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
• • 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
  • D02G1/06—Spindles

Definitions

• the invention relates to a false twist device for false twisting of a synthetic thread according to the preamble of claim 1.
• the friction disks are arranged on three shafts which are rotatably held on a bearing block.
• the shafts are spaced from each other to form a triangle in such a way that the friction discs overlap in the center of the triangle.
• the shafts are driven by a drive in such a way that the friction disks rotate at a substantially constant peripheral speed.
• the thread is guided in the center on the circumferential surfaces of the friction disks, so that a winding thread run is formed.
• the thread is guided in an inclined run over the circumferential surfaces of the friction discs.
• the friction mechanisms acting between the thread and the peripheral surface of the friction disks result in a tensile force for conveying the thread and a transverse force for twisting the thread being generated on the thread.
• the ratio between the tensile force for conveying the thread and the transverse force for twisting the thread essentially depends on the disc geometry and on the degree of overlap of the discs.
• thread-sparing textures can be used as the conveying effect increases.
• a greater funding effect can be however, often only at the expense of reduced swirling. There is therefore a desire that the conveying effect and swirl generated by the false twist unit be in a favorable relationship to one another. However, it can be observed that an increasing funding effect can only be achieved at the expense of a decreasing swirl.
• Another object of the invention is to provide a disk geometry of the friction disks for a false twist device of the generic type, with which an optimum between the conveying of the thread and the twisting of the thread is achieved, regardless of the thread type.
• This object is achieved by a false twist device with the features of claim 1 and by a friction disc with the features of claim 8.
• Advantageous developments of the invention are defined by the features and combinations of features of the respective subclaims.
• the invention takes a new approach, which is based on the fact that the friction disks have the largest possible disk diameter. Considered in isolation, increasing the disk diameter of the friction disks would initially lower the peripheral speed of the friction disks and thus reduce the swirl. On the other hand, however, as the disk diameter increases, the thread overflow on the peripheral surface of the friction disk changes so that the proportion of the conveying effect increases. Surprisingly, it was found that in spite of the enlarged disc diameter, if a certain disc width is maintained and the functional discs have a minimum overlap, the loss of swirl is compensated, so that despite high production speeds, a thread-friendly maximum swirl on the thread is achieved.
• the overlap of the friction discs is determined by a ratio between the disc diameter and the center distance of the shafts, which is above the value 1.45.
• the friction disks have a disk width in the range from 9.5 mm to 11.5 mm.
• the upper limit of the ratio formed by the disk diameter and the center distance is the fixed center distance of the shafts.
• the friction disks having a geometry with a disk diameter in the range from 54 mm to 62 mm, a disk width in the range from 9.5 mm to 11.5 mm and a profile radius on the circumferential surface of the friction disk, which forms a ratio in the range from 1.6 to 2.0 with the disk width.
• the profile radius is preferably symmetrical on the peripheral surface of the friction discs, so that the inlet and the outlet of the thread on the peripheral surface of the friction discs are kept the same.
• the friction disks can be formed from a ceramic, an elastomer or a plastic. Regardless of the choice of material this results in an advantageous extension of the operating time, in particular for all soft materials.
• FIG. 2 schematically shows a top view of the exemplary embodiment from FIG. 1,
• FIGS. 1 and 3 schematically shows a cross-sectional view of a friction disk of the exemplary embodiment from FIGS. 1 and
• FIG. 4 schematically shows a side view of FIG. 3.
• FIG. 1 and FIG. 2 schematically show a first embodiment of the false twist device according to the invention.
• Fig. 1 shows the false twist device in a perspective view and in Fig. 2 the false twist device is shown in a plan view.
• the following description applies to both figures, insofar as no express reference is made to one of the figures.
• the false twist device has a bearing block 1.
• several shafts 2.1, 2.2 and 2.3 are held so that they can project and rotate.
• the shafts 2.1, 2.2 and 2.3 are coupled at their bearing end to a drive, not shown here.
• a drive is known for example from EP 0 744 480 AI.
• the waves 2.1, 2.2 and 2.3 are arranged in a triangle.
• several friction disks 4.1 to 4.7 are arranged offset to one another.
• the shaft 2.1 has a run-in disk 3 and two friction disks 4.3 and 4.6 in the thread running direction at a distance from one another.
• the second shaft 2.2 has a first friction disc 4.1 arranged directly below the run-in disc 3 and the further friction discs 4.4 and 4.7 which follow at a distance.
• the third wave 2.3. has a first friction disc 4.2 in the thread running direction, which is arranged between the friction discs 4.1 and 4.3. At a distance from the friction disc 4.2 there follows another friction disc 4.5, which is arranged between the friction discs 4.4 and 4.6. At the end, the shaft 2.3 carries an outlet disk 5.
• the shafts 2.1, 2.2 and 2.3 are each arranged with the same center distance A from one another to the triangle.
• the friction disks (the inlet disk 3 is not shown in FIG. 2) have such a large disk diameter D that the friction disks 4.1 to 4.7 overlap in the center of the triangle formed by the shafts 2.1 to 2.3.
• the overlap of the friction disks 4.1 to 4.7 is defined by the ratio between the disk diameter D and the center distance A as follows:
• the discs 3, 4.1 to 4.7 and 5 are rotatably connected to the shafts 2.1, 2.2 and 2.3, so that the drive disc 3, the friction discs 4.1 to 4.7 and the output disc 5 rotate in the same direction when the shafts 2.1, 2.2 and 2.3 are driven.
• an EM thread guide 7 is provided on the inlet side and an outlet thread guide 8 is provided on the outlet side in order to insert a thread 7 into the thread
• the thread 6 is guided in a tortuous, screw-shaped thread run along the circumferential surfaces of the inlet disk 3, the friction disks 4.1 to 4.7 and the outlet disk 5. Due to the friction mechanisms acting between the thread 6 and the circumferential surfaces of friction disks 4.1 and 4.7, a false twist is built up on the thread 6 and is planted back in the thread 6 against the direction of the thread running. The false twist is released on the outlet side and the thread leaves the aggregate untwisted via the outlet thread guide 8.
• the inlet disk 3 has a polished peripheral surface, so that the thread can slide over the peripheral surface without any significant effect. In relation to the friction disks 4.1 to 4.7, the inlet disk 3 can have a small disk diameter. The inlet disk 3 thus only takes over a thread guide.
• the stack of disks of the overlapping disks is delimited on the outlet side by the outlet disk 5.
• the outlet disc 5 is preferably designed with a relatively sharp-edged, limited peripheral surface, so that the thread receives a certain spread after overflow. A residual twist on the thread can thus advantageously be reduced.
• a friction disc is shown, as used in the embodiment of FIG. 1.
• the friction disk is shown in FIG. 3 in a cross-sectional view and in FIG. 4 in a side view with the thread overflowing.
• the disk geometry can be seen in the illustration shown in FIG. 3.
• the friction disc has a disc diameter D.
• the disc diameter D is to be selected as a function of the center distance between the shafts of the exemplary embodiment shown in FIG. 1. For the center distances currently common in the state of the art in the range of max.
• the disk diameter D of the friction disk is 39.5 mm in the range from 54 mm to 62 mm.
• the friction disk has a disk width B in the range from 9.5 to 11.5 mm.
• the profile radius R on the peripheral surface 9 of the friction disk which is preferably symmetrical, forms the following relationship with the disk width B:
• the disk body 10 of the friction disk can be formed from a ceramic, a plastic, preferably from polyurethane, or from an elastomer, preferably HNBR.
• FIG. 4 schematically shows the situation in which the friction disk rotates and a thread 6 contacts the peripheral surface 9.
• the relative movement between the peripheral surface 9 of the friction disc and the thread 6 triggers several friction mechanisms, which are essentially defined by Eytelwein's laws and Euler's rope friction. It is essential, however, that a tensile force Fp and a transverse force Fp are generated on the thread by rotating the friction disk.
• the tensile force F F acting in the running direction of the thread 6 represents the so-called conveying component.
• the transverse force F D acting transverse to the thread running direction is largely responsible for the twist of the thread.
• the tractive force can Disc speed can be influenced.
• the delivery rate increases with increasing disc speed.
• PES threads it is customary for PES threads to choose a thread tension ratio of thread tension outlet side to thread tension inlet side of the false locking device which is less than one. Taking such relationships into account, it is therefore essential for the production of crimped threads that in the texturing process through in the texturing process the false twist device the generated tensile forces Fp and shear forces F D lie in the predetermined size ranges.
• the disc geometry according to the invention enables an improved conveying effect and thus a further reduction in the thread tension with the same or improved twist.
• the number and the arrangement of the disks on the shafts are exemplary.
• more than seven or less than seven friction disks can be arranged to overlap to treat a thread.
• the invention is not limited to the disc materials mentioned, the discs of the false twist device could also be made of metal.
• the choice, arrangement and configuration of an inlet disk or an outlet disk is also exemplary. LIST OF REFERENCE NUMBERS

Landscapes

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

Priority Applications (2)

Applications Claiming Priority (2)

Publications (1)

Family

ID=34305983

Family Applications (1)

Country Status (5)

Cited By (2)

Families Citing this family (4)

Citations (5)

• 2003
  • 2003-09-20 DE DE2003143619 patent/DE10343619A1/de not_active Withdrawn
• 2004
  • 2004-09-17 DE DE502004005523T patent/DE502004005523D1/de not_active Expired - Fee Related
  • 2004-09-17 TW TW093128220A patent/TW200513556A/zh unknown
  • 2004-09-17 CN CN 200480027191 patent/CN1856602A/zh active Pending
  • 2004-09-17 EP EP04765343A patent/EP1664406B1/de not_active Not-in-force
  • 2004-09-17 WO PCT/EP2004/010450 patent/WO2005031051A1/de active IP Right Grant

Patent Citations (5)

Also Published As

Similar Documents

Legal Events