WO2016146465A1 - Broche de bobinage - Google Patents

Broche de bobinage Download PDF

Info

Publication number
WO2016146465A1
WO2016146465A1 PCT/EP2016/055085 EP2016055085W WO2016146465A1 WO 2016146465 A1 WO2016146465 A1 WO 2016146465A1 EP 2016055085 W EP2016055085 W EP 2016055085W WO 2016146465 A1 WO2016146465 A1 WO 2016146465A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
winding
damping
shaft
chuck
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.)
Ceased
Application number
PCT/EP2016/055085
Other languages
German (de)
English (en)
Inventor
Heinz Waltermann
Jürgen KOWALSKI
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.)
Oerlikon Textile GmbH and Co KG
Original Assignee
Oerlikon Textile 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
Application filed by Oerlikon Textile GmbH and Co KG filed Critical Oerlikon Textile GmbH and Co KG
Priority to JP2017549039A priority Critical patent/JP7002939B2/ja
Priority to CN201680015749.0A priority patent/CN107428489B/zh
Priority to DE112016001265.9T priority patent/DE112016001265A5/de
Publication of WO2016146465A1 publication Critical patent/WO2016146465A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H54/00—Winding, coiling, or depositing filamentary material
    • B65H54/02—Winding and traversing material on to reels, bobbins, tubes, or like package cores or formers
    • B65H54/40—Arrangements for rotating packages
    • B65H54/54—Arrangements for supporting cores or formers at winding stations; Securing cores or formers to driving members
    • B65H54/547—Cantilever supporting arrangements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H67/00—Replacing or removing cores, receptacles, or completed packages at paying-out, winding, or depositing stations
    • B65H67/04—Arrangements for removing completed take-up packages and or replacing by cores, formers, or empty receptacles at winding or depositing stations; Transferring material between adjacent full and empty take-up elements
    • B65H67/044—Continuous winding apparatus for winding on two or more winding heads in succession
    • B65H67/048—Continuous winding apparatus for winding on two or more winding heads in succession having winding heads arranged on rotary capstan head
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2601/00—Problem to be solved or advantage achieved
    • B65H2601/50—Diminishing, minimizing or reducing
    • B65H2601/52—Diminishing, minimizing or reducing entities relating to handling machine
    • B65H2601/524—Vibration
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2701/00—Handled material; Storage means
    • B65H2701/30—Handled filamentary material
    • B65H2701/31—Textiles threads or artificial strands of filaments
    • B65H2701/313—Synthetic polymer threads
    • B65H2701/3132—Synthetic polymer threads extruded from spinnerets

Definitions

  • the invention relates to a winding spindle for winding threads into a plurality of bobbins in a winding machine according to the preamble of claim 1.
  • the filaments of a spinning position are co-wound in parallel with spools.
  • winding machines are used, each having a winding point per thread and parallel to the winding points have a unilaterally mounted winding spindle.
  • Such winding spindles are arranged cantilevered on a spindle carrier, so that the coils wound on the circumference of the winding spindles can be removed after completion from the free end of the winding spindle.
  • a winding spindle is known for example from DE 195 48 142 AI.
  • the known winding spindle has a chuck, on the circumference of a clamping jacket is arranged with a clamping device for receiving winding tubes.
  • the chuck is hollow cylindrical and has a hub in a longitudinal section, which is connected to a drive shaft.
  • the drive shaft is designed in several parts and executed by a rear bearing shaft and a front bearing shaft, wherein the rear bearing shaft is coupled with a drive and wherein the front bearing shaft is connected to the hub of the chuck.
  • the weight of the chuck is received via a bearing of the front bearing shaft, which is formed within a hollow carrier.
  • the hollow beam is likewise auskra- attached to the spindle carrier, wherein a free end of the hollow carrier protrudes into the interior of the chuck.
  • the material of the O-rings is basically designed for a sealing function and not for vapors and springs.
  • the double bushings require a relatively large installation space, which weakens the rigidity of the hollow beam. It is an object of the invention to form a generic winding spindle such that, despite limited outside diameter, very long projecting chucks for relatively high winding speeds can be realized. Another object of the invention is to provide a winding spindle in which the chuck can be used over several critical winding speeds.
  • each of the damping rings is formed from an inner sleeve and an outer sleeve enclosing the inner sleeve at a distance, and wherein the inner sleeve and the outer sleeve are elastically connected to one another by a rubber element.
  • the invention is characterized in that the installation space is independent of the respective rubber element and is determined solely by the diameter of the inner sleeve and the outer sleeve.
  • the spring characteristic of the rubber element between the inner sleeve and the outer sleeve can therefore be formed before installation with predetermined damping characteristics.
  • the damping rings can be combined directly with the storage, so that constructive weakenings can be omitted by receiving grooves or by additional support members.
  • the damping rings can be formed such that a width of the inner sleeve is smaller, equal to or greater than a width of the outer sleeve.
  • the mobility of the inner sleeve relative to the outer sleeve and vice versa can be positively influenced.
  • the development of the invention is preferably carried out, in which the width of the inner sleeve and / or the width of the outer basedhülse is at least 10 mm.
  • the bearing of the front bearing shaft is preferably formed within a bearing bush, at least two of the damping rings are held at opposite end portions of the bearing bush, which are respectively supported with the inner ring on the bearing bush and the outer ring on the hollow shaft.
  • the location of the damping rings on the bearing bush is not limited to the ends of the bearing bush. It results from the machine-dynamic calculations and interpretations.
  • the development of the invention has proven to be provided in which between the front bearing shaft and the hollow support axially offset from the storage axially staggered additional damping bearing and wherein the damping bearing has a much lower radial stiffness compared to the damping rings of the storage , Thus, essentially no loads are absorbed by the damping bearing.
  • the damping bearing is arranged in a shaft portion between the bearing and an end of the front bearing shaft connected to the chuck. The positioning of the damping bearing in the vicinity of the connection point to the chuck shows a high attenuation both at critical winding speeds in the lower region and at critical winding speeds in the upper region.
  • the damping bearing is preferably formed from a rolling bearing and a damping ring, which is directly supported on an outer ring of the rolling bearing.
  • the rolling bearing forms the outgoing from the rotating bearing shaft articulation point for the damping ring.
  • the Au s Inserts variant of the invention is preferably used, in which the rolling bearing two damping rings are assigned, which are arranged laterally next to the rolling bearing and each support a collar sleeve on the outer ring of the bearing. This makes it possible to position the damping rings next to the rolling bearing.
  • the winding machine according to the invention is characterized in particular by the fact that a plurality of winding points can be formed on the projecting winding spindle. Due to the effective and predeterminable damping characteristics can be realized length-diameter ratios of the winding spindles, which are increased by at least 60% over the winding spindles known in the prior art.
  • Fig. 1 shows schematically a cross-sectional view of a first embodiment of the winding spindle according to the invention
  • FIG. 2 schematically shows a cross-sectional view of a damping ring of the exemplary embodiment from FIG. 1.
  • Fig. 3 shows schematically a cross-sectional view of another embodiment of a damping ring
  • Fig. 4 shows schematically a cross-sectional view of another embodiment of the winding spindle according to the invention
  • Fig. 5 shows schematically a diagram with a curve of a dynamic characteristic of the winding spindle
  • Fig. 6 shows schematically another embodiment of a damping bearing
  • Fig. 7 shows schematically a view of a winding machine according to the invention
  • FIG. 1 schematically shows a cross-sectional view of a first exemplary embodiment of a winding spindle in a partial view.
  • the winding spindle 2 is held by a hollow carrier 11 on a spindle carrier 1.
  • the winding spindle 2 has a long projecting chuck 3, which is formed as a hollow cylinder at both ends.
  • the free end of the chuck 3 is not shown in Fig. 1, since no components relevant to the invention are included therein.
  • the free end of the chuck 3 is closed by a lid.
  • the opposite the spindle carrier 2 facing open end of the chuck 3 serves to receive a drive shaft 7 which is connected by a shaft-hub connection 15 with a hub 6 of the chuck 3.
  • the drive shaft 7 is formed of a front bearing shaft 7.1 and a rear bearing shaft 7.2, via a clutch 9 are coupled together.
  • couplings are preferably used which transmit only torsional but no bending moments.
  • the coupling 9 has at least means for torsional damping in order to decouple the front bearing shaft 7.1 from the rear bearing shaft 7.2.
  • the front bearing shaft 7.1 is rotatably supported via a front bearing 8.1 in the hollow beam 11.
  • the hollow support 11 projects for this purpose with a free end into the interior of the chuck 3.
  • the spindle carrier 1 facing the end of the chuck 3 surrounds the projecting hollow support 11 at a distance, so that the chuck 3 can rotate relative to the fixed hollow support 11.
  • the front bearing 8.1 of the front bearing shaft 7.1 is arranged.
  • the front bearing 8.1 is formed in this embodiment by two rolling bearings 16.1 and 16.2, which are held with their inner rings on the circumference of the front bearing shaft 7.1 and which are supported with their outer rings on a bearing bush 12.1.
  • a plurality of damping rings are provided on the circumference of the bearing bush 12.1.
  • two damping rings 13.1 and 13.2 are provided, which are each arranged in the end regions of the bearing bush 12.1.
  • one of the damping rings 13.2 in the vicinity of the shaft-hub connection 15 between the front bearing shaft 7.1 and the chuck 3 is positioned.
  • the bearing bush 12.1 protrudes beyond the rolling bearing 16.2, so that the damping ring 13.2 is arranged offset in the axial direction to the rolling bearing 16.2.
  • the structure of the damping rings 13.1 and 13.2 is identical. In order to explain the construction, reference is additionally made to FIG. 2. 2, an embodiment of the damping ring 13.1 and 13.2 is shown in a cross-sectional view.
  • the damping ring 13.1 or 13.2 has an inner sleeve 19 and a distance from the inner sleeve 19 enclosing outer sleeve 18. Between the inner sleeve 19 and the outer sleeve 18, a rubber element 20 is arranged.
  • the rubber element 20 is fixedly connected to the inner sleeve 19 and the outer sleeve 18 and forms a rubber spring. Thus, the inner sleeve 19 and the outer sleeve 18 can be moved relative to each other.
  • the inner sleeve 19 and the outer sleeve 18 are preferably formed of a metal, so that the rubber element can be fixed by vulcanization between the inner sleeve and the outer sleeve.
  • the rubber element 20 acting as a rubber spring can be adapted to the installation site and also to the respective operating state occurring at the installation location, both from the material and from the material characteristic.
  • the outer sleeve 18 and the inner sleeve 19 can be produced precisely with narrow manufacturing tolerances, so that unacceptable deformations are advantageously avoided when installing the sealing rings 13.1 and 13.2.
  • slight tolerance deviations within the installation space due to the mobility of the outer sleeve 18 and the inner sleeve 19 can be compensated to a certain extent without negatively influencing the spring-damper characteristic of the rubber element 20.
  • the damping rings 13.1 and 13.2 are supported in each case via the inner sleeves 19 on the circumference of the bearing bush 12.1.
  • the outer sleeves 18 of the damping rings 13.1 and 13.2 are based directly on the fixed hollow beam 11 from.
  • the relative movements between the front bearing shaft 7.1, which is excited via the chuck 3 can be transmitted directly via the bearing 7.1 into the damping mechanism.
  • the advantageous properties of the damping rings are also used to decouple a rear bearing 8.2 of the rear bearing shaft 7.2 of the hollow beam 11.
  • the rear bearing 8.2 is also formed in this embodiment by two rolling bearings 17.1 and 17.2, which are held between the rear bearing shaft 7.2 and a bearing bush 12.2.
  • two further damping rings 14.1 and 14.2 are arranged at the periphery of the bearing bush 12.2 .
  • the damping rings 14.1 and 14.2 are supported in a portion of the hollow support 11, which is held directly on the spindle carrier 1.
  • the rear bearing 7.2 is formed at the end of the hollow carrier 11.
  • the rear bearing shaft 7.2 protrudes with a drive end outside of the hollow support 11, wherein the drive end is designed as a coupling end 10.
  • a spindle drive could be coupled directly to the drive shaft 7 via the coupling end 10.
  • the clamping device 4 and the clamping jacket 5 are well known in the art and therefore not further explained here.
  • the clamping device 4 and the clamping jacket 5 could, for example, be designed in accordance with the exemplary embodiment according to WO 2011/086142 A1. In that regard, reference is made at this point to the cited document.
  • the decisive for receiving the Spulhülsen size is determined by a nominal diameter D of the clamping jacket 5.
  • the nominal diameter D of the clamping jacket 5 is usually identical to an inner diameter of the winding tube taking into account a radial play in the range of 0.5 mm to 1 mm.
  • the usable length for receiving winding tubes is indicated in FIG. 1 by a nominal length L of the clamping jacket 5.
  • the nominal length L thus represents a measure of the cantilevered length of the chuck 3.
  • damping ring 19 different types are shown, as it would be used, for example, as a damping ring 13.1 and 13.2 or as a damping ring 14.1 and 14.2.
  • the inner sleeve 19 is designed with a smaller in relation to the outer sleeve 18 width.
  • the width of the inner sleeve 19 is here marked with b r and the width of the outer sleeve 18 with the code letter b A.
  • the relationship bi ⁇ b A therefore applies, the rubber element 20 having at most the width of the inner sleeve 19.
  • the design of the damping ring according to FIG. 3 has a width smaller outer sleeve 18 relative to the inner sleeve 19.
  • the rubber element 20 has a maximum width of the outer sleeve 30.
  • the minimum width of the inner sleeve 19 or the outer sleeve 18 is limited due to the static loads to be transmitted between the chuck 3 and the hollow beam 11.
  • the width of the inner sleeve or the width of the outer sleeve is at least 10 mm depending on the design.
  • large widths of the inner sleeve 19 and the outer sleeve 18 are avoided in order to obtain a concentration of the articulation point for initiating the movements.
  • the damping rings are used within the winding spindle 2 with a maximum of a width of the inner sleeve or width of the outer sleeve of 50 mm.
  • the wider sleeve can be used to fix the damping ring with a stop.
  • FIG. 4 shows a cross-sectional view of the drive end of the winding spindle 2.
  • FIG. 4 is substantially identical to the embodiment of FIG. 1, so that at this point only the subordinate be explained and otherwise reference is made to the above description.
  • the drive shaft 7 is assigned an additional damping means in the form of a damping bearing 21.
  • the damping bearing 21 is arranged axially offset in a shaft portion of the front bearing shaft 7.1 outside the front bearing 8.1.
  • the damping bearing 21 is associated with the shaft end of the front bearing shaft 7.1 and held in the vicinity of the shaft-hub connection 15. In this case, the damping bearing 21 extends between the front bearing shaft 8.1 and the free projecting end of the hollow beam 11.
  • the damping bearing 21 points in This embodiment, a rolling bearing
  • the rolling bearing 21.1 is held with an inner ring on the circumference of the front bearing shaft 7.1 and carries on the outer ring the damping ring 21.2.
  • the damping ring can be
  • the damping ring 21.2 is designed in accordance with one of the types shown in FIGS. 2 and 3. In this case, however, the rubber element 20 of the damping ring 21.2 has a substantially lower radial rigidity in order to obtain a soft connection of the damping bearing 21.
  • the damping bearing 21 is positioned such that substantially no loads act on the damping bearing 21 and only when resonances occur, the damping bearing 21 is effective.
  • the Einmss of the damping bearing 21 and in particular the influence and use of the damping rings 13.1 and 13.2 in the area of the front bearing 7.1 can be represented in particular on the basis of a dynamic characteristic of the winding spindle 2.
  • the dynamic parameter is designated here by the code letter K.
  • the maximum winding speed is designated by v spu i, max , the maximum winding speed in the case of the winding machines known in the prior art being equal to a critical winding speed is.
  • the reference character D stands for the nominal diameter of the chuck as already explained above with reference to FIG.
  • the reference character L indicates the nominal length of the chuck for receiving the winding tubes.
  • the dynamic characteristic K takes into account in addition to complex rotor dynamic relationships, in particular the damping measures and vibration behavior of the chuck. In today's usual designs of such winding spindles, the dynamic parameter K lies in the rich between the values 8 to 10. In this case, the dynamic characteristic K as a function of a ratio between nominal length and nominal diameter (L / D) determines a maximum permissible winding speed (v), which is equal to a critical winding speed limiting the winding area.
  • the maximum permissible winding speed relative to a length-to-diameter ratio L / D of the chuck is plotted in a diagram for this purpose.
  • the maximum permissible winding speed is entered for each ratio value L / D.
  • the winding spindle according to the invention offers the particular advantage that the number of winding tubes to be accommodated and thus the realization of winding stations in a winding machine can almost be doubled compared to conventional winding spindles.
  • the length-diameter ratio of the chuck is increased by at least 60% in the winding machine according to the invention.
  • the use and positioning of the damping rings as well as the coordination of the types to each other shows a surprising decisive effect in order to influence the operating range of the winding spindles.
  • the damping bearing was additionally integrated on the front bearing shaft.
  • the diagram serves to illustrate possible dynamic improvements of the winding spindle according to the invention.
  • FIG. 6 An embodiment of a possible damping bearing 21 is shown schematically in a cross-sectional view in FIG.
  • a rolling bearing 21.1 is arranged on the circumference of the front bearing shaft 7.1.
  • the rolling bearing 21.1 is formed in this embodiment by two spindle bearings 23.1 and 23.2, which are held in an O-arrangement.
  • the bearing 8.1 of the front bearing shaft 7.1 is completely unaffected and it ensures a secure guidance and positioning of the damping ring 21.2.
  • the damping rings 21.2 and 21.2 ' are identical to the aforementioned embodiment of the sealing rings executed. in this respect can the height of the damping bearing 21 is considerably reduced, so that neither a weakening of the drive shaft 7 nor a weakening of the hollow support 11 within the winding spindle are required.
  • FIG. 7 an embodiment of the winding machine according to the invention is shown schematically.
  • the on winding machine has two long projecting winding spindles 2.1 and 2.2, which are held on a spindle carrier 1.
  • the spindle carrier 1 is designed as a winding turret, which is rotatably mounted in a machine frame 24.
  • the winding spindles 2.1 and 2.2 are designed according to one of the exemplary embodiments according to FIG. 1 or FIG. 4.
  • the winding spindles 2.1 to 2.2 are each assigned two spindle motors 26.1 and 26.2.
  • the number of winding positions depends on the manufacturing process, whether textile or technical threads need to be wound up. It is exemplary in this embodiment and could be used in the winding of technical threads or carpet threads in the variant shown.
  • the winding stations 25.1 to 25.4 is associated with a pressure roller 30 and a traversing device 29, wherein the traversing device 29 for each winding point 25.1 to 25.4 each thread guide means for reciprocating one of the threads.
  • the pressure roller 30 is held on a movable roller carrier 32.
  • the inlet of the threads is guided over a respective head thread guide 31, which form the inlet of the winding points 25.1 to 25.4.
  • a plurality of winding tubes 28 are spanned side by side on the winding spindles 2.1 and 2.2.
  • the winding spindles 2.1 and 2.2 each have long projecting chucks, as described in the aforementioned embodiments of FIGS. 1 and 4.
  • the usable length L and the nominal diameter D of the chuck is characterized by the example of the winding spindle 2.2 in FIG.
  • the winding machine according to the invention is suitable for all common melt spinning processes to wind freshly extruded threads as a group of threads parallel to coils.
  • the synthetic yarns produced in a POY, FDY or IDY melt spinning process can be wound into coils in a yarn bundle having a plurality of yarns simultaneously.
  • the winder is also suitable for BCF processes to wind several crimped filaments into spools.

Landscapes

  • Winding Filamentary Materials (AREA)
  • Support Of The Bearing (AREA)

Abstract

L'invention concerne une broche de bobinage destiné au bobinage de fils dans une bobineuse. A cet effet, la broche de bobinage comporte un long mandrin saillant (3) destiné à recevoir une pluralité de bobinots, le mandrin pouvant être entraîné par un arbre d'entraînement (7) en plusieurs parties, qui est monté dans un support creux (11), et un arbre de palier arrière (7,2) étant accouplé à un entraînement. Un arbre de palier avant (7.1), accouplé à l'arbre de support arrière, est couplé au mandrin et est monté dans le support creux par le biais d'un palier (8.1). Une pluralité de bagues d'amortissement (13.1, 13.2) agissent entre le palier et le support creux. Selon l'invention, pour pouvoir amortir des vitesses de bobinage critiques du mandrin de façon uniforme et intense, chacune des bagues d'amortissement est formée d'un manchon intérieur (19) et d'un manchon extérieur (18) entourant le manchon intérieur (19) à une certaine distance, le manchon intérieur et le manchon extérieur étant reliés entre eux de manière élastique par un élément en caoutchouc (20).
PCT/EP2016/055085 2015-03-17 2016-03-10 Broche de bobinage Ceased WO2016146465A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2017549039A JP7002939B2 (ja) 2015-03-17 2016-03-10 巻取りスピンドル
CN201680015749.0A CN107428489B (zh) 2015-03-17 2016-03-10 卷绕锭子
DE112016001265.9T DE112016001265A5 (de) 2015-03-17 2016-03-10 Spulspindel

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015003444.8 2015-03-17
DE102015003444 2015-03-17

Publications (1)

Publication Number Publication Date
WO2016146465A1 true WO2016146465A1 (fr) 2016-09-22

Family

ID=55521718

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2016/055085 Ceased WO2016146465A1 (fr) 2015-03-17 2016-03-10 Broche de bobinage

Country Status (4)

Country Link
JP (1) JP7002939B2 (fr)
CN (1) CN107428489B (fr)
DE (1) DE112016001265A5 (fr)
WO (1) WO2016146465A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN118004824A (zh) * 2024-03-14 2024-05-10 北京中丽制机工程技术有限公司 一种卷绕锭子及纺丝卷绕机

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2985181T3 (es) * 2019-09-10 2024-11-04 Rockwool As Rotor

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB553760A (en) * 1942-01-28 1943-06-03 Wright Howard Clayton Improvements in or relating to bearings
GB1421060A (en) * 1972-12-16 1976-01-14 Barmeg Barmer Maschinenfabrik Winding machine
DE2935218A1 (de) * 1979-08-31 1981-03-26 Barmag Ag, 42897 Remscheid Spindel fuer hohe drehzahlen
DE19548142A1 (de) * 1995-12-22 1997-06-26 Barmag Barmer Maschf Aufspulvorrichtung
EP1024102A2 (fr) * 1999-01-29 2000-08-02 Murata Kikai Kabushiki Kaisha Support de bobine
DE10036861A1 (de) * 1999-07-29 2001-04-12 Barmag Barmer Maschf Aufspulvorrichtung
JP2003081532A (ja) * 2001-09-13 2003-03-19 Toray Ind Inc ボビンホルダ
DE102009021647A1 (de) * 2009-05-16 2010-11-18 Schaeffler Technologies Gmbh & Co. Kg Wellensystem für den Einsatz in einem Spannfutter eines Spulkopfes
DE102012104249A1 (de) * 2012-05-16 2013-11-21 Carl Freudenberg Kg Vorrichtung zum Andrücken eines Fadens an eine Spule

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2244197A (en) * 1936-03-25 1941-06-03 Hessler Christian Rudolph Bearing
JPS5142214B2 (fr) * 1972-12-16 1976-11-15
JPH0679958B2 (ja) * 1988-10-07 1994-10-12 東レ株式会社 糸条の巻取装置
CN2057249U (zh) * 1989-09-18 1990-05-16 宗连台 弹性阻尼轴承
DE4005708A1 (de) * 1990-02-23 1991-08-29 Jakob Ludwig Bewegliche kupplung in schalenbauweise
JPH05338914A (ja) * 1992-06-13 1993-12-21 Teijin Seiki Co Ltd 糸条の巻取装置
JP3198736B2 (ja) * 1993-07-14 2001-08-13 東レ株式会社 ボビン把持装置およびボビンホルダ
DE19616314A1 (de) * 1995-05-17 1996-11-21 Barmag Barmer Maschf Aufspulvorrichtung zum Aufspulen von Chemiefasern mit einer Spulspindel
JP2000255899A (ja) 1999-03-12 2000-09-19 Teijin Seiki Co Ltd 糸条の巻取機におけるボビンホルダ
DE10037201A1 (de) * 1999-08-03 2001-02-15 Barmag Barmer Maschf Aufspulvorrichtung
CH695563A5 (de) * 2000-10-13 2006-06-30 Saurer Gmbh & Co Kg Vorrichtung zum Führen oder Aufwickeln eines laufenden Fadens.
JP3998473B2 (ja) * 2001-11-28 2007-10-24 Ｔｓｔｍ株式会社 ボビンホルダー
DE10300404A1 (de) * 2002-02-06 2003-08-14 Barmag Barmer Maschf Aufspulvorrichtung
DE102010004562A1 (de) * 2010-01-14 2011-07-21 Oerlikon Textile GmbH & Co. KG, 42897 Spulspindel
JP2013193819A (ja) * 2012-03-16 2013-09-30 Tmt Machinery Inc ボビンホルダー及びボビンホルダーを備える糸巻取機

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB553760A (en) * 1942-01-28 1943-06-03 Wright Howard Clayton Improvements in or relating to bearings
GB1421060A (en) * 1972-12-16 1976-01-14 Barmeg Barmer Maschinenfabrik Winding machine
DE2935218A1 (de) * 1979-08-31 1981-03-26 Barmag Ag, 42897 Remscheid Spindel fuer hohe drehzahlen
DE19548142A1 (de) * 1995-12-22 1997-06-26 Barmag Barmer Maschf Aufspulvorrichtung
EP1024102A2 (fr) * 1999-01-29 2000-08-02 Murata Kikai Kabushiki Kaisha Support de bobine
DE10036861A1 (de) * 1999-07-29 2001-04-12 Barmag Barmer Maschf Aufspulvorrichtung
JP2003081532A (ja) * 2001-09-13 2003-03-19 Toray Ind Inc ボビンホルダ
DE102009021647A1 (de) * 2009-05-16 2010-11-18 Schaeffler Technologies Gmbh & Co. Kg Wellensystem für den Einsatz in einem Spannfutter eines Spulkopfes
DE102012104249A1 (de) * 2012-05-16 2013-11-21 Carl Freudenberg Kg Vorrichtung zum Andrücken eines Fadens an eine Spule

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN118004824A (zh) * 2024-03-14 2024-05-10 北京中丽制机工程技术有限公司 一种卷绕锭子及纺丝卷绕机

Also Published As

Publication number Publication date
JP2018512348A (ja) 2018-05-17
JP7002939B2 (ja) 2022-01-20
CN107428489A (zh) 2017-12-01
CN107428489B (zh) 2020-12-18
DE112016001265A5 (de) 2017-11-23

Similar Documents

Publication Publication Date Title
DE102010044107B4 (de) Spulenhalter
EP2523884A1 (fr) Broche à bobine
EP1456108B1 (fr) Broche a bobiner a frequence propre accrue
DE102016006148A1 (de) Aufspulmaschine
EP2429932B1 (fr) Système d'arbres destiné à être utilisé dans un mandrin de serrage d'une tête de bobinage
DE3780188T3 (de) Spulmaschine.
WO2016146465A1 (fr) Broche de bobinage
DE2643060B2 (de) Spulspindellagerung
WO2016150737A1 (fr) Broche de bobinage
DE2343776A1 (de) Vorrichtung zum uebertragen von garndrehungen bei ringspinnmaschinen
DE102015002963A1 (de) Aufspulmaschine
DE10218993A1 (de) Hülsenteller für einen Spulenrahmen
WO2016146464A1 (fr) Bobineuse
WO2005115896A1 (fr) Enrouleuse
WO2017129512A1 (fr) Bobinoir
EP2949612A1 (fr) Dispositif de bobinage pour une machine textile fabriquant des bobines croisées
DE19705872A1 (de) Ringspinn- oder Ringzwirnmaschine
EP4227247B1 (fr) Tambour à fente pour une bobineuse et bobineuse
WO2020105006A1 (fr) Broche d'un métier à filer à anneaux
CH695563A5 (de) Vorrichtung zum Führen oder Aufwickeln eines laufenden Fadens.
WO2016150767A1 (fr) Broche de bobinage
EP3670718A1 (fr) Métier à filer à anneaux pourvu de bancs d'étirage
DE102017006865A1 (de) Aufspulmaschine
DE10300404A1 (de) Aufspulvorrichtung
WO2018185145A1 (fr) Bobineuse

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 16709059

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2017549039

Country of ref document: JP

Kind code of ref document: A

WWE Wipo information: entry into national phase

Ref document number: 112016001265

Country of ref document: DE

REG Reference to national code

Ref country code: DE

Ref legal event code: R225

Ref document number: 112016001265

Country of ref document: DE

122 Ep: pct application non-entry in european phase

Ref document number: 16709059

Country of ref document: EP

Kind code of ref document: A1