-08 CS CS850184A patent/CS274410B2/en unknown
- 1984-11-13 IN IN866/MAS/84A patent/IN161367B/en unknown
- 1984-11-14 JP JP59238713A patent/JPS60119231A/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2112913A1 (en) * | 1971-03-17 | 1972-10-05 | Stahlecker Gmbh Wilhelm | Storage of a spinning turbine of an open-end spinning unit |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS60119231A (en) | 1985-06-26 |
| EP0146741A1 (en) | 1985-07-03 |
| DE3485867D1 (en) | 1992-09-17 |
| IN161367B (en) | 1987-11-14 |
| CS850184A2 (en) | 1990-09-12 |
| DE3342768A1 (en) | 1985-06-05 |
| CS274410B2 (en) | 1991-04-11 |
| JPS6327454B2 (en) | 1988-06-03 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
| AK | Designated contracting states |
Designated state(s): CH DE FR GB IT LI |
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