EP0892864A1 - Frein a disque axial et appareil d'alimentation en fil equipe d'un tel frein - Google Patents

Frein a disque axial et appareil d'alimentation en fil equipe d'un tel frein

Info

Publication number
EP0892864A1
EP0892864A1 EP97914308A EP97914308A EP0892864A1 EP 0892864 A1 EP0892864 A1 EP 0892864A1 EP 97914308 A EP97914308 A EP 97914308A EP 97914308 A EP97914308 A EP 97914308A EP 0892864 A1 EP0892864 A1 EP 0892864A1
Authority
EP
European Patent Office
Prior art keywords
thread
braking
disc brake
brake
braking surface
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP97914308A
Other languages
German (de)
English (en)
Other versions
EP0892864B1 (fr
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/fr
Application granted granted Critical
Publication of EP0892864B1 publication Critical patent/EP0892864B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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 thread delivery device with an axial disc brake.
  • the adjacent braking surfaces are arranged exactly perpendicular to the axis of the storage drum.
  • the braking surface arranged on the front side of the storage drum is exactly perpendicular to the storage drum axis, while the other braking surface is formed by the convexly rounded outer edge of a funnel-shaped braking element with a funnel angle that is almost 180 °.
  • the braking surface perpendicular to the storage drum axis is formed in one piece on the storage drum.
  • the thread rotating in the clockwise manner when the overhead drum is pulled off from the storage drum runs approximately axially from the outside between the braking surfaces, is braked by the braking surfaces and is then drawn off approximately centrally through the opening of the braking surface.
  • the fade is deflected twice by 90 °.
  • the thread is deflected at least once by 90 °. Under severe circumstances, this strong deflection can mean a high load in the thread and lead to undefined friction conditions.
  • the centering of the braking element on the axis of the storage drum is unproblematic because of the one braking surface perpendicular to the storage drum axis.
  • the invention has for its object to provide an axial disc brake of the type mentioned and a yarn delivery device, in which a very favorable thread geometry for the thread without strong deflections and a clean mutual centering of the braking surfaces with perfect contact conditions between the braking surfaces in the Contact area are guaranteed.
  • the area of contact lies in which the thread which is drawn from the outside to the central take-off opening and thereby rotates in a clockwise manner around the axis of the disc brake is braked. oblique, so that there is a very favorable thread geometry with weak deflections. The incoming thread is just entering the contact area and is only gently deflected into the draw-off opening after the contact area.
  • the cooperation of the braking surfaces results in constant contact conditions and a perfect centering of the braking surfaces against one another, because the contact area remains a full circle even when the cone axis deviates from the axis of the disc brake or the storage drum or the spherical braking surface is displaced whose diameter cannot be changed due to the geometry.
  • the risk of thread breaks is low due to a favorable thread geometry, since the thread that runs from the thread guide surface into the disc brake without deflection and rotates like clockwise is deflected after the contact area of the brake surface, and then only gently.
  • the resulting reduction in the respective rotation angle or the lack of deflection in the inlet area rich has a particularly favorable effect on the thread, specifically because of the exposed influence of the deflection angle.
  • the thread is practically braked only in the contact area, so that the constant braking effect of the braking surfaces leads to very favorable, largely constant thread tension in the thread being drawn off.
  • Relative displacements of the braking surfaces that occur do not change the contact and braking conditions between the braking surfaces, since the full circle of the contact area is always retained and the braking surfaces automatically align themselves appropriately to one another. Manufacturing or assembly tolerances are tolerated by the perfect cooperation between the tapered braking surface and the spherically convex braking surface without any noticeable influence on the braking effect.
  • the spherically convex braking surface is on the inlet side of the thread, the ball center being in the axis of the disc brake.
  • the conical braking surface is on the inlet side of the thread.
  • the spherical, convex braking surface is defined by the inside of a funnel on the withdrawal side of the thread.
  • the direction of the tangent approximately determines the feed direction of the thread, so that this follows an optimal thread geometry without any deflection on the feed side and with only a gentle deflection on the take-off side.
  • the disc brake brakes on a smaller diameter than the diameter of the thread guide surface.
  • the thread takes an optimal path without deflection into the disc brake.
  • the spherically convex braking surface is located on the front side of the storage drum. Despite Possible positional deviations of the braking surfaces from an optimally centered relative position maintain the full circle of the contact area with an unchangeable diameter.
  • the conical braking surface is located on the end face of the storage drum. In spite of possible position deviations of both braking surfaces from an optimally centered relative position, the full circle of the contact area between the braking surfaces is retained with an unchanged diameter.
  • the end face of the storage drum itself forms the one braking surface or supports the braking body having this braking surface.
  • the braking element is supported in the holder and thereby receives important mobility.
  • the brake drive acts upon the braking element with the application force which is expedient for the desired braking effect, specifically in a flexible manner, so that the braking element in the dynamic phase during thread take-off can automatically carry out its own movements required to keep the braking effect constant. Space is saved in the axial direction of the storage drum, since the braking-effective elements are optimally provided close to the storage drum.
  • the brake body is able to adapt itself automatically to the respective relative position of the brake element, both by tilting movements and by radial offset movements.
  • the brake body of the embodiment according to claim 11 is technically simple to manufacture and ensures a long service life with a constant braking effect.
  • the optionally provided edge flange and the central recess increase the dimensional stability of the brake body and allow it to be easily attached.
  • the edge flange receding backwards is a factor that prevents the thread from penetrating behind the brake body in a structurally simple manner.
  • the braking element in the embodiment according to claim 12 is also technically simple and ensures a long service life with a constant braking effect.
  • the optionally provided outer edge flange increases the dimensional stability of the braking element and prevents the thread from accidentally running in behind the braking element.
  • the thread funnel enables a gentle pulling-off movement of the thread and can profitably serve to arrange a thread eyelet that guarantees optimal friction and deflection conditions.
  • a particularly favorable thread geometry is achieved with the cone angle range of claim 13, an optimal value of the cone angle being approximately 120 ° in order to achieve a symmetrical thread geometry.
  • the diameter range of claim 14 is expedient.
  • the components of the disc brake can be made very light, in particular the braking element.
  • the thread rotating in the manner of a clockwise along the thread guide surface expediently runs free over a relatively long distance between the thread guide surface and the contact area, so that the thread's own movements within this distance do not propagate appreciably into the contact area and impair the braking effect.
  • the pointer rotation movement is very concise and the thread is drawn clean radially into the contact area regardless of the speed and - viewed in the direction of the axis of the disc brake.
  • the pressing force between the braking surfaces is exerted in a precisely selectable manner with the spring element. If necessary, the braking element can yield (even when a knot passes through). It is particularly favorable that the spring element acts approximately on the diameter of the contact area, so that there is a linear transmission of force from the spring element into the contact area.
  • the membrane attached to the edge flange prevents the thread from penetrating behind the braking element. Furthermore, by means of the membrane and a suction of the suction chamber, the brake element is lifted off the brake body in order to allow the threading in (conveniently, manually or by means of a pneumatic threading device).
  • the membrane has no harmful effect on the normal braking action. However, it can help center the braking element.
  • the embodiment according to claim 17 is directed to a controllable axial disc brake on a thread delivery device, as is expedient for projectile or rapier weaving machines, in order to vary the braking effect depending on the weaving cycle during each insertion process.
  • the retraction drive releases or releases the axial disc brake in operating phases in which no or only minimal braking is required, e.g. at the beginning of the entry, after the handover phase or at the end of the entry.
  • a basic braking effect is set by means of the spring element and is reduced or modulated by the trigger drive.
  • the embodiment according to claim 18 is characterized by an immediate and sensitive response with a long service life.
  • the axial disc brake Since the pointer movement of the thread running into the disc brake is a basic prerequisite for an optimal effect of the disc brake, it is very expedient to combine the axial disc brake with a second brake device which, for example, in the area of the thread guide surface of the storage drum works and stabilizes the thread with very low tension in the inlet area to the axial disc brake.
  • This second brake device can be a bristle brake ring or the like, which cooperates in contacting manner with the storage drum.
  • the geometric shape of the spherical or conical braking surface need not necessarily be derived exactly from a ball of a cone. Since the relative displacements of the braking surfaces have 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 in the braking surfaces.
  • FIG. 1 shows a longitudinal section of a first embodiment of an axial disc brake
  • Fig. 2 is a longitudinal section of an alternative embodiment
  • FIG 3 shows a longitudinal section of a front section of a yarn delivery device with an axial disc brake.
  • the main components of an axial disc brake B according to FIG. 1 consist of a brake body K, against which a brake element E is pressed coaxially, in such a way that the brake body K and the brake element E provide axis 3 of the disc brake B rotationally symmetrical braking surfaces 1, 2 lie against one another in a circular contact area C with preselectable preload.
  • the axial disc brake B serves to brake a thread (not shown) which is pulled through between the braking surfaces 1, 2.
  • the indication "axial disc brake” is intended to express that the solid thread runs parallel to the direction of axis 3 of the disc brake and thereby undergoes an S-shaped displacement in axis 3.
  • the showed thread in FIG. 1 in the inlet gap i formed between the brake body K and the brake element E then passes through the contact area C and is pulled off axially through a central withdrawal opening e of the brake element E.
  • the braking surface 1 is spherically convex with the ball center 4 in the axis 3 of the disc brake B.
  • the other braking surface 2 of the braking element E interacting therewith is conical and affects the spherically convex braking surface 1 in the common contact area C.
  • the straight-line generating end of the conical braking surface 2 thus forms a tangent T to the spherically convex braking surface 1, the cone angle ⁇ being able to be between 90 ° and 160 °, but expediently being approximately 120 °.
  • the tapered axis of the tapered braking surface 2, designated 5, corresponds at least approximately to the axis 3 of the axial disc brake.
  • a circular thread guide surface 6 is provided concentrically to the axis 3, on which the thread running straight into the inlet gap i is guided in such a way that during its withdrawal movement it executes a clockwise rotation around the axis 3 and thereby - in the direction of the axis 3 seen - 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 approx. 17% of the diameter of the thread guide surface 6.
  • An approximately axial circumferential edge flange 7 can be provided on the brake body K, as well as a recess 8 in the center.
  • a fastening element 9 with a cladding 10 engages in the recess 8, around the brake body K on a carrier 10 on all sides to be stored at least to a limited extent.
  • a radial bearing play 11 can be expedient so that the brake body K can also perform radial displacement movements in a limited area. It is conceivable to brake the body K by a weak centering spring in FIG left to act.
  • the tilting center of the brake body K designated by 12 in its bearing is expediently approximately in the radial plane of the contact area C.
  • the braking element E has a generally funnel-like shape.
  • a radial edge flange 13 adjoins the conical braking surface 2 on the outside.
  • the braking surface 2 has the trigger opening e, which in the embodiment shown is delimited by a funnel section 14 in which a thread eyelet 15 is arranged.
  • a cylindrical tube section 16 adjoins the funnel section 14 as a guide section, which is displaceable in an axial guide 17 and 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 helical spring.
  • the effective diameter of the spring element 18 essentially corresponds to the diameter of the full circle in the contact area C.
  • the relative positions of the braking surfaces 1 and 2 are interchanged.
  • the conical braking surface 2 is arranged on the brake body K, while the spherically convex braking surface 2 is provided on the braking element E.
  • the braking element E is formed in the rotationally symmetrical and spherical-convex braking surface 1 defining the section in the manner of a funnel which has an inner generatrix in the form of a circular arc section.
  • the cone angle ⁇ and thus the optimal thread feed angle is defined by the generatrix of the conical braking surface 2.
  • the conical braking surface 2 affects the spherically convex braking surface 1 in the contact area C, which is designed as a full circle, and its circular shape and diameter do not change with relative displacement movements between the braking element E and the braking body K.
  • the braking surface mounted on the carrier 10 could also be formed in one piece directly on the carrier either with a conical shape or with a spherical convex shape.
  • the brake element E as well as the brake body K are expediently metal or plastic molded parts in a dimensionally stable design. It is expedient to form the brake body K and the brake element E from light metal and to provide at least the brake surfaces 1, 2 with a wear-resistant coating.
  • the axial disc brake B (for example corresponding to FIG. 1) is structurally incorporated as a weft pull-off brake in a thread delivery device F, of which only the front end region of a storage drum D is shown with a bracket 20 fixed to the housing.
  • the thread delivery device F furthermore (not shown) has a drive motor for a take-up element housing, a drive shaft for the take-up element and a bearing for the storage drum D on which a weft thread Y for a textile machine, not shown, in particular a projectile or Rapier weaving machine, for which the weaving machine stores it for consumption.
  • the textile machine pulls the thread Y over the 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).
  • the thread Y is indicated by dash-dotted lines in its path.
  • a conical nose part of the storage drum D forms the carrier 10 for the brake body K.
  • At the front end of the storage drum D there is a curved or conical draw-off area 19 which defines the thread guide surface 6 mentioned in FIGS. 1 and 2.
  • the thread Y After passing through the contact area, the thread Y is again deflected from its running direction by the angle ⁇ / 2 in the axial draw-off direction.
  • the cone angle ⁇ of the conical braking surface is expediently matched to the outer diameter of the thread guiding surface 6 and the axial distance between the thread guiding surface 6 and the deflection area in the axial disc brake such that the deflections of the thread on the thread guiding surface 6 and in the axial disc brake approximately are the same size.
  • the longitudinal guide 17 of the braking element E is part of a bracket 21 connected to the arm 20, in which a brake drive A is provided.
  • the spring drive 18 serves as the brake drive A, which presses the brake element E against the brake body K with a predetermined axial loading force, which can be set, for example, by means of an adjusting screw 25.
  • the adjustment takes place in that an abutment 24 for the spring element 18 is adjusted in the axial direction in the holder 21 by turning the adjusting screw 25.
  • a controllable retraction drive 30 is also provided in the holder 21, which acts on the braking element E in the opposite direction to the direction in which the spring element 18 acts in order to reduce or modulate the braking effect.
  • the retraction drive 30 can be operated depending on the web cycle, specifically electrically, electromagnetically or pneumatically.
  • the outer edge flange 13 of the braking element E is fixed in an annular membrane 26, the outer edge of which is attached to the holder 21 and which forms a boundary of a suction chamber 27 in the holder 21.
  • the braking element E in FIG. 3 can be moved to the right and completely lifted off the braking body K, for example for threading in a new thread Y.
  • an ejector suction and biasing nozzle 28 are provided, with which compressed air is applied to between the Braking surfaces acting suction and at the same time a blow-out flow directed to the right can be generated in order to suck in a thread brought into the area of the (then lifted off) brake surfaces and blow it out to the right.
  • the induced draft can be used directly to actuate the membrane 26 by transferring it into the suction chamber 27 when the ejector nozzle 28 is activated.
  • the diaphragm 26 or the retraction drive 30 generate a force or movement in the direction of an arrow 29 on the braking element E.
  • a second thread brake device 22 is expediently provided upstream of the axial disc brake, which is supported in a holder 23 of the arm 20 and interacts with the draw-off area 19.
  • this second thread brake 22 has a rubber membrane with a truncated cone brake band.
  • a conventional bristle ring a so-called multi-disk brake or a finite band placed flat on the circumference of the storage drum, which is elastically tensioned by a tensioning device.
  • the second thread brake 22 generates only a low basic tension in the thread in order to ensure that the thread Y does not loosen and runs smoothly between the turns on the storage drum D and the inlet gap of the axial disc brake, and that the balloon formation is limited or suppressed becomes.

Landscapes

  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Looms (AREA)

Abstract

Frein à disque axial (B), en particulier pour appareil d'alimentation en fil (F), présentant des surfaces de freinage (1, 2) indéformables, symétriques en rotation par rapport à un axe (3), pressées axialement élastiquement l'une contre l'autre sous une pression d'appui prédéterminée, dont une surface de freinage présente une ouverture centrale d'extraction et est montée sur au moins un élément de freinage prenant appui mobile en direction axiale. Une surface de freinage (1) est sphériquement convexe, cependant que l'autre (2) est de forme conique, avec l'axe du cône (5) situé au moins approximativement dans l'axe (3) du frein à disque (B), la génératrice du cône formant, dans la zone de contact (C) des surfaces de freinage (1, 2), une tangente (T) du cercle générateur de la surface sphériquement convexe (1). Le frein à disque axial (B) est de préférence disposé sur la partie frontale d'un tambour d'enroulement (D) d'un appareil d'alimentation en fil (F) pour un métier à tisser à projectile ou un métier à tisser à navette à pince, de telle façon que le fil entraîné en rotation par le tambour d'enroulement (D), lors d'un travail à la défilée, dans le sens d'une aiguille d'une montre, le long de la surface du guide-fil (6), entre directement, sans changer de direction, dans la zone de contact de la surface de freinage et, après son passage dans cette zone, soit dévié en douceur pour reprendre de nouveau la direction axiale.
EP97914308A 1996-04-01 1997-03-25 Frein a disque axial et appareil d'alimentation en fil equipe d'un tel frein Expired - Lifetime EP0892864B1 (fr)

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 (fr) 1996-04-01 1997-03-25 Frein a disque axial et appareil d'alimentation en fil equipe d'un tel frein

Publications (2)

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

Family

ID=7790193

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97914308A Expired - Lifetime EP0892864B1 (fr) 1996-04-01 1997-03-25 Frein a disque axial et appareil d'alimentation en fil equipe d'un tel frein

Country Status (6)

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

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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 (fr) * 2007-10-10 2009-05-13 Iro Ab Machine à tisser, passe-fil et procédé d'insertion d'un passe-fil
ITTO20111217A1 (it) * 2011-12-28 2013-06-29 Lgl Electronics Spa Dispositivo frena-trama per alimentatori di filato a tamburo fisso
ITTO20111218A1 (it) * 2011-12-28 2013-06-29 Lgl Electronics Spa Alimentatore di filato a tamburo fisso con dispositivo frena-trama controllato
DE102021115596B3 (de) * 2021-06-16 2022-05-12 Memminger-IRO Gesellschaft mit beschränkter Haftung Fadenliefergerät

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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
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Also Published As

Publication number Publication date
KR100293647B1 (ko) 2001-08-07
WO1997037069A1 (fr) 1997-10-09
DE59702079D1 (de) 2000-08-31
CN1063242C (zh) 2001-03-14
KR20000004939A (ko) 2000-01-25
EP0892864B1 (fr) 2000-07-26
US6257516B1 (en) 2001-07-10
CN1215442A (zh) 1999-04-28
DE19613055A1 (de) 1997-10-02

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