EP1387899B1 - Fachbildeeinrichtung mit federdämpfung - Google Patents

Fachbildeeinrichtung mit federdämpfung Download PDF

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Publication number
EP1387899B1
EP1387899B1 EP02727236A EP02727236A EP1387899B1 EP 1387899 B1 EP1387899 B1 EP 1387899B1 EP 02727236 A EP02727236 A EP 02727236A EP 02727236 A EP02727236 A EP 02727236A EP 1387899 B1 EP1387899 B1 EP 1387899B1
Authority
EP
European Patent Office
Prior art keywords
shedding device
core element
spring
coil spring
heald
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
EP02727236A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1387899A1 (de
Inventor
Hans-Jürgen BAUDER
Helmut WEINSDÖRFER
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.)
Deutsche Institute fuer Textil und Faserforschung Stuttgart
Original Assignee
Deutsche Institute fuer Textil und Faserforschung Stuttgart
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 Deutsche Institute fuer Textil und Faserforschung Stuttgart filed Critical Deutsche Institute fuer Textil und Faserforschung Stuttgart
Publication of EP1387899A1 publication Critical patent/EP1387899A1/de
Application granted granted Critical
Publication of EP1387899B1 publication Critical patent/EP1387899B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03C—SHEDDING MECHANISMS; PATTERN CARDS OR CHAINS; PUNCHING OF CARDS; DESIGNING PATTERNS
    • D03C3/00—Jacquards
    • D03C3/24—Features common to jacquards of different types
    • D03C3/44—Lingoes
    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03C—SHEDDING MECHANISMS; PATTERN CARDS OR CHAINS; PUNCHING OF CARDS; DESIGNING PATTERNS
    • D03C3/00—Jacquards
    • D03C3/24—Features common to jacquards of different types
    • D03C3/42—Arrangements of lifting-cords

Definitions

  • the strands are inevitably moved in one direction while being pulled in the other direction by a spring.
  • the strand is moved by the spring to form the lower compartment.
  • the spring is stationary or anchored to the ground at the other end in the weaving machine and keeps the harness cord and the heddle under tension in any operating condition.
  • the arrangement of spring, heald and harness cord shows resonance phenomena including the propagation of waves passing through the linear system.
  • the self-resonances of the system play no role as long as the speed of movement of the heald is small compared to the resonance frequency. But at the moment, where the moving speed of the heddle reaches the resonance frequency range, unpleasant waves occur in the spring.
  • the waves are excited in the spring by the movement of the heald and run towards the fixed end, where they are reflected and run back towards the heald. Under unfavorable circumstances, it may even happen that the heald is tension-free, because the returning shaft in the connection between the spring and the heald a phase position, which is directed against the initialized by the movement of the Harnischkordel movement.
  • the resonances within the spring also provide for increased mechanical stress and premature breakage. This is typical break points.
  • the lower spring attachment point consists of a plastic molded part, on which a threaded pin is formed. On the threaded pin, the coil spring is screwed.
  • the threaded pin carries at its free end two resiliently mutually movable legs which protrude into the interior of the spring and press against the spring. The two legs are in turn connected to each other at the end remote from the threaded pin and go over into two other legs, which form an open fork.
  • the heald between the Harnischkordel and the coil spring is kept taut.
  • the remote from the heald end of the coil spring is anchored stationary.
  • a damping element is present, which is in contact at least at several spaced locations with the coil spring and the originally straight coil spring imposes a non-straight course.
  • the coil spring is at points spaced from each other with the damping element in touch.
  • the contact force of the coil spring on the damping element is determined by the inherent elasticity of the spring and the degree of deflection.
  • the elasticity of the damping element By contrast, it plays virtually no role.
  • the modulus of elasticity of the steel coil spring is much less temperature dependent than the modulus of elasticity of plastic, and moreover, the modulus of elasticity changes less over time.
  • the damping element needs compared to the resilience of the coil spring to have no elasticity at all. It may be rigid relative to the force exerted by the coil spring in such a way that it is not pressed into another shape by the coil spring. In this way, it is possible, very accurate reproducible contact forces and thus very accurate reproducible frictional forces between the spring and the damping element to create.
  • the degree of deformation ie. the wavelength and / or the amplitude which urges the damping element of the coil spring changes over the length of the damping element. For example, in this way an increasing damping or coupling of the vibrations can be achieved.
  • the damping element is first relatively little deformed in the direction of the heald from the straight course and the deformation increases in the direction of the anchoring end of the coil spring. With very little dispersion, a very good damping is achieved on the damping element.
  • the damping element is preferably a core element which is arranged in the coil spring and linear. In this way, additional space for the damping element is saved, because it is located at the point that is already inevitable anyway.
  • the core element may have a non-straight course deviating from the straight course.
  • Another possibility is to use a per se straight core element which carries at a distance from each other discretely distributed wart-like projections or bumps with which the coil spring of the desired not straight course is imposed.
  • the diameter in the region of the projection or hump is smaller than the inside diameter of the helical spring.
  • this essentially represents a cylindrical structure which exhibits a wave-shaped course.
  • the waves define a regression line, so that on average a straight course of the spring comes about.
  • the wave-shaped course can be created by the core element forming a screw or by the core element forming waves which lie in a common plane.
  • a projection of the core element on a plane generates a wave-shaped band whose width corresponds to the diameter of the core element and whose wave-like nature substantially coincides with the wave or helical course of the core element.
  • the dimensions of the wave-shaped course are expediently defined on this band resulting from projection in the plane.
  • the wave-shaped course shows in the projection a wave depth, measured at an edge of the band, which lies between a wave crest and a wave trough between 0.1 and 3 mm.
  • the strength of this shaft stroke depends on how the diameter ratio between the core element and the inside diameter of the coil spring is dimensioned, and how strongly the coil spring is to be deflected or pressed against the core element.
  • the distances between wave crest and wave trough can be between 2 and 20 mm.
  • projections or bumps they can be arranged along a helical line, or in the simplest case zigzag, ie in each case two adjacent protrusions are located on opposite sides with respect to the core element.
  • the distance between the projections is suitably in the range between 5 mm and 30 mm, preferably between 5 mm and 20 mm.
  • the projections or bumps are expediently integral with the core element and can be either molded or molded, when the core element is manufactured in this form in the primary molding process. Another possibility is to produce the bumps by local deformation, for example, the crimping of ears. The last possibility is appropriate if the core element consists of a permanently deformable material, for example metal.
  • the length of the core element is expediently dimensioned such that at least one full wave having the above dimensions can be produced.
  • the core element may be loose in the coil spring or fixedly connected to the lower anchoring means.
  • Suitable materials for the core element are thermoplastics such as polyamide, polyethylene and polyurethane or other materials such as metal, ceramic, thermosets or vulcanizable materials in question.
  • the shed forming device according to the invention is preferably used in jacquard weaving machines.
  • the arrangement according to the invention is not on Jacquard machines but can also be used in normal weaving machines for producing un-patterned woven fabrics or dobby machines.
  • the shed-forming device is also, for example, a dobby, a Jacquard machine or a comparable drive device in order to set the strands in motion.
  • the heald may be provided at the respective end of the heddle shaft with a plastic molded part having, for example, a screwed into the coil spring thread.
  • connection of the coil spring with the lower or the upper anchoring member can be done according to the prior art.
  • Fig. 1 shows very schematically the essential for understanding the invention functional parts of the shed-forming device in a Jacquard loom.
  • a drive device 1 of which a pulley 2 is illustrated.
  • a strung cord fastened to a strupter bottom 3 goes out, which merges into a harness cord 4 which passes between a glass grate or a guide bottom 5.
  • the Harnischkordel 4 continues to a chorus board 6 and exits through a hole 7 down.
  • a heald 8 is attached at the lower end, ie at the end of the Harnischkordel 4, which is spaced from the pulley 2, a heald 8 is attached.
  • the heald 8 has an eyelet or an eye 9 for a warp thread 11. From the eyelet 9 go from an upper and a lower heddle shaft 12, 13, which lie on a common line. The lower end of the lower heddle shaft is connected to a return spring 14, which is anchored at 15 on the machine frame or on the ground.
  • the movement of the pulley 2 is transmitted via the Harnischkordel 4 on the heald 8.
  • the Harnischkordel 4 is pulled up and the eye 9 pulled up from the neutral position to form the upper compartment.
  • the return spring 14 is thereby stretched more than in the neutral position of the heddle 8, which corresponds to the closed shed.
  • the harness cord 4 is lowered, the return spring 14 moves downwardly as the harness cord 4 moves down, the heald 8 downward.
  • the respective warp thread 11 forms the lower compartment.
  • the upward movement of the heald 8 is an inevitable motion which is imposed rigidly over the longitudinally inconvenient harness cord 4.
  • the opposite direction is a movement initiated by the return spring 14 and, to that extent, only conditionally inevitable or rigid.
  • the harness of harness 4, heald 8, warp 11 and return spring 14 is a spring-mass system having one or more resonant frequencies.
  • the frequency with which the heald 8 is brought from the closed shed neutral position to the upper shed position or the lower shed position is about 10 Hz.
  • These frequencies are determined by the drive system 1 imposed, are in the order of the resonance frequencies of the entire system, or the resonance frequency of subsystems.
  • harmonics occur and it can Form at these frequencies waves on the linear structure between the chorus board 6 and the anchoring point 15 in the return spring 14, which are reflected without appropriate countermeasures to the anchoring point 15 and become standing waves in the return spring 14.
  • the return spring 14 is extremely heavily loaded at certain points and tends to break.
  • the lower anchoring point of the return spring 14 is according to Fig. 2 educated.
  • the in Fig. 2 is shown in sections, belongs to an anchoring element 16 which is formed substantially rod-shaped.
  • the anchoring element 16 has at its lower end an eyelet 17 which is to be hooked into a corresponding rail which is fixedly mounted on the machine frame.
  • From the eyelet 17 is a substantially cylindrical shaft 18, which is provided at its upper end with a collar 19. Concentric with the shaft 18 extends above the collar 19, an external thread pin 21.
  • the external thread pin has a length corresponding to about 10 spring coils.
  • the return spring 14 is screwed.
  • the return spring 14 is a cylindrical spring wound from a cylindrical steel wire, in which the turns in the relaxed state usually lie on each other.
  • the threaded pin 21 passes into a core element 22, which, as shown, has a non-straight course.
  • the core element 22 forms valleys 23 and vertices 24. It is deformed such that the area defined by the valleys and vertices represents a plane. This means that in a 90 ° rotated side view, compared to Fig. 2 , the core element 22 is straight.
  • the wave trough 23 on the opposite side of the core element 22 leads to a wave vertex, which deforms the spring 14 in the correspondingly opposite direction, like the vertex 24.
  • the core element 22 has a circular cross section at all points, wherein the diameter of the cross section is smaller by about 5-30% than the inner diameter of the helical spring 14.
  • the diameter of the core element 22 may be constant over its length or decreasing towards the tip.
  • the core member 22 is integrally molded together with the threaded stem 21, the shaft 18 and the eyelet 17 made of plastic. Suitable plastics are polyamide, polyethylene, polyurethane, polyester.
  • the wave-shaped course which the core element 22 describes is so strong that the wave troughs and wave crests 23, 24 of the helical spring 14 impose a corresponding course.
  • the coil spring 14 no longer runs straight in the region of the core element, but with a zigzag movement, which corresponds to the core element 22, as indicated by the dashed lines 25 and 26.
  • the deflection of the spring 14 in the lateral direction is mitigated in accordance with the difference in diameter between the outer diameter of the core member 22 and the clear width of the coil spring 14.
  • the shape of the representation of the core element 22 in FIG Fig. 2 corresponds to a projection of the core element 22 on a plane, and that projection in which the by the The projection produced a meandering band that has the largest amplitude.
  • the amplitude of the oscillation measured between tip and tip about 0.1 to 3 mm, preferably 0.1 to 1 mm, while the Wavelength of the vibration is between about 4 and 40 mm; both values can vary along the core element 22.
  • the amplitude of the wavy line i. increase the degree of lateral deflection, starting from the free end of the core member 22 to the threaded pin 21. This ensures that the spring 14 rests with its turns on the first wave crest with small lateral force, because it is less deformed than at a wave crest, which is closer to the threaded pin 21.
  • a plastic molded body 27 is formed, which corresponds in terms of its construction to the opposite end of the anchoring element 16.
  • the plastic molded body forms a collar 28, and a threaded pin 29 which extends coaxially to the heddle shaft 13.
  • the threaded pin 29 carries an external thread, which may be cylindrical or conical and on which, as described above, the return spring 14 is screwed until the end, as shown, abuts the collar 28.
  • the shock passes as a wave in the direction of the anchoring element 16.
  • the shock runs as a longitudinal wave on the tensioned return spring 14. It is ensured in normal operation that the Spring coils of the return spring 14 in no operational situation lie on each other. Due to the shock wave, however, such a clash may well happen.
  • the core element 22 thus effectively provides for suppression of standing waves on the return spring 14.
  • the damping effect by the core element 22, the total length of which is between 5% and 40%, preferably between 10% and 30% of the operationally tensioned return spring 14, also ensures that longer-frequency waves are effectively damped to suppress the formation of standing waves whose wavelength is on the order of the tensioned spring.
  • the core element 22 in one piece with the threaded pin 21.
  • the core element can be provided to provide its damping effect at any point.
  • FIG. 4 another embodiment of a core member 22 is shown, which serves to impose a non-straight course of the coil spring 14, at the same time only a point contact between the core member 22 and the coil spring 14 comes about to produce the damping effect described above.
  • the core element 22 consists of a straight shaft 31 whose diameter is significantly smaller than the inside diameter of the cylindrical interior within the coil spring 14.
  • On the outside of the shaft 31 are wart-like projections or bumps 32 which are arranged along a helical line.
  • the bumps or extensions 32 are mutually offset by 90 °, ie it arises in the projection, as the cross section of Fig. 5 shows a four-pointed star.
  • the area of each hump 32 is still the largest diameter
  • the coil spring 14 is made of their natural exactly straight shape in forced a helical shape.
  • the height of the hump 32 measured in the radial direction with respect to the axis of the shaft 31 and the distance of the projections 32 measured in the longitudinal direction of the shaft 31 define the force with which the coil spring 14 abuts against the apices of the extensions 32.
  • FIGS. 4 and 5 consists of the core element 22 in one piece from a plastic molding.
  • the wart-like extensions 32 are integrally formed. Their axial extension is smaller than their axial distance from each other.
  • Fig. 6 instead of integrally forming the wart-like projections 32 on a plastic molding, there is also the possibility according to Fig. 6 to use a core element 22 whose shaft 31 consists of an originally cylindrical metal wire.
  • the projections or bumps 32 are formed by the starting material is crushed sideways, so that as the cross section according to Fig. 4 shows the material is forced radially outward. The result is "ears" that protrude radially beyond the contour of the original circular cross-section. The effect is the same as before with reference to the embodiment according to Fig. 2 described.
  • a shed-forming device in a Jacquard weaving machine has the formation of, for example, the lower shed a return spring, the niedes is rigidly anchored in the weaving machine or on the ground.
  • a core element is provided which applies at spaced locations on the inside of the spring and the spring imposes a course which deviates from the straight course. As a result, frictional forces between the spring and the core element are generated, which contribute to the damping of the spring movement.

Landscapes

  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Springs (AREA)
  • Vibration Dampers (AREA)
  • Vibration Prevention Devices (AREA)
  • Vehicle Body Suspensions (AREA)
EP02727236A 2001-05-17 2002-03-15 Fachbildeeinrichtung mit federdämpfung Expired - Lifetime EP1387899B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10124022A DE10124022C2 (de) 2001-05-17 2001-05-17 Fachbildeeinrichtung mit Federdämpfung
DE10124022 2001-05-17
PCT/DE2002/000958 WO2002092892A1 (de) 2001-05-17 2002-03-15 Fachbildeeinrichtung mit federdämpfung

Publications (2)

Publication Number Publication Date
EP1387899A1 EP1387899A1 (de) 2004-02-11
EP1387899B1 true EP1387899B1 (de) 2008-04-02

Family

ID=7685126

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02727236A Expired - Lifetime EP1387899B1 (de) 2001-05-17 2002-03-15 Fachbildeeinrichtung mit federdämpfung

Country Status (8)

Country Link
US (1) US7036532B2 (ja)
EP (1) EP1387899B1 (ja)
JP (1) JP4240366B2 (ja)
CN (1) CN100340704C (ja)
AT (1) ATE391199T1 (ja)
DE (2) DE10124022C2 (ja)
TN (1) TNSN03114A1 (ja)
WO (1) WO2002092892A1 (ja)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10329219B4 (de) * 2003-06-28 2007-04-05 Groz-Beckert Kg Schaftstab mit beweglichem Litzendämpfungselement
FR2857675B1 (fr) * 2003-07-18 2006-01-13 Staubli Sa Ets Cadre lisses et metier a tisser pourvu d'au moins un tel cadre
DE102004044783A1 (de) * 2004-09-16 2006-03-30 Deutsche Institute für Textil- und Faserforschung (DITF) Stuttgart Fachbildeeinrichtung mit verformter Feder
EP1908863B1 (de) 2006-10-06 2009-04-08 Groz-Beckert KG Weblitze für Jacquardwebmaschine
EP2166138A1 (de) * 2008-09-23 2010-03-24 Groz-Beckert KG Jacquardlitze mit geprägtem Fadenaugenbereich
FR3027313B1 (fr) * 2014-10-16 2016-11-18 Staubli Lyon Lisse pour metier a tisser, metier a tisser equipe d'une telle lisse et procede de fabrication d'une telle lisse
FR3027314B1 (fr) * 2014-10-16 2019-04-26 Staubli Lyon Lisse pour metier a tisser et metier a tisser equipe d'une telle lisse
FR3027315B1 (fr) * 2014-10-16 2019-04-26 Staubli Lyon Lisse pour metier a tisser et metier equipe d'une telle lisse
EP3112509A1 (en) * 2015-07-02 2017-01-04 NV Michel van de Wiele Connecting member for connecting elements of a shed forming mechanism for a weaving machine with each other
CN106592049A (zh) * 2017-01-10 2017-04-26 约科布·缪勒机械制造(中国)有限公司 一种防共振蛇形支架
GB2566092B (en) 2017-09-04 2022-06-15 Kristian Fjelldal Alf An energy-absorbing structure for a tether line, and a tether line incorporating the same

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2072541U (zh) * 1990-07-10 1991-03-06 黄高玉梅 织布控制提花装置
CN2103570U (zh) * 1991-07-17 1992-05-06 张海林 精简提花选针机构
CN2175244Y (zh) * 1993-06-19 1994-08-24 山东淄博毛巾厂 提花织机的提综装置
FR2718810B1 (fr) * 1994-04-19 1996-06-14 Staubli Verdol Dispositif d'assemblage de l'extrémité d'un ressort hélicoïdal par rapport à un autre organe.
FR2756849B1 (fr) * 1996-12-06 1999-05-07 Tardy Jean Jacques Dispositif amortisseur pour ressort de lisse de metier a tisser jacquard
FR2766501B1 (fr) * 1997-07-23 1999-09-10 Staubli Lyon Embout pour element de metier a tisser, element pourvu d'un tel embout et metier a tisser pourvu d'un tel element
FR2800395B1 (fr) * 1999-10-28 2002-03-15 Staubli Lyon Dispositif et ensemble de solidarisation de ressort de harnais jacquard et metier a tisser equipe d'un tel ensemble

Also Published As

Publication number Publication date
DE10124022C2 (de) 2003-04-10
WO2002092892A1 (de) 2002-11-21
US20040168735A1 (en) 2004-09-02
JP4240366B2 (ja) 2009-03-18
CN1509354A (zh) 2004-06-30
CN100340704C (zh) 2007-10-03
ATE391199T1 (de) 2008-04-15
DE10124022A1 (de) 2002-12-12
TNSN03114A1 (en) 2005-04-08
US7036532B2 (en) 2006-05-02
JP2004526883A (ja) 2004-09-02
EP1387899A1 (de) 2004-02-11
DE50212019D1 (de) 2008-05-15

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