EP0498852B1 - Verfahren zum verhindern von drehschwingungen in einer fadenspeicher- und -liefervorrichtung und fadenspeicher- und -liefervorrichtung - Google Patents

Verfahren zum verhindern von drehschwingungen in einer fadenspeicher- und -liefervorrichtung und fadenspeicher- und -liefervorrichtung Download PDF

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Publication number
EP0498852B1
EP0498852B1 EP91900243A EP91900243A EP0498852B1 EP 0498852 B1 EP0498852 B1 EP 0498852B1 EP 91900243 A EP91900243 A EP 91900243A EP 91900243 A EP91900243 A EP 91900243A EP 0498852 B1 EP0498852 B1 EP 0498852B1
Authority
EP
European Patent Office
Prior art keywords
thread
storage
rotary
shaft
oscillation 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.)
Expired - Lifetime
Application number
EP91900243A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0498852A1 (de
Inventor
Lars Helge Gottfrid Tholander
Pär JOSEFSSON
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.)
Iro AB
Original Assignee
Iro AB
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from SE8903711A external-priority patent/SE8903711D0/xx
Priority claimed from SE8903786A external-priority patent/SE8903786D0/xx
Priority claimed from SE8903807A external-priority patent/SE8903807D0/xx
Priority claimed from DE3938646A external-priority patent/DE3938646A1/de
Application filed by Iro AB filed Critical Iro AB
Publication of EP0498852A1 publication Critical patent/EP0498852A1/de
Application granted granted Critical
Publication of EP0498852B1 publication Critical patent/EP0498852B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D47/00—Looms in which bulk supply of weft does not pass through shed, e.g. shuttleless looms, gripper shuttle looms, dummy shuttle looms
    • D03D47/34—Handling the weft between bulk storage and weft-inserting means
    • D03D47/36—Measuring and cutting the weft
    • D03D47/361—Drum-type weft feeding devices
    • D03D47/362—Drum-type weft feeding devices with yarn retaining devices, e.g. stopping pins
    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D47/00—Looms in which bulk supply of weft does not pass through shed, e.g. shuttleless looms, gripper shuttle looms, dummy shuttle looms
    • D03D47/34—Handling the weft between bulk storage and weft-inserting means
    • D03D47/36—Measuring and cutting the weft
    • D03D47/361—Drum-type weft feeding devices
    • D03D47/362—Drum-type weft feeding devices with yarn retaining devices, e.g. stopping pins
    • D03D47/363—Construction or control of the yarn retaining devices
    • 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

Definitions

  • the invention relates to a method according to the preamble of claim 1 and a thread storage and delivery device.
  • the magnets fixed to the housing lie radially outside the component group and the magnets arranged in the component group lie under the storage area.
  • the magnetic holding forces act as far away from the shaft as possible.
  • the characteristic curve of the holding force which counteracts a rotation of the component group, initially runs with a flat rise and then rises steeply behind. In modern thread storage and delivery devices, high shaft speeds occur because of extremely high thread speeds.
  • the counterforce of the thread which is variable in the direction of rotation, the floating mounting of the component group on the shaft, accelerations and decelerations that occur during operation, and other disturbing influences, torque impulses can occur on the component group, which then result from the holding position defined by the magnets after both Direction of rotation is stimulated to oscillate movements.
  • the component group Because of the holding force characteristic curve, the component group begins a rocking torsional vibration around the target position, which is a resonance state with a large, for example several millimeters, amplitude reached.
  • the torsional vibrations place a high load on the holders of the magnets and make it difficult to precisely scan the thread supply and to maintain a thread pull tension that is as uniform as possible. If the thread storage and delivery device is equipped with an integrated weft metering device, then the torsional vibrations interfere with the weft thread metering.
  • the invention has for its object to provide a method of the type mentioned, with which disturbing torsional vibrations are avoided when holding the component group by means of magnetic holding force, and to provide a thread storage and delivery device with magnetically fixed component group, in which a largely torsional vibration-free even at high speeds Operation is possible.
  • the temporary torsional vibration damping connection between the housing and the component group prevents rocking the component group against the weak holding force of the magnets around the target position. Since the torsional vibrations take a certain time to reach a resonance state and a disturbing amplitude, the temporary torsional vibration damping connection disturbs the tendency to rock from the outset, so that no more harmful torsional vibrations arise.
  • the forces exerted on the component group during the temporary torsional vibration damping connection can be relatively small because they influence the relatively free vibration system of the component group extremely effectively and in such a way that the component group can no longer be stimulated to any noticeable oscillations.
  • the torsional vibration-damping connection is controlled precisely and reliably in time if it is pneumatic, is produced mechanically or magnetically.
  • a torsional vibration damping member which is supported in a stationary manner relative to the component group is expediently aligned with an abutment on the feed body and a movement drive is provided with which a positive and / or non-positive connection can be produced temporarily to disrupt torsional vibrations as they arise and largely destroy them.
  • the feed body is in any case prevented from rotating with the shaft and is tumbled and the thread is pushed forward on the storage surface. It is expedient to use the wobble movement for the temporary positive and / or non-positive connection.
  • the shaft then forms, so to speak, the motion drive for the temporary cooperation between the torsional vibration damping member and the feed body.
  • the feed body is of a different type, e.g. an eccentric and inclined rod cage, which not only gives the thread the feed but also creates distances between the thread turns, the wobble movement may not be sufficient, the temporary shape and / or Establish frictional connection. Then it is expedient to force the torsional vibration damping member into and out of engagement. in the the former case, the engagement is practically made at least once with each shaft revolution. In the latter case, the distances between the interventions are largely independent of the shaft speed. Due to the eliminated disturbing torsional vibrations, the loads on the holders of the magnets are spared, the thread can be scanned without errors and undesired changes in tension in the drawn thread are eliminated. (Claim 6).
  • a different type e.g. an eccentric and inclined rod cage
  • the torsional vibration damping member can be arranged movably in order to forcibly establish the engagement (claim 8).
  • the torsional vibration damping member could, however, also be easily held on a support which, like the housing, is arranged in a stationary manner and is separate from the housing (claim 9).
  • the torsional vibration damping member is a U-shaped bracket made of resilient material, which works with its crossbar with the abutment.
  • the self-suspension of the bracket avoids a disturbing influence on the operation of the feed body. Nevertheless, the engagement between these two parts is sufficient to suppress the torsional vibrations. (Claim 10)
  • a permanently constant damping effect is achieved with a frictionally active area on the torsional vibration damping element and / or on the abutment.
  • the force that is transmitted in the engagement between these two parts can be low because the frictional engagement supports the damping effect (claim 11).
  • the engaging force can be very low if a positive connection is generated between the torsional vibration damping member and the abutment, which suddenly interrupts the movement of the component group from the target position (claim 13).
  • the motion drive can have a clock control (claim 16).
  • the torsional vibration damping member can also be a compressed gas nozzle which directs a flow onto the abutment designed as a guide element. (Claim 17).
  • the torsional vibration damping member In the case of a thread storage and delivery device in which the abutment on the component group does not perform a self-movement sufficient for a temporary engagement, the torsional vibration damping member is moved approximately radially to the shaft between a passive position and an engagement position by means of a motion drive connected to a control. It is ensured that the torsional vibration damping member does not collide with the moving thread or the thread winding member. In order to suppress disruptive torsional vibrations, it is irrelevant in which area of the component group the interference force is applied. It becomes useful however, applied at the greatest possible radial distance from the shaft. The intervention time can be extremely short. In practice, it is sufficient to touch the component group only, for example over milliseconds. (Claim 18)
  • a thread storage and delivery device in which a thread stop device containing a stop element is assigned to the storage area, it is expedient to offset the torsional vibration damping member axially and / or in the circumferential direction in order to avoid mutual interference here.
  • the torsional vibration damping member expediently comes into engagement when the thread is fixed by the stop element. The same period of time can be used as the duration of the engagement, as is predetermined for the holding of the thread.
  • the intervention does not necessarily have to take place each time the stop device is actuated. The occurrence of disruptive torsional vibrations is suppressed even with larger distances between the interventions (claim 23).
  • the torsional vibration damping member can also be incorporated into the stop device with its movement drive, which saves space and leaves access to the component group free (claim 24).
  • the torsional vibration damping element can be formed by the stop element of the stop device itself.
  • the stop element is used as an obstacle in the circumferential direction of the storage area.
  • the engagement between the stop element and the storage surface is used locally, separately therefrom.
  • a thread storage and delivery device F contains in a stationary housing G a drive motor M for an obliquely protruding winding tube 2 supporting shaft 1.
  • a control device C for the drive motor M is arranged, which is in signal-receiving connection with sensor devices, not shown.
  • the winding tube 2 is integrated in an annular body R, which contains a thread winding member W.
  • a support A for a torsional vibration damping element X is provided on the housing and can be temporarily brought into engagement with an abutment Y in order to produce a torsional vibration damping connection D (FIG. 3).
  • a component group K is mounted in bearings 3, which, in addition to components that are not described in any more detail, contains a storage body 4 with axially extending arms 4b consisting of individual segments.
  • the arms 4b define a polygonal storage surface S.
  • a feed body 6 is rotatably mounted on the free end of the shaft 1 in bearings 5, which extends outwards beyond the storage surface S into the vicinity of the ring body R.
  • the axis of rotation 1 a of the feed body 6 is inclined relative to the axis of rotation 1 a of the shaft 1, such that the feed body 6 is tilted toward the thread winding member W.
  • Magnets 10 are arranged in housing G and aligned with magnets 11 in component group K. Between the magnets 10, 11 there is a gap permitting the passage of the winding tube 2, over which magnetic holding forces act which prevent the component group K and the feed element 6 from rotating with the shaft 1. When the shaft 1 rotates, the feed body 6, which is prevented from rotating, is excited to a wobble movement (wobble region 7).
  • a thread 8 fed through the hollow shaft 1 runs through the winding tube 2 and the thread winding member W, from which it is placed in the form of a thread supply 9 from individual turns onto the storage area S.
  • Dash-dotted lines indicate how the thread is withdrawn overhead from the storage area S.
  • the feed element 6 continuously pushes the thread supply 9 axially further from the thread winding member W during its wobbling movement.
  • the torsional vibration damping member is a U-shaped bracket 12 (FIG. 2) formed from spring steel wire, which is clamped in a receptacle 14 of the housing with a tensioning element 13 and a tensioning screw 15.
  • the U-legs of the bracket 12, designated 16 and 17, are cranked and extend over the orbit of the thread winding member W to the feed member 6.
  • a crossbar 18 connecting the legs 16, 17 is approximately tangential to the shaft 1. It has a frictionally active area , e.g. a coating 19 provided.
  • the bracket 12 is bent in the region of the crosspiece 18 towards the feed element 6.
  • the device F according to FIG. 1 is designed as a weft metering device which releases sections of the length that are precisely dimensioned from the thread supply 9 for triggering.
  • a stop device 21 is attached to the housing, on which a magnet coil or a magnet is attached as a movement drive 22 for a plunger-shaped stop element 23.
  • the stop element 23 can be moved into a recess 24 provided in the storage area S in order to hold the thread 8 rotating during the withdrawal. Is the stop element 23rd withdrawn, the thread runs freely.
  • Fig. 2 it can be seen that the longitudinal bars 4b of the storage body 4 engage in radial slots 20 of the feed member 6.
  • the ring-shaped edge of the feed element 6 (FIG. 4), designated 6a, serves at one point on the circumference as the abutment Y for the torsional vibration damping element X.
  • a friction-active lining is provided there or a depression which is connected to the bracket 12 is able to form fit when the edge 6a lies in the wobble region 7 of the feed body 6 on the bracket 12 in order to produce a temporary torsional vibration-damping connection.
  • the diameter of the storage area S can be changed.
  • the segments of the storage body 4 are radially adjustable.
  • the thread winding member W is rotated by approximately 180 ° relative to its position in Fig. 1.
  • the feed member 6 has moved axially to the bracket 12 until the torsional vibration-damping connection D has occurred due to an engagement between the crosspiece 18 and the surface 6a.
  • the crosspiece 18 has a length which is limited to a few angular degrees in the circumferential direction of the feed body 6 such that the engagement is maintained over approximately 1/4 of a full revolution of the shaft 1 before the feed body 6 detaches again from the crosspiece 18 and one Frees gap (Fig. 1) in which the thread 8 passes the bracket 12 without being caught.
  • nascent torsional vibrations of the component group K are suppressed, so that the Component group remains in the target position determined by the magnets 10, 11.
  • elastic fillers 26, 27 are arranged in the interior of the component group. Thanks to the elasticity of the filler bodies 26, 27, the wobble movement of the feed body 6 is not impaired.
  • 5a to 5i represent different embodiments of the torsional vibration damping member X and its associated abutment Y.
  • the torsional vibration damping member X is a pin 28 with a friction lining 29 attached to the head end, which is pressed onto a flat surface 30 of the abutment Y.
  • the torsional vibration damping member X is a plunger 31, which enters with its head end 32 into a, preferably conically widened, recess 33 of the abutment Y.
  • the torsional vibration damping jacket X is a plunger 34 with a rounded head end 35 which is pressed into an elastic covering 36 of the abutment Y.
  • the rounded head end 35 of the torsional vibration damping member X is inserted into a recess or bore 37 of the abutment Y.
  • the walls of the borehole can be rounded or flared.
  • the torsional vibration damping element X has the Shape of a mushroom 39 with a recess 40 on the underside, which is placed on a projection 38 of the abutment Y.
  • the torsional vibration damping member X is a pin 41 with an oblique head end 42.
  • the abutment Y has the shape of a sawtooth-shaped recess 43 with a one-sided stop 44. It is sufficient to suppress torsional vibrations a secure positive fit in only one Ensure direction of rotation.
  • the torsional vibration damping member X is a plunger 45, which carries a magnet 46 at its head end.
  • the abutment Y is either made of magnetic material or is equipped with a magnet 47, which produces a force fit when the magnet 46 is in contact.
  • the abutment Y can be contained in the feed body 6.
  • the torsional vibration damping member X is a compressed air nozzle 48 which is connected to a pressure source Q and is aligned with the abutment Y, which has the shape of a guide element 49.
  • the jet emerging from the nozzle 48 generates an interference force on the guide surface 49, which prevents the development of torsional vibration damping.
  • the slots 20 in the feed body 6 serve as flow passages on both sides of the guide element 49.
  • the torsional vibration damping member X is a plunger 50, which can be inserted with its head end 51 into a recess 52 of the abutment Y. At the bottom of the recess 52, an elastic friction lining 53 is attached.
  • the abutment Y can not only in Feed body 6 may be arranged, or - as indicated here - in one of the longitudinal bars 4b of the storage body 4.
  • the torsional vibration damping member X requires a movement drive which gives it the movements indicated in the direction of a double arrow.
  • FIG. 6 schematically shows a movement drive for a torsional vibration damping element X designed as a double lever 54.
  • the double lever 54 is pivotable in the support A about an axis 55 and is acted upon at one end by a movement drive 56 which contains a clock control.
  • a return spring 57 counteracts the movement drive 56.
  • the abutment Y can be arranged either on the feed body 6 or on a longitudinal rod 4b of the storage body 4.
  • the torsional vibration damping connection D is established between a support A, 58 which is fixed relative to the component group K and the storage area S.
  • the torsional vibration damping member X has the configuration shown in FIG. 5i, ie the plunger 50 is attached radially with its head end to the storage surface S in order to produce the engagement.
  • a holder 59 is held for a movement drive 60 in the support 58, which may or may not belong to the housing G.
  • the movement drive 60 is expediently connected to a control which actuates the torsional vibration damping element X only when the thread 8 is motionless during a draw pause.
  • FIG. 7 corresponds to the structure of FIGS. 1 to 3. If the device F is equipped with a stop device 21, the torsional vibration damping element X is always brought into engagement when the stop element 23 holds the thread running off. 7 and 8, the torsional vibration damping member X is offset in the circumferential direction relative to the stop device 21. It would also be conceivable to offset the torsional vibration damping member in the axial direction with respect to the stop device 21. In Fig. 7 the offset is 180 ° in the circumferential direction, in Fig. 8 only 90 °.
  • the torsional vibration damping element X is arranged separately from the stop device 21 in a separate support A, 58.
  • This principle could also be used for a thread storage and delivery device without a stop device, as long as the movement drive 60 is controlled as a function of the withdrawal movement of the thread.
  • the torsional vibration damping member X can also be structurally integrated into the stop device 21 with its movement drive 60. It is particularly expedient if the stop element 23 at the same time forms the torsional vibration damping member X by cooperating with the recess 23 in a form-fitting manner or being pressed therein onto an elastic covering 53 in order to always produce the temporary torsional vibration damping connection D, when the thread is to be stopped. In this case, no additional torsional vibration damping element X is required.

Landscapes

  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Vibration Prevention Devices (AREA)
  • Forwarding And Storing Of Filamentary Material (AREA)
  • Looms (AREA)
  • Sewing Machines And Sewing (AREA)
EP91900243A 1989-11-03 1990-10-30 Verfahren zum verhindern von drehschwingungen in einer fadenspeicher- und -liefervorrichtung und fadenspeicher- und -liefervorrichtung Expired - Lifetime EP0498852B1 (de)

Applications Claiming Priority (11)

Application Number Priority Date Filing Date Title
SE8903704 1989-11-03
SE8903704 1989-11-03
SE8903711 1989-11-06
SE8903711A SE8903711D0 (sv) 1989-11-06 1989-11-06 Garnlagringsenhet
SE8903786A SE8903786D0 (sv) 1989-11-10 1989-11-10 Verfahren zum festhalen
SE8903786 1989-11-10
SE8903807A SE8903807D0 (sv) 1989-11-13 1989-11-13 Verfarhen zur verhinderung von drehschwingungen
SE8903807 1989-11-13
DE3938646 1989-11-21
DE3938646A DE3938646A1 (de) 1989-11-03 1989-11-21 Verfahren zum verhindern von drehschwingungen in einer fadenspeicher- und -liefervorrichtung und fadenspeicher- und -liefervorrichtung
PCT/EP1990/001937 WO1991006500A1 (de) 1989-11-03 1990-10-30 Verfahren zum verhindern von drehschwingungen in einer fadenspeicher- und -liefervorrichtung und fadenspeicher- und -liefervorrichtung

Publications (2)

Publication Number Publication Date
EP0498852A1 EP0498852A1 (de) 1992-08-19
EP0498852B1 true EP0498852B1 (de) 1995-01-04

Family

ID=27511360

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91900243A Expired - Lifetime EP0498852B1 (de) 1989-11-03 1990-10-30 Verfahren zum verhindern von drehschwingungen in einer fadenspeicher- und -liefervorrichtung und fadenspeicher- und -liefervorrichtung

Country Status (5)

Country Link
US (1) US5294067A (ja)
EP (1) EP0498852B1 (ja)
JP (1) JP2880289B2 (ja)
CZ (1) CZ283635B6 (ja)
WO (1) WO1991006500A1 (ja)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4127796A1 (de) * 1991-08-22 1993-02-25 Iro Ab Faden-fournisseur
US5600530A (en) * 1992-08-04 1997-02-04 The Morgan Crucible Company Plc Electrostatic chuck

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH439161A (de) * 1965-06-25 1967-06-30 Sulzer Ag Webmaschine mit Schussfadenzwischenspeicher
DE2843548C2 (de) * 1978-10-05 1980-10-30 Ab Iro, Ulricehamn (Schweden) Fadenspeicher- und -liefervorrichtung für Textilmaschinen
US4226379A (en) * 1979-12-06 1980-10-07 Leesona Corporation Loom storage feeder improvement
CH647999A5 (de) * 1980-06-17 1985-02-28 Rueti Ag Maschf Fadenliefervorrichtung fuer textilmaschinen und verfahren zum betrieb der fadenliefervorrichtung.
JPS5782546A (en) * 1980-11-12 1982-05-24 Nissan Motor Storage apparatus of "futakoshi" weft yarn of shuttleless loom
JPS57101040A (en) * 1980-12-11 1982-06-23 Nissan Motor Weft yarn storing apparatus of shuttleless loom
JPS59125944A (ja) * 1982-12-27 1984-07-20 日産自動車株式会社 断片織機の緯糸供給装置
DE3862670D1 (de) * 1987-04-08 1991-06-13 Sulzer Ag Verfahren fuer den betrieb eines schussfadenspeichers fuer eine webmaschine.
IT1230562B (it) * 1988-10-14 1991-10-28 Roy Electrotex Spa Gruppo di avvolgimento della riserva di filo di trama a sviluppo di spira variabile regolabile con un intervento singolo, per l'uso in porgitrama-misuratori per telai di tessitura

Also Published As

Publication number Publication date
WO1991006500A1 (de) 1991-05-16
EP0498852A1 (de) 1992-08-19
US5294067A (en) 1994-03-15
CZ283635B6 (cs) 1998-05-13
JP2880289B2 (ja) 1999-04-05
CS540490A3 (en) 1992-05-13
JPH05502004A (ja) 1993-04-15
WO1991006500A8 (de) 2004-04-22

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