EP0654097A1 - Ensemble de cylindres-etireurs. - Google Patents

Ensemble de cylindres-etireurs.

Info

Publication number
EP0654097A1
EP0654097A1 EP94916118A EP94916118A EP0654097A1 EP 0654097 A1 EP0654097 A1 EP 0654097A1 EP 94916118 A EP94916118 A EP 94916118A EP 94916118 A EP94916118 A EP 94916118A EP 0654097 A1 EP0654097 A1 EP 0654097A1
Authority
EP
European Patent Office
Prior art keywords
vibration damper
housing
stretching roller
support cylinder
damping
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.)
Granted
Application number
EP94916118A
Other languages
German (de)
English (en)
Other versions
EP0654097B1 (fr
Inventor
Armin Wirz
Kurt Wetter
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.)
Maschinenfabrik Rieter AG
Original Assignee
Maschinenfabrik Rieter AG
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 Maschinenfabrik Rieter AG filed Critical Maschinenfabrik Rieter AG
Publication of EP0654097A1 publication Critical patent/EP0654097A1/fr
Application granted granted Critical
Publication of EP0654097B1 publication Critical patent/EP0654097B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • D—TEXTILES; PAPER
    • D02—YARNS; MECHANICAL FINISHING OF YARNS OR ROPES; WARPING OR BEAMING
    • D02J—FINISHING OR DRESSING OF FILAMENTS, YARNS, THREADS, CORDS, ROPES OR THE LIKE
    • D02J13/00—Heating or cooling the yarn, thread, cord, rope, or the like, not specific to any one of the processes provided for in this subclass
    • D02J13/005—Heating or cooling the yarn, thread, cord, rope, or the like, not specific to any one of the processes provided for in this subclass by contact with at least one rotating roll
    • H—ELECTRICITY
    • H05—ELECTRIC TECHNIQUES NOT OTHERWISE PROVIDED FOR
    • H05B—ELECTRIC HEATING; ELECTRIC LIGHT SOURCES NOT OTHERWISE PROVIDED FOR; CIRCUIT ARRANGEMENTS FOR ELECTRIC LIGHT SOURCES, IN GENERAL
    • H05B6/00—Heating by electric, magnetic or electromagnetic fields
    • H05B6/02—Induction heating
    • H05B6/10—Induction heating apparatus, other than furnaces, for specific applications
    • H05B6/14—Tools, e.g. nozzles, rollers, calenders
    • H05B6/145—Heated rollers

Definitions

  • the invention relates to a draw roll unit for draw-bobbin, spin-draw-winder and draw-twisting machines according to the preamble of the first claim.
  • Such stretching roller units are known, for example from the European patent applications with the publication numbers 0 349 829 A2 and 0 454 618 AI, both applications of the applicant of the current patent application.
  • Such stretching roller units have a high operating speed, for example to convey and heat filament threads up to 6000 m / min and more on the heated godets.
  • a godet alone can have a weight of, for example, 25 kg, so that the combination of mass and high speed inevitably leads to vibrations which are transmitted within the stretching roller assembly and resonances can arise which can cause malfunctions in operation.
  • vibrations can be prevented in various ways, including measures relating to the weight and rigidity of the parts that start to vibrate or, on the other hand, by appropriate provision of vibration-damping elements at suitable points.
  • the advantage of the invention is that it is an effective, yet simple solution.
  • FIG. 1 shows a stretching roller unit according to the invention in longitudinal section, shown schematically,
  • FIG. 2 shows a variant of FIG. 1,
  • FIG. 4 shows a variant of a detail of the stretching roller assembly. gates of Fig. 3,
  • FIG. 5 shows a detail of the stretching roller unit from FIGS. 1 and 2, shown enlarged
  • FIG. 6 shows a variant of the detail from FIG. 5,
  • Fig. 8b shows the detail of Fig. 8a in viewing direction A (Fig. 8a)
  • FIG. 9a shows the detail according to the invention from FIG. 9, shown separately and in a side view
  • Fig. 9b shows the detail of Fig. 9a in viewing direction B (Fig.9a)
  • FIG. 12a shows a variant of a detail from FIG. 12,
  • FIG. 13a is an enlarged view of the inventive detail of FIG. 13,
  • FIG. 13b shows the detail of FIG. 13a in viewing direction C (FIG. 13a)
  • FIG. 16 shows a variant of FIG. 15 according to the invention, only the upper half, viewed with a view of FIG. 15.
  • a stretching roller unit 1 with a godet 2 and an electric motor 3 with a shaft 8, which at the end of the godet is provided with a conical end section 13 for receiving a hub 12 and is part of an end wall 11 of the godet 2. Furthermore, a jacket wall 10 is connected to the end wall 11, on which the filament (not shown) rests in several loops in a manner known per se during operation.
  • An inductor 16 with an intermediate space 15 to the jacket wall 10 is provided within the jacket wall 10 around the shaft 8 and is received by a support cylinder 18.
  • deflections of the godet which are caused by radial forces due to the rotation of the godet and the resulting vibrations and natural vibrations of the inductor, are shown purely schematically with the arrows N and M shown.
  • the support cylinder 18 has at its end opposite the motor 3 a support cylinder flange 9 which is centered in the radial direction by means of a centering ring 24 belonging to a motor housing 23.
  • a centering ring 24 belonging to a motor housing 23.
  • an annular or a number of annularly arranged vibration dampers is provided between the support cylinder flange 9 and a motor housing end wall 32 in order to avoid vibrations being transmitted mainly in the axial direction from the motor housing 23 to the support cylinder 18 and thus to the inductor 16 become.
  • the support cylinder flange 9 is by means of a compression spring 25 which is provided between the support cylinder flange 9 and a screw 26 and which exerts a force in the axial direction against the support cylinder flange 9 when the screw 26 is tightened up to a stop 35 shown in FIGS. 5 and 6, pressed against the motor housing end wall 32.
  • a rotor 22 is received within the motor housing 23 by the shaft 8, which in turn is rotatably supported within the motor housing 23 by means of roller bearings 20 and 21.
  • the godet 2 is firmly connected to the shaft 8 by means of a screw 14.
  • a vibration damper ring 30 is additionally provided between the centering ring 24 and the support cylinder flange 9, or alternatively a number of ring-shaped vibration dampers are provided, which in addition to the axially directed vibration damping by dampens or dampens radially directed vibrations the vibration damper 27.
  • FIG. 3 shows a variant of a stretching roller unit, which is identified here by 1.1.
  • the same elements which have already been described in connection with FIGS. 1 and 2 or have the same function have the same reference symbols here, except that the vibration damper 27 of FIGS. 1 and 2 is identified here by 27.1 and that the support cylinder flange 9 is centered by means of a cylinder part 31 which surrounds the housing flange 49 and belongs to the support cylinder flange 9.
  • the motor 3.1 is not arranged directly next to the godet 2, but is fastened to a housing 17 in which the shaft 8 is rotatably mounted by means of the roller bearings 4, 5, 6 and 7.
  • the symmetry axis of the inductor 16 lies coaxially with the axis of rotation 29 of the shaft 8, which is shown with the geometric axis 34.
  • FIG. 4 shows a detail from FIG. 3, in particular with a vibration damper 30.1, which, like the vibration damper 30 of FIG. 2, dampens the deflections in the radial direction and between a cylinder part 31 of the support cylinder flange 9 and the bearing housing end wall 49 is seen.
  • a vibration damper 30.1 which, like the vibration damper 30 of FIG. 2, dampens the deflections in the radial direction and between a cylinder part 31 of the support cylinder flange 9 and the bearing housing end wall 49 is seen.
  • FIG. 4 does not have a compression spring 25, as shown in FIGS. 1 to 3, but a vibration damper 33, which is provided between each screw 26 and the support cylinder flange 9 .
  • This vibration damper on the one hand has the function of the compression spring 25 and on the other hand additionally dampens the function of certain axially directed vibrations.
  • FIG. 7 shows a spring pin 38 which is fixedly inserted with its rear part in the support cylinder flange 9.1 and which on the front part carries a radially acting vibration damper 30.2 consisting of a hollow cylindrical damping element, which is provided in a front wall 49.1 of the bearing housing Bore of the housing 17 is inserted.
  • the spring pin 38 and the vibration damper 30.2 form a vibration damper unit 30.A.
  • annular disk-shaped vibration damper 27.2 acting in the axial direction of the shaft 8 is provided between the end wall 49.1 of the bearing housing and the support cylinder flange 9.1.
  • the support cylinder flange 9.1 is pressed against the bearing housing end wall 49.1 by means of the screw 26 and the compression spring 25 provided on the screw 26, but only in such a way that the vibration damper 27.2 is able to transmit the radial vibrations to the spring pin 38 or to be transmitted to the vibration damper 30.2, that is to say that a relative movement between the support cylinder flange 9.1 and the bearing housing end wall 49.1 is possible.
  • the units 30.A formed from the spring pin 38 and the vibration damper 30.2 are evenly distributed over the circumference, the screw 26 being shown directly above this unit in FIG. 7, but expediently between two circumferentially distributed units made of spring pin 38 and vibration damper 30.2 is provided, which also applies to all circumferentially distributed vibration dampers.
  • FIG. 8 shows, instead of the two-part radial and axial damping means shown in FIG. 7, a damping means consisting of a single ring-shaped element which, on the one hand, consists of a radially acting ring-shaped vibration damper 30.3 of essentially octagonal cross section and, on the other hand composed of the axially effective ring-shaped vibration damper 27.3.
  • the octagonal cross-section of the vibration damper 30.3 is contained in annular grooves 61, one annular groove being embedded in the end wall 49.2 of the bearing housing and the other in the cylinder flange 9.2 of the supporting cylinder 18.
  • FIG. 8a shows separately the vibration-damping element shown in FIG. 8, consisting of the ring-shaped vibration damper 27.3, which is the axially directed one Dampens vibrations, and the vibration damper 30.3 connected to the circumference thereof, which dampens the radially directed vibrations.
  • FIG. 8b is a top view of FIG. 8a in viewing direction A with the illustration of vibration dampers 27.3 and 30.3.
  • Fig. 9 shows a variant of the radial and axial damping element of Fig. 8, which is also made from one piece, which is here instead of the octagonal, radially acting damping element 30.3 is a vibration damper with opposite cylindrical knobs 30.4, which is uniform distributed around the circumference and arranged opposite the annular vibration damper 27.4.
  • the knobs 30.4 are each held in bores 50 of the same diameter, which are each provided in accordance with the number of knobs 30.4 in the bearing housing end wall 49.3 and in the support cylinder flange 9.3. At least three such pairs of knobs are uniformly provided on the circumference.
  • the knobs 30.4 absorb the radial vibrations and the ring-shaped vibration damper 27.4 the axial vibrations.
  • the bearing housing end wall 49.3 is clamped together with the support cylinder flange 9.3 by means of the screws 26 and the compression springs 25, which is only schematically indicated here with the screw axis 37, the distribution of these screws on the circumference being as symmetrical as the distribution of the knobs 30.4.
  • FIG. 9a shows separately the vibration damper according to the invention, namely the ring disk with the identification 27.4 as vibration damper for receiving axially directed vibrations and the knob-like cylinder with the Marking 30.4, which vibration dampers are for absorbing radially directed vibrations.
  • the vibration damper 30.4 are firmly connected to the vibration damper ring 27.4.
  • the radially acting vibration damper is a hollow cylindrical damping element 30.5 which, on the one hand, is free of play with its outer cylindrical surface is accommodated in a bore (not marked) in the support cylinder flange 9.4 of the support cylinder 18 and on the other hand receives an end part of a support bolt 39 without play, the other end part of which is received in the bearing housing end wall 49.4 of the housing 17 without play.
  • the vibration damper 30.5 and the support pin 39 form a vibration damper unit 30.B.
  • the axial vibrations are absorbed by an annular vibration damper 27.5, which is held between the bearing housing end wall 49.4 and the support cylinder flange 9.4 and is held by means of the screws 26 and the springs 25 a predetermined preload.
  • This preload is such that there is no play between the bearing housing end wall 49.4 and the support cylinder flange 9.4 and the annular vibration damper 27.5.
  • the vibration damper unit 30.B is distributed over a circumference with a predetermined regularity, for example evenly with three units.
  • 11 further shows that the radially acting vibration damper is a hollow cylindrical damping element 30.5, which is fixedly inserted in a bore (not marked) in the bearing housing end wall 49.5 of the housing 17. and that the damping element 30.5 is Fe ⁇ derteil 42 receives, at one end of the spring part 42, a support pin 41 is fixedly connected, which is free of play in the support cylinder flange 9.5 of the support cylinder 18 and at the other end, a support pin 41.1 which is embedded free of play in the housing 17.
  • the support bolt 41 and 41.1 and the spring part together with the vibration damper 30.5 form a vibration damper unit 30.C.
  • annular vibration damper 27.6 is provided, which, like already for the other annular vibration dampers, is provided preloaded between the end wall 49.5 of the bearing housing and the support cylinder flange 9.5. This pretension, as already described earlier, is generated by the screw 26 and the springs 25.
  • these damping elements consisting of the elements 41, 41.1, 42 and 30.5 are also distributed uniformly, circumferentially, preferably three such units being distributed over the circumference, which does not rule out a majority of them.
  • the screws 26 are also distributed over the circumference with the same or a different regularity.
  • FIG. 12 shows the ring flange 44 in the axial direction and parallel to it a cylindrical inner surface of the bearing housing end wall 49.6, it being only essential that the ring flange 44 and the aforementioned cylindrical inner surface lie essentially parallel to one another ⁇ gen, on the other hand, an exact axial alignment of these two opposing parallel surfaces is not necessary.
  • the two O-rings 30.6 and the spring pin 40 together with the oil form a vibration damper unit 30.D.
  • the axially directed vibrations are absorbed by an o-ring-shaped vibration damper 27.7, which is provided with a certain preload between the bearing housing end wall 49.6 and the support cylinder flange 9.6.
  • the pretension is generated by the screw 26 and the springs 25, which is shown schematically as an alternative to the axis 37.
  • the screws 26 can be provided evenly distributed over the circumference. 12a shows that instead of the O-rings 30.6 and the oil located between them, a full vibration damper 30.6.1 can be provided.
  • FIG. 13 shows an annular vibration damper 27.8, for damping the axially directed vibrations, which is held between the support cylinder flange 9.7 and the bearing housing end wall 49.7 as described above with a predetermined preload.
  • the vibration damper 27.8 has a passage 57 for a spring pin 38 which is fixedly received at one end in the support cylinder flange 9.7 and at the other end carries a slot sleeve 45 shown enlarged in FIG. 13a and provided with slots 58.
  • This slot sleeve 45 is surrounded by O-rings 51 with such a predetermined preload that the spring pin 38 receives the slot sleeve 45 without play.
  • Each O-ring is received in a groove 60 (not marked) embedded in the circumference of the slot sleeve in order not to change its position on the slot sleeve 45 even if the O-rings 51 together with the slot sleeve 45 are in a cylindrical recess 46, which is formed by a bore 52 provided in the end wall of the bearing housing (shown with dash-dotted lines in FIG. 13a).
  • the inside diameter of the bore 52 is provided in such a way that the inserted O-rings are pressed in the radial direction into the said grooves 60 and are thus held therein with a predetermined preload, so that in combination, on one side the spring pin 38, as before described, the O-rings are held in the bore 52 without play in the slot sleeve 45 and on the other hand without play.
  • the slot sleeve 45 and the O-rings form a radially acting vibration damper 30.7 and together with the spring pin they form a vibration damper unit 30.E. At least three such vibration damper units 30.7 are arranged circumferentially distributed, but there may also be more ⁇ as required.
  • vibration damper unit 30 E The advantage of such a vibration damper unit 30 E is that the end of the spring pin 38 located in the end wall 49.7 of the bearing housing can move, but without causing any play, since the pretension in the O-rings does not occur Clearance between the cylindrical bore 52 and the O-rings still allows between the spring pin 38 and the slot sleeve 45.
  • FIG. 13b shows the vibration damper 30.7 in viewing direction C, in which the elements with the same functions as in FIG. 13a are identified with the same identifiers.
  • FIG. 14 provides a variant of FIG. 3 between the housing 17 and the roller bearings 4, 5, 6 and 7, each with radially acting damping elements 30.12, in order to dampen the radial movements of the shaft 8 within the housing 17. 14 serves as a general starting point for the following description of FIGS. 15 and 16.
  • the adapter 53 is provided between the support cylinder flange 9.8 and a bearing housing end wall 49.8 belonging to the housing 17.
  • the adapter 53 has one end, seen in the axial direction of the shaft, against the Support cylinder flange 9.8 directed and is at the other end, that is with the adapter flange 54 on the Lagerge ⁇ housing end wall 49.8.
  • An annular vibration damper 27.8 is provided between the support cylinder flange 9.8 and the aforementioned end of the adapter 53, which dampens the axial vibrations.
  • the vibration damper 27.8 is provided with bores 55, which are provided coaxially with depressions 46.1, which each result from a bore 52.1 and have the same diameter as these depressions 46.1.
  • depressions 46.1 each serve to receive a radially acting vibration damper 30.7 known from FIG. 13.
  • the depression 46.1 corresponds to the depression 46 delimited by dash-dotted lines in FIG. 13a.
  • this figure is also a radially acting vibration damper unit 30.E which corresponds to that for FIG. 13, this vibration damper is also identified in this figure with 30.7. Furthermore, at least three such vibration damper units 30E are arranged distributed over the circumference, but there may also be more if required.
  • the support cylinder flange 9.8 is held together by means of screws 26 and spring elements 25 with a prestress in the ring-shaped vibration damper 27.8 with the adapter 53 such that the vibration damper 27.8 is able to process the axial vibrations.
  • the damped mounting of the shaft 8 is based on the same principle of vibration damping as for the support cylinder 18 provided that a spring pin 38 of a vibration damper 30.8 is firmly received in a bearing housing 48 which serves to receive the shaft bearings 6 and 7.
  • the vibration damper unit is marked here with 30.F.
  • the spring pin 38 receives a slot sleeve with O-rings 51, which is constructed analogously to FIG. 13a.
  • This slot sleeve-O-ring combination is also seated in a depression 46.2, which corresponds in principle to depression 46.1.
  • An adapter flange 54 belonging to the adapter 53 lies directly against the end wall 49.8 of the bearing housing and is connected to this by means of screws 26 and spring elements 25, which is shown schematically with the center line 37.1.
  • At least three vibration damping elements 30.7 or 30.8 should be provided in a uniform distribution over the circumference, the screw connections by means of the screws 25 not necessarily having to be arranged at the same location as the provision of the vibration dampers, but in a predetermined manner in between, which incidentally applies to all Connection with FIGS. 7, 10, 11, 13 or 15 and 16 shown and described screw connections applies.
  • FIG. 16 shows a variant of FIG. 15, in that the damping between the support cylinder 18 and the bearing housing 17 is carried out by means of an axially acting damping element 27.9, the damping element 27.9 being arranged between the support cylinder flange 9.9 and the bearing housing end wall 49.9 and in Principle corresponds to the damping element 27.3 already described for FIG. 8, that is to say that the trapezoidal elevations 30.10 are radial acting vibration damper between the support cylinder flange and bearing housing end wall.
  • the radial damping of the bearings 6 and 7 takes place by means of a radially acting vibration damper unit 30.C from FIG. 11, the vibration damper here being identified with 30.9 and the vibration damper unit with 30.G.
  • the bearings 6 and 7 are accommodated in a bearing housing 48.1, a support bolt 41 being fixedly arranged in the bearing housing 48.1, the opposite end 41.1 of which is accommodated in the housing 17 without play.
  • the part 42 accommodating the radially acting vibration damper 30.9, which on the one hand on a cylindrical inner wall 56 of the housing 17 and otherwise on the bearing housing part 59 and thereby radially dampens the vibrations caused by the shaft.
  • bearing damping can also be provided at the other end of the bearing housing (not shown here) in a mirror-image arrangement, specifically for bearings 4 and 5 (see FIG. 14).
  • FIGS. 1 and 2 there is no bearing housing, but that the shaft is mounted directly in the motor housing, and that the damping is carried out in the manner shown in FIG. 15 and 16 can be carried out directly in the motor housing. This means that the bearings 20 and 21 of FIG. 1 would be stored in the manner shown in FIGS. 15 and 16.
  • FIGS. 7 to 16 can also be used with the motor housing 3 shown with FIGS. 1 and 2 and 5 and 6.

Landscapes

  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Yarns And Mechanical Finishing Of Yarns Or Ropes (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

Pour éviter que les vibrations générées par la rotation d'une galette (2) ne soient transmises à l'inducteur (16) de chauffage de la galette, l'inducteur (16) est monté sur un amortisseur de vibrations (27) qui le garantit contre les vibrations. L'amortisseur de vibrations (27) est situé entre la bride (9) d'un cylindre (18) de support de l'inducteur (16) et une paroi frontale (32) du boîtier. Un anneau amortisseur supplémentaire (30) est monté à l'intérieur d'un anneau de centrage (24) afin d'amortir l'inducteur (16) dans le sens radial. La bride (9) est pressée contre l'amortisseur de vibrations (27) par des vis (26). Un ressort de pression (25) situé entre la vis (26) et la bride (9) comprime la bride (9).
EP94916118A 1993-06-04 1994-06-02 Ensemble de cylindres-etireurs Expired - Lifetime EP0654097B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
CH168093 1993-06-04
CH1680/93 1993-06-04
CH925/94 1994-03-28
CH92594 1994-03-28
PCT/CH1994/000104 WO1994029500A1 (fr) 1993-06-04 1994-06-02 Ensemble de cylindres-etireurs

Publications (2)

Publication Number Publication Date
EP0654097A1 true EP0654097A1 (fr) 1995-05-24
EP0654097B1 EP0654097B1 (fr) 1997-09-17

Family

ID=25686124

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94916118A Expired - Lifetime EP0654097B1 (fr) 1993-06-04 1994-06-02 Ensemble de cylindres-etireurs

Country Status (5)

Country Link
US (1) US5763859A (fr)
EP (1) EP0654097B1 (fr)
JP (1) JPH07509758A (fr)
DE (1) DE59404089D1 (fr)
WO (1) WO1994029500A1 (fr)

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JP2010277981A (ja) * 2009-04-28 2010-12-09 Tokuden Co Ltd 誘導発熱ローラ装置
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DE102010047103A1 (de) * 2010-09-29 2012-03-29 Carl Zeiss Jena Gmbh Flansch zum Abschluss eines optischen Geräts gegenüber einem Probenstrom und optisches Gerät zur teilweisen Anordnung in einem Probenstrom
EP2899414A1 (fr) * 2014-01-23 2015-07-29 Siemens Aktiengesellschaft Palier amorti d'arbre de rotor
ITUA20161409A1 (it) * 2016-03-07 2017-09-07 M A E S P A Giunto di trasmissione per un organo di avanzamento ed organo di avanzamento di materiale in fibra in una linea di filatura da laboratorio
US10156204B2 (en) * 2017-04-24 2018-12-18 Sunpower, Inc. Attachment of cylinders in the housing of free-piston stirling machines
CN110804783B (zh) * 2019-10-18 2020-12-01 桐乡越顺经编有限公司 一种用于纺织纱线加工的牵伸定型机构
DE102021002068A1 (de) 2020-05-14 2021-11-18 Oerlikon Textile Gmbh & Co. Kg Galettendämpfer

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Also Published As

Publication number Publication date
WO1994029500A1 (fr) 1994-12-22
EP0654097B1 (fr) 1997-09-17
DE59404089D1 (de) 1997-10-23
US5763859A (en) 1998-06-09
JPH07509758A (ja) 1995-10-26

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