EP0892864B1 - Axiale scheibenbremse und fadenliefergerät mit axialer scheibenbremse - Google Patents

Axiale scheibenbremse und fadenliefergerät mit axialer scheibenbremse Download PDF

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Publication number
EP0892864B1
EP0892864B1 EP97914308A EP97914308A EP0892864B1 EP 0892864 B1 EP0892864 B1 EP 0892864B1 EP 97914308 A EP97914308 A EP 97914308A EP 97914308 A EP97914308 A EP 97914308A EP 0892864 B1 EP0892864 B1 EP 0892864B1
Authority
EP
European Patent Office
Prior art keywords
braking
disc brake
storage drum
yarn
feeding device
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
EP97914308A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0892864A1 (de
Inventor
Joachim Fritzson
Kurt Arne Gunnar Jacobsson
Lars Helge Gottfrid Tholander
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
Application filed by Iro AB filed Critical Iro AB
Publication of EP0892864A1 publication Critical patent/EP0892864A1/de
Application granted granted Critical
Publication of EP0892864B1 publication Critical patent/EP0892864B1/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
    • 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
    • D03D47/364—Yarn braking means acting on the drum
    • 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
    • D03D47/364—Yarn braking means acting on the drum
    • D03D47/366—Conical

Definitions

  • the invention relates to an axial disc brake and a yarn delivery device an axial disc brake.
  • axial disc brake known from WO91 / 14032 for the Storage drum of a thread delivery device rotatingly pulled weft for a textile machine in one embodiment are the adjacent Braking surfaces arranged exactly perpendicular to the axis of the storage drum.
  • braking surface exactly perpendicular to the storage drum axis, while the other braking surface from the convex rounded outer edge of a funnel-shaped Brake elements formed with a funnel angle almost 180 ° becomes.
  • the braking surface perpendicular to the storage drum axis is at another Embodiment integrally formed on the storage drum.
  • the one at Overhead deduction from the storage drum rotating clockwise Thread runs approximately axially from the outside between the braking surfaces, is by the braking surfaces braked and then approximately centrally through the opening of one Braking surface deducted.
  • the Thread deflected twice by 90 °.
  • the Thread deflected at least once by 90 °. This strong redirection can under unfavorable circumstances mean a high load in the thread and become undefined Cause friction.
  • the centering of the braking element the axis of the storage drum is due to the one, to the storage drum axis vertical braking surface unproblematic.
  • a thread brake of a thread delivery device known from EP-A-652 312 there is a continuous braking surface in the circumferential direction with the shape of a truncated cone directly on the rounded trigger edge of the storage drum of the Thread delivery device.
  • the truncated cone axis of the braking surface coincides approximately the axis of the storage drum.
  • the from the rounded deduction margin of the Storage drum has defined braking surface in the axial section of the storage drum seen a curve with the shape of a circular arc section, the center of the circle inside the storage drum, but radially spaced apart from the storage drum axis.
  • the frustoconical braking surface becomes formed by a deformable band.
  • the storage drum axis is the contact area of a full circle. Squeezes a thread through the contact area and / or there is a slight dislocation or tilting the truncated cone axis relative to the storage drum axis, then the shape of the contact area changes compared to a full circle from.
  • the invention has for its object an axial disc brake of the beginning mentioned type as well as a thread delivery device, in which one for the thread very favorable thread geometry without strong deflections and a mutual centering of the braking surfaces with perfect contact conditions guaranteed in the contact area between the braking surfaces are.
  • the spherical braking surface tangent braking surface is the contact area, in which the one pulled from the outside to the central exhaust opening, and thereby Thread rotating in a clockwise manner around the axis of the disc brake is braked obliquely, so that a very favorable thread geometry with weak deflections results.
  • the incoming thread just enters the area of contact and is only in the trigger opening after the touch area gently redirected.
  • the cooperation of the braking surfaces results constant contact conditions and perfect centering of the braking surfaces against each other, because the contact area also in the event of deviations the cone axis from the axis of the disc brake or storage drum or displacements of the spherical braking surface remains a full circle Diameter cannot be changed for geometric reasons.
  • the danger of thread breaks is low due to a favorable thread geometry, because of the thread guide surface deflecting into the disc brake without deflection and thereby according to Art a clockwise rotating thread after the contact area of the braking surfaces and then only gently, is redirected.
  • the resulting Reduction of the respective rotation angle or the lack of deflection in the Inlet area has a particularly favorable effect on the thread, because of the exponential influence of the deflection angle.
  • the thread becomes practically only braked in the contact area, so that the constant braking effect of the Braking surfaces to very cheap, largely constant thread tension in the withdrawn Thread leads.
  • Relative displacements of the braking surfaces that occur change the contact and braking conditions between the braking surfaces not because the full circle of the contact area is always preserved and the braking surfaces automatically align with each other.
  • Manufacturing or assembly tolerances are achieved through perfect cooperation between the conical braking surface and the spherically convex braking surface without tolerable influence on the braking effect tolerated.
  • the ball is spherical convex braking surface on the inlet side of the thread, the ball center in the axis of the disc brake or sepia drum.
  • the disc brake brakes on one smaller diameter than the diameter of the thread guide surface.
  • the string takes an optimal path without deflection into the disc brake.
  • the end face of the storage drum forms even the spherical braking surface, or supports the spherical braking surface having brake body.
  • the brake element is supported in the holder and receives an important mobility.
  • the brake drive is applied the braking element with the appropriate for the desired braking effect Acting force, resilient, so that the braking element in the dynamic phase during thread take-off automatically for keeping the Braking effect is able to perform the necessary own movements.
  • axial Space is saved in the direction of the storage drum because the braking elements are optimally provided close to the storage drum.
  • the brake body is capable automatically adapt to the respective relative position of the braking element, and both by tilting movements and by radial displacement movements.
  • the brake body of the embodiment according to claim 7 is manufacturing technology simple and ensures a long service life with constant Braking effect.
  • the edge flange, if applicable, and the middle one Recess increase the dimensional stability of the brake body and allow it to be simple Attachment.
  • the edge flange receding backwards is a safety factor, through the penetration of the thread behind the brake body structurally simple way is avoided.
  • the braking element in the embodiment according to claim 8 is also manufacturing technology simple and ensures a long service life with constant Braking effect.
  • the possibly provided outer edge flange increases the dimensional stability of the braking element and prevents accidental running-in of the thread behind the braking element.
  • the thread funnel enables one gentle pulling movement of the thread and can be profitable to arrange an optimal friction and deflection conditions guarantee thread eyelet.
  • a particularly favorable thread geometry is the cone angle range of Claim 9 reached, with an optimal value of the cone angle at about 120 ° lies in order to achieve a symmetrical thread geometry.
  • the diameter range of claim 10 is appropriate.
  • the components of the Make the disc brake very lightweight, especially the brake element. It expediently runs in a clockwise manner along the thread guide surface rotating thread between the thread guide surface and the contact area over a relatively long distance, so that the thread's own movements Do not propagate appreciably within this distance up to the contact area and affect the braking effect.
  • the long free thread path between the thread guide surface and the contact area the circular movement of the hands turns out very concise and the thread is independent of the speed and - seen in the direction of the axis of the disc brake - is pulled clean radially into the contact area.
  • the braking element can yield if necessary (even when a knot passes). It is particularly advantageous that the spring element approximately on the Diameter of the contact area acts, so that there is a straight line Power transmission from the spring element in the contact area results.
  • the embodiment according to claim 13 is a controllable axial disc brake directed to a thread delivery device, such as for projectile or rapier weaving machines is appropriate to the braking effect depending on the web cycle to vary each entry process.
  • the retraction drive ventilates or relieves pressure the axial disc brake in operating phases in which no or only a minimal one Braking is required, e.g. at the beginning of the entry, after the handover phase or at the end of the entry.
  • the spring element there is a basic braking effect set, which is reduced or modulated by the trigger drive.
  • the embodiment according to claim 14 is characterized by an immediate and sensitive response behavior with a long service life.
  • a second brake device for the axial disc brake to combine, e.g. in the area of the thread guide surface of the storage drum acts and the thread with very low tension in the inlet area axial disc brake stabilized.
  • This second braking device can be a Bristle brake ring or the like. That works in contact with the storage drum.
  • the geometric shape of the spherical or conical braking surface does not necessarily need to be derived exactly from a sphere to a cone his. Because the relative displacements of the braking surfaces to a relatively small extent an optimally working axial disc brake can also be realized if there are slight deviations from an exact geometric spherical or conical shape.
  • An axial disc brake B according to FIG. 1 consists of its essential components from a brake body K, against which a brake element E is pressed coaxially is such that provided on the brake body K and on the braking element E, to the axis 3 of the disc brake B rotationally symmetrical braking surfaces 1, 2 in a circular contact area C with preselectable preload lie together.
  • the axial disc brake B is used to brake a between the braking surfaces 1, 2 solid thread (not shown).
  • the information "Axial disc brake” is intended to express that the solid Thread runs parallel to the direction of axis 3 of the disc brake and one S-shaped displacement in axis 3 experiences. As a rule, the one not shown runs Thread in Fig. 1 in the between the brake body K and the braking element E formed inlet gap i, then passes through the contact area C and becomes withdrawn axially through a central discharge opening e of the braking element E.
  • the braking surface 1 is spherical convex with the ball center 4 in the Axis 3 of disc brake B.
  • the other braking surface interacting with it 2 of the braking element E is conical and affects the spherical convex Braking surface 1 in the common contact area C.
  • the linear generatrix the conical braking surface 2 forms a tangent T to the spherical convex braking surface 1, the cone angle ⁇ being between 90 ° and 160 ° can, but is conveniently at about 120 °.
  • the one labeled 5 Cone axis of the conical braking surface 2 is at least approximately the same Axis 3 of the axial disc brake coincides.
  • a circular thread guide surface 6 is provided concentrically with the axis 3 of the thread running straight into the inlet gap i is guided such that during its pull-off movement it follows a movement rotating about axis 3 Executes the type of a clock hand and - seen in the direction of axis 3 - in runs approximately radially to axis 3.
  • the diameter of the thread guide surface 6 is larger than the diameter of the full circle in the contact area C.
  • the diameter of the full circle in the contact area C is e.g. between 10 and 50%, preferably 15 to 25% or approximately 17% of the diameter of the thread guide surface 6.
  • An approximately axial peripheral flange 7 can be provided on the brake body K be, as well as a recess in the middle 8.
  • a fastening element engages in the recess 8 9 with a panel 10 to the brake body K on a carrier 10 to be tilted at least to a limited extent on all sides.
  • a radial bearing play 11 be appropriate so that the brake body K radial Can perform displacement movements in a limited area. It is conceivable, the brake body K by a weak centering spring in Fig. 1 of left to act.
  • the tilting center of the brake body K, designated 12 its storage is expediently approximately in the radial plane of the contact area C.
  • the braking element E has a generally funnel-like shape.
  • the conical one Braking surface 2 is followed by a radial edge flange 13 on the outside.
  • the middle shows Brake surface 2, the trigger opening e, in the embodiment shown is delimited by a funnel section 14 in which a thread eyelet 15 is arranged is.
  • a cylindrical tube section adjoins the funnel section 14 16 as a guide section which is displaceable in an axial guide 17 and is performed with little play.
  • the pressing force of the braking surfaces 1, 2 in the contact area B is generated by a spring element 18, e.g. a coil spring.
  • the effective diameter of the spring element 18 essentially corresponds the diameter of the full circle in the contact area C.
  • the braking surface mounted on the carrier 10 could also be made in one piece directly on the Be trained carrier.
  • the braking element E as well as the brake body K are expediently metal or plastic molded parts in a dimensionally stable design. It is useful to the brake body K and the braking element E made of light metal form and at least the braking surfaces 1, 2 with a wear-resistant coating to provide.
  • the axial disc brake B (e.g. corresponding to FIG. 1) is as Weft pulling brake structurally integrated into a thread delivery device F, from only the front end area of a storage drum D with a housing-fixed Boom 20 is shown.
  • the thread delivery device F still has (not shown) via a drive motor for a take-up element Housing, a drive shaft for the winding element and a bearing for the Storage drum D on which a weft Y for a textile machine, not shown, especially a projectile or rapier weaving machine, for consumption is cached by the weaving machine.
  • the textile machine pulls it Y thread overhead of storage drum D and further in the axial direction (the axis 3 of the axial disc brake B coincides with the axis of the storage drum D. match).
  • the thread Y is indicated by dash-dotted lines in its path.
  • a conical one Nose part of the storage drum D forms the carrier 10 for the brake body K.
  • a curved or conical Draw-off area 19 is provided, which is the thread guide surface mentioned in FIGS. 1 and 2 6 defined.
  • the thread Y is from the axial direction by an angle ⁇ / 2, half the cone angle of the conical braking surface, deflected inwards before it runs straight into the axial disc brake B. After passing through the contact area, the thread Y becomes his Direction of rotation again deflected by the angle ⁇ / 2 in the axial withdrawal direction.
  • the cone angle ⁇ of the conical braking surface is expediently on the Outside diameter of the thread guide surface 6 and the axial distance between the Thread guide surface 6 and the deflection area in the axial disc brake matched, that the deflections of the thread on the thread guide surface 6 and in the axial disc brake are approximately the same size.
  • the longitudinal guide 17 of the braking element E is part of a with the boom 20th connected bracket 21, in which a brake drive A is provided.
  • a brake drive A serves as the brake drive A
  • the spring element 18, the the braking element E against the brake body K with a predetermined axial loading force presses, for example by means of an adjusting screw 25 is adjustable.
  • the setting is made by turning the adjusting screw 25 an abutment 24 for the spring element 18 in the axial direction in the Bracket 21 is adjusted.
  • a controllable retraction drive 30 is also provided in the holder 21, which is opposite to the direction of loading of the spring element 18 acts on the braking element E to reduce or modulate the braking effect.
  • the retraction drive 30 can be operated depending on the web cycle, namely electrical, electromagnetic or pneumatic.
  • the outer edge flange 13 of the braking element E is in one annular membrane 26 is set, the outer edge of which on the bracket 21st is fixed and a boundary of a suction chamber 27 in the holder 21st forms.
  • the brake element E in Fig. 3 By connecting the suction chamber 27 to a vacuum source the brake element E in Fig. 3 to the right and completely from the brake body Take off K, e.g. for threading a new thread Y.
  • an ejector suction and blowing nozzle in the embodiment shown 28 provided, with one by compressed air to between Braking surfaces acting suction and at the same time one to the right Blow-out flow can be generated in the range of (then from each other lifted) braking surfaces brought in thread and to the right blow out.
  • the suction can be used directly to actuate the membrane 26 are transferred into the suction chamber 27 when the ejector nozzle 28 is activated becomes.
  • the membrane 26 and the retraction drive 30 generate for Brake element E a force or movement directed in the direction of an arrow 29.
  • the rotating pointer movement of the thread along the thread guide surface 6 and down to the axial disc brake B is for proper functioning of the axial disc brake useful. Since the consumption of the thread Y, e.g. by a Loom, intermittent, and the thread speed when consumed varies, is suitably upstream of the axial disc brake second thread braking device 22 is provided, which is in a holder 23 of the Boom 20 supports and cooperates with the trigger area 19.
  • This second thread brake 22 has a rubber membrane in the embodiment shown with a truncated cone brake band. But it would be too possible, here a usual bristle ring, a so-called multi-disc brake or to provide a finite belt laid flat on the circumference of the storage drum, which is stretched elastically by a tensioning device.
  • the second thread brake 22 creates only a low basic tension in the thread to ensure that the thread Y between the turns on the storage drum D and the inlet gap of the axial disc brake does not loosen and works properly runs, and that balloon formation is limited or suppresse

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  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Looms (AREA)
EP97914308A 1996-04-01 1997-03-25 Axiale scheibenbremse und fadenliefergerät mit axialer scheibenbremse Expired - Lifetime EP0892864B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19613055 1996-04-01
DE19613055A DE19613055A1 (de) 1996-04-01 1996-04-01 Axiale Scheibenbremse und Fadenliefergerät mit axialer Scheibenbremse
PCT/EP1997/001523 WO1997037069A1 (de) 1996-04-01 1997-03-25 Axiale scheibenbremse und fadenliefergerät mit axialer scheibenbremse

Publications (2)

Publication Number Publication Date
EP0892864A1 EP0892864A1 (de) 1999-01-27
EP0892864B1 true EP0892864B1 (de) 2000-07-26

Family

ID=7790193

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97914308A Expired - Lifetime EP0892864B1 (de) 1996-04-01 1997-03-25 Axiale scheibenbremse und fadenliefergerät mit axialer scheibenbremse

Country Status (6)

Country Link
US (1) US6257516B1 (ko)
EP (1) EP0892864B1 (ko)
KR (1) KR100293647B1 (ko)
CN (1) CN1063242C (ko)
DE (2) DE19613055A1 (ko)
WO (1) WO1997037069A1 (ko)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19839272B4 (de) * 1997-09-11 2007-02-01 Iro Sweden Ab Steuerbare Fadenbremse
DE19911943A1 (de) * 1999-03-17 2000-09-21 Iro Patent Ag Baar Fadenliefergerät und Fadenbremskörper
DE102005026234A1 (de) * 2005-06-07 2006-12-14 Iro Ab Fadenliefergerät für Greifer- und Projektilwebmaschinen
EP2058423A1 (en) * 2007-10-10 2009-05-13 Iro Ab Weaving machine, yarn feeder and method for inserting a weft yarn
ITTO20111218A1 (it) * 2011-12-28 2013-06-29 Lgl Electronics Spa Alimentatore di filato a tamburo fisso con dispositivo frena-trama controllato
ITTO20111217A1 (it) * 2011-12-28 2013-06-29 Lgl Electronics Spa Dispositivo frena-trama per alimentatori di filato a tamburo fisso

Family Cites Families (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB243141A (en) 1924-10-29 1925-11-26 George Herbert Thompson Improvements in tension device for yarn winding machines
CH472518A (de) * 1966-12-13 1969-05-15 Sulzer Ag Webmaschine mit Schussfaden-Zwischenspeicher
DE2200058A1 (de) * 1972-01-03 1973-09-20 Rosen Karl I J Magnetische fadenbremse
CH550730A (de) * 1972-04-28 1974-06-28 Sulzer Ag Verfahren fuer den gebremsten abzug fadenfoermigen materials von einem wickelkoerper einer speichereinrichtung fuer textilmaschinen und einrichtung zur durchfuehrung des verfahrens.
IT1108819B (it) * 1978-04-11 1985-12-09 Roy Electrotex Spa Dispositivo alimentatore di filato a tensione costante e regolabile,particolarmente per l'uso nelle macchine tessili e per maglieria
IT1049362B (it) * 1975-03-10 1981-01-20 Vella Spa R Dispositivo alimentatore di filato a tensione costante regolabile particolarmente per l uso nelle macchine tessili e per maglieria
DE2511162A1 (de) * 1975-03-14 1976-09-23 Horst Paepke Ausgleichs- und spannvorrichtung fuer faeden und garne an textilmaschinen
ES451189A1 (es) * 1975-09-12 1977-08-16 Iro Ab Dispositivo almacenador y alimentador de hilo preferentemen-te para maquinas textiles.
IT1087411B (it) * 1977-09-29 1985-06-04 Savio & C Spa Dispositivo per il controllo della tensione di filo svolgentesi da un corpo di supporto di filo
DE2932782C2 (de) * 1979-08-13 1985-08-22 Aktiebolaget Iro, Ulricehamn Fadenspeicher- und -liefervorrichtung für Textilmaschinen
DE3640515A1 (de) * 1985-12-04 1987-06-11 Barmag Barmer Maschf Fadenabsauggeraet
CH669621A5 (ko) 1986-04-29 1989-03-31 Sulzer Ag
WO1989002944A1 (en) * 1987-09-25 1989-04-06 Aktiebolaget Iro Yarn storing and delivering device
IT1236993B (it) * 1989-12-29 1993-05-12 Roy Electrotex Spa Alimentatore di trama per telai di tessitura a pinze e a proiettili
DE69132780T2 (de) * 1990-03-12 2002-04-18 Iro Ab, Ulricehamn Garnliefervorrichtung
IT1251209B (it) * 1991-09-20 1995-05-04 Lgl Electronics Spa Dispositivo di frenatura autoregolante del filato per apparecchi alimentatori di trama.
EP0534263B1 (en) * 1991-09-20 1997-12-17 L.G.L. ELECTRONICS S.p.A. Self-adjusting thread braking device for weft feeder units
IT1256329B (it) * 1992-11-23 1995-11-30 Dispositivo di alimentazione di filo
IT1261331B (it) * 1993-11-05 1996-05-14 Lgl Electronics Spa Perfezionamento ai dispositivi di frenatura modulata positiva del filato per apparecchi alimentatori di trama.
US5546994A (en) * 1994-10-14 1996-08-20 Sobrevin Societe De Brevets Industriels-Etablissement Thread storage drum with frustoconical brake strip
IT1282898B1 (it) * 1995-09-20 1998-04-01 Mario Gallo Dispositivo per controllare la tensione di un filo.
DE19542045A1 (de) * 1995-11-10 1997-05-15 Iro Ab Fadenliefergerät
DE19649220A1 (de) * 1996-11-27 1998-05-28 Iro Ab Fadenliefergerät mit einer Fadenbremse

Also Published As

Publication number Publication date
DE19613055A1 (de) 1997-10-02
DE59702079D1 (de) 2000-08-31
KR100293647B1 (ko) 2001-08-07
KR20000004939A (ko) 2000-01-25
CN1215442A (zh) 1999-04-28
CN1063242C (zh) 2001-03-14
WO1997037069A1 (de) 1997-10-09
EP0892864A1 (de) 1999-01-27
US6257516B1 (en) 2001-07-10

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