EP0402782B1 - Disque de friction - Google Patents

Disque de friction Download PDF

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Publication number
EP0402782B1
EP0402782B1 EP90110857A EP90110857A EP0402782B1 EP 0402782 B1 EP0402782 B1 EP 0402782B1 EP 90110857 A EP90110857 A EP 90110857A EP 90110857 A EP90110857 A EP 90110857A EP 0402782 B1 EP0402782 B1 EP 0402782B1
Authority
EP
European Patent Office
Prior art keywords
zone
friction
curvature
thread
friction coefficient
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
EP90110857A
Other languages
German (de)
English (en)
Other versions
EP0402782A2 (fr
EP0402782A3 (fr
Inventor
Hellmut Lorenz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Oerlikon Barmag AG
Original Assignee
Barmag AG
Barmag Barmer Maschinenfabrik 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 Barmag AG, Barmag Barmer Maschinenfabrik AG filed Critical Barmag AG
Publication of EP0402782A2 publication Critical patent/EP0402782A2/fr
Publication of EP0402782A3 publication Critical patent/EP0402782A3/fr
Application granted granted Critical
Publication of EP0402782B1 publication Critical patent/EP0402782B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • D—TEXTILES; PAPER
    • D02—YARNS; MECHANICAL FINISHING OF YARNS OR ROPES; WARPING OR BEAMING
    • D02G—CRIMPING OR CURLING FIBRES, FILAMENTS, THREADS, OR YARNS; YARNS OR THREADS
    • D02G1/00—Producing crimped or curled fibres, filaments, yarns, or threads, giving them latent characteristics
    • D02G1/02—Producing crimped or curled fibres, filaments, yarns, or threads, giving them latent characteristics by twisting, fixing the twist and backtwisting, i.e. by imparting false twist
    • D02G1/04—Devices for imparting false twist
    • D02G1/08—Rollers or other friction causing elements
    • D02G1/082—Rollers or other friction causing elements with the periphery of at least one disc

Definitions

  • the invention relates to a friction disk according to the preamble of claim 1.
  • the object of the invention is to avoid this disadvantage.
  • the invention also divides the friction disk into zones, of which one zone performs the functions of twisting and conveying and the other zone performs the function of optimal thread guidance.
  • the zones for swirling and conveying on the one hand and the thread guide on the other hand are designed in such a way that the conveying effect is not impaired.
  • This precisely defined division of the zones can on the one hand result in an optimal friction effect and on the other hand an optimal thread guidance.
  • the thickness of the friction disks is limited to values that have previously been customary and are acceptable in mechanical engineering.
  • the friction false twister has three shafts 1, 2, 3, which are rotatably mounted in the base plate 4.
  • the waves are supported on the corners of an equilateral triangle.
  • the shafts are driven by a tangential belt 6 running in the machine length, which abuts a whorl 5.
  • the whorl 5 is attached to the shaft 1.
  • From the shaft 1, the other shafts 2 and 3 are driven in the same direction via pulleys 7 and 8 and small drive belts.
  • three friction disks 11, 12, 13 are mounted on the shafts 1, 2, 3 in such a way that they overlap in an overlap region 14.
  • the overlap region 14 lies over the center of the equilateral triangle, on the corner points of which the shafts 1, 2, 3 are mounted.
  • the base plate 4 has an insertion slot 9 which projects into the central overlap region 14 of the disks.
  • the friction disks 12 and 13 form a gusset 10 into which the thread is inserted so that it reaches the overlap area 14.
  • the formation of the new friction disks 11, 12, 13 results from FIGS. 3 and 5.
  • a known friction disk is shown in FIG. 7.
  • the friction disks have a spherical circumferential surface over which the thread 15 runs.
  • the thread 15 partially wraps around the spherical peripheral surface.
  • the wrap area is designated with UIV or UVI or UVIII.
  • the geometry of the friction false twister results in a thread guide in which the thread is inclined to the tangent over the circumference of the disc.
  • the angle of inclination alpha denotes the complement angle to the angle between the thread and the circumferential tangent. In the static state, this angle of inclination alpha is constant over the entire wrap area U.
  • FIGS. 4A, 6A, 8A a development of the circumference is shown in FIGS. 4A, 6A, 8A. This development represents the spherical circumference of the friction disk linearly both in the circumferential direction and in the axial direction.
  • the new friction disks according to FIGS. 3 and 5 now consist of zones with different coefficients of friction, namely a zone 16 with high friction, hereinafter referred to as “friction zone”, and a zone 17 with low friction, hereinafter referred to as “guide zone”.
  • the friction zone has e.g. compared to the thread a coefficient of friction of 0.25 and the guide zone a coefficient of friction of 0.1.
  • the friction zone has a larger radius of curvature than the guide zone.
  • the coefficient of friction there is a direct relationship between the coefficient of friction and the radius of curvature. That means: the greater the coefficient of friction, the greater the radius of curvature.
  • the decisive factor is rather the following: The disc becomes very thick due to a large radius of curvature. This is undesirable in mechanical engineering.
  • the contact distance cannot be as short as desired, since this would lead to impermissible surface pressures between the thread and the friction disk. Surface pressures are to be kept particularly low if the friction disc has a high coefficient of friction.
  • the radius of curvature of the friction disc which determines the length of the contact distance in the friction zone, should therefore be designed according to the permissible surface pressure.
  • the permissible surface pressure can only result from tests and experience and is very much dependent on the material on the one hand the friction surface and on the other hand the thread.
  • the radius of curvature of the guide zone is chosen to be as small as is expedient in mechanical engineering in order to achieve a small disk thickness and for thread guidance.
  • the radius of curvature of the friction zone can e.g. 7 mm, the guide zone is 2 mm.
  • the zones of different friction can now be arranged in a different order in the thread running direction.
  • the friction zone 16 is located at the entrance and the guide zone 17 is located at the exit of the friction disk.
  • the development of the circumference of the friction disk results in the following picture:
  • the thread first runs onto the friction disk at an angle of inclination alpha, specifically into the friction zone 16, which is essentially due to the geometrical design of the friction false twister and the resulting thread guide is due.
  • the thread is then very heavily carried over through the friction zone in the sense of a reduction in the angle of inclination alpha. Therefore, the movement component of the circumferential speed of the friction disk, which points in the direction of the thread axis, which is therefore effective in conveying, becomes smaller and smaller.
  • the angle of inclination alpha goes to zero.
  • the length of the friction zone 16 is limited.
  • the friction zone 16 Before the angle of inclination alpha approaches zero, the friction zone 16 is followed by the guide zone 17, which has only a small amount of friction. However, the thread carryover is in the low friction zone low. Therefore, there is no further decrease in the angle of inclination alpha.
  • the arrangement of the guide zone thus causes the thread to leave the friction zone at a minimum angle alpha and is therefore always exposed to a positive, but in no case a negative, conveying effect.
  • the thread tension diagram of FIG. 4B shows the effect on the thread tension.
  • the decrease in the thread tension does not continue, since the angle of inclination alpha and thus the conveying effect of the friction disc is reduced.
  • the thread tension remains essentially constant.
  • FIGS. 7 and 8 A friction disk of the prior art is now shown in FIGS. 7 and 8.
  • the wrap-around area UVIII is equipped with a uniform coefficient of friction. This means that at the beginning - as shown in FIG. 8B - the thread tension of the friction zone also decreases. Subsequently, however, the angle of inclination changes so decisively that the thread tension increases again. When the thread leaves the friction disc, the thread tension is higher than in the entrance of the friction disc. This shows that the delivery effect at the exit of the friction disc is negative.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Textile Engineering (AREA)
  • Yarns And Mechanical Finishing Of Yarns Or Ropes (AREA)
  • Braking Arrangements (AREA)

Claims (7)

  1. Disque de friction (11) pour la fausse torsion d'un fil synthétique (15), le disque (11) étant entraîné en rotation et présentant, sur son pourtour, une surface de friction incurvée sur laquelle le fil (15) passe transversalement à la direction périphérique, le disque de friction (11) présentant une zone (16) avec un rayon de courbure plus grand et un coefficient de friction plus élevé et une zone (17) avec un rayon de courbure plus petit et un coefficient de friction plus faible, les deux zones formant l'ensemble de la surface périphérique se trouvant en contact avec le fil,
    caractérisé par le fait que
    la zone (16) ayant le coefficient de friction plus élevé présente un rayon de courbure exclusivement plus grand.
  2. Disque de friction suivant la revendication 1,
    caractérisé par le fait
    que le coefficient de friction plus élevé s'élève à environ 0,25 et le coefficient de friction plus faible à environ 0,1.
  3. Disque de friction suivant l'une des revendications 1 ou 2,
    caractérisé par le fait
    que le rayon de courbure de la zone (16) à coefficient de friction plus élevé est d'environ 7 mm et le rayon de courbure de la zone (17) à coefficient de friction plus faible est d'environ 2 mm.
  4. Disque de friction suivant l'une des revendications 1 à 3,
    caractérisé par le fait que
    la zone (17) à coefficient de friction plus faible se trouve, dans le sens de déplacement du fil, en avant de la zone (16) à coefficient de friction plus élevé.
  5. Dispositif pour la fausse torsion d'un fil (15), comprenant une plaque de fixation (4) et trois arbres (1, 2, 3) qui sont montés en rotation autour d'axes parallèles sur la plaque de fixation (4) en étant situés aux angles d'un polygone équilatéral dont le nombre de côtés est égal au nombre des arbres, une pluralité de disques circulaires (11, 12, 13) fixés sur chaque arbre de telle manière que les zones marginales des disques se chevauchent en un point situé au milieu entre les arbres et forment entre elles un trajet de mouvement pour le fil, et un dispositif d'entraînement pour la rotation simultanée des disques dans le même sens, chaque disque (11, 12, 13) présentant un corps circulaire disposé coaxialement à l'axe de rotation de l'arbre associé et portant sur son pourtour une surface de friction sur laquelle le fil passe transversalement à la direction périphérique, et la surface de friction présentant axialement côte à côte une première zone (16) à coefficient de friction plus élevé et à rayon de courbure plus grand et une deuxième zone (17) à coefficient de friction plus faible et à rayon de courbure plus petit,
    caractérisé par le fait que
    la zone (16) à coefficient de friction plus élevé présente un rayon de courbure exclusivement plus grand, et que les deux zones forment l'ensemble de la surface périphérique en contact avec le filé.
  6. Dispositif suivant la revendication 5,
    caractérisé par le fait que
    la deuxième zone (17) est située dans le sens de déplacement du fil en avant de la première zone (16).
  7. Dispositif suivant la revendication 5 ou 6,
    caractérisé par le fait que
    le rayon de courbure de la première zone (16) s'élève à environ 7 mm et le rayon de courbure de la deuxième zone (17) à environ 2 mm.
EP90110857A 1989-06-14 1990-06-08 Disque de friction Expired - Lifetime EP0402782B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3919395 1989-06-14
DE3919395 1989-06-14

Publications (3)

Publication Number Publication Date
EP0402782A2 EP0402782A2 (fr) 1990-12-19
EP0402782A3 EP0402782A3 (fr) 1991-04-10
EP0402782B1 true EP0402782B1 (fr) 1995-09-20

Family

ID=6382717

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90110857A Expired - Lifetime EP0402782B1 (fr) 1989-06-14 1990-06-08 Disque de friction

Country Status (3)

Country Link
US (1) US5349808A (fr)
EP (1) EP0402782B1 (fr)
DE (1) DE59009674D1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH683700A5 (de) * 1991-06-21 1994-04-29 Rieter Ag Maschf Drallorgan für mechanisches Falschdrallspinnen.
DE4401321A1 (de) * 1994-01-18 1995-07-20 Temco Textilmaschkomponent Friktionsfalschdrallaggregat mit variabler Drehrichtung für S- bzw. Z-Drehung
US20050019325A1 (en) * 1996-01-08 2005-01-27 Carter Paul J. WSX receptor agonist antibodies
EP0943022B1 (fr) 1997-09-26 2001-12-12 B a r m a g AG Broche de fausse torsion
DE19814921A1 (de) * 1998-04-03 1999-10-07 Temco Textilmaschkomponent Geometrische Anordnung für eine Texturiervorrichtung

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1419085A (en) * 1972-03-06 1975-12-24 Scragg & Sons Yarn processing
DE2213881C3 (de) * 1972-03-22 1978-11-30 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Friktions-Falschdrallvorrichtung
CH564619A5 (fr) * 1973-02-12 1975-07-31 Kugelfischer G Schaefer & Co
DE2306853B2 (de) * 1973-02-12 1975-06-12 Kugelfischer Georg Schaefer & Co, 8720 Schweinfurt Reibscheibe
CH584780A5 (fr) * 1974-06-12 1977-02-15 Kugelfischer G Schaefer & Co
DE2518538B1 (de) * 1975-04-25 1976-01-29 Kugelfischer G Schaefer & Co Reibscheibe
US4051655A (en) * 1975-07-30 1977-10-04 Barmag Barmer Maschinenfabrik Aktiengesellschaft Friction false twister
DE7623421U1 (de) * 1976-07-24 1977-04-07 Barmag Barmer Maschinenfabrik Ag, 5600 Wuppertal Friktionsfalschdraller
JPS5361748A (en) * 1976-11-12 1978-06-02 Teijin Ltd Friction falseetwisting apparatus
DE2708204C2 (de) * 1977-02-25 1979-04-05 Feldmuehle Ag, 4000 Duesseldorf Falschdrallvorrichtung
US4218870A (en) * 1978-12-18 1980-08-26 Milliken Research Corporation False twist machine
DE3126726A1 (de) * 1980-07-16 1982-03-11 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid "reibscheibe"
DE8532434U1 (de) * 1985-11-16 1986-01-02 FAG Kugelfischer Georg Schäfer KGaA, 8720 Schweinfurt Reibrotor zum Falschdrallen von synthetischen Fäden

Also Published As

Publication number Publication date
DE59009674D1 (de) 1995-10-26
EP0402782A2 (fr) 1990-12-19
US5349808A (en) 1994-09-27
EP0402782A3 (fr) 1991-04-10

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