JPH0364610B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention provides a method for processing synthetic fiber yarn in a texturing machine while heating the yarn by tightening the yarn between two friction member surfaces having a motion component perpendicular to the direction of yarn travel. This invention relates to a friction false twisting machine for applying false twist to materials.

In the friction false twisting machine disclosed in German Patent Application No. 2958522, at least one friction member surface is formed by the end face of a flexible rotary disk, the rotary disk having a rear surface thereof The thread is pressed against the surface of another moving friction member, such as a rigid disc, a flexible disc or a roller, by means of a crimping device acting on the thread.

The friction false-twisting machine known from German Patent No. 1 192 779 has been improved by the above-mentioned construction, in which the friction surface is There are no longer any pulsations or fluctuations in the frictional force between the thread and the thread.

In the prior art described in DE 31 23 671, which improves the friction false twisting machine based on DE 1 192 779 for the same purpose, one rotary disk is rotated with respect to its axis. The thread is clamped between the surface of the member and the friction surface of the rotating disk by means of a crimping device which is tilted out of a plane perpendicular to the axis or axis of rotation. It is becoming more and more crowded.

The object of the invention is to further improve the known friction false twisting machine in order to produce a line contact between the yarn and the friction surface in the ring-shaped friction area, thereby increasing the frictional force, while The goal is to reduce wear.

The constituent means of the present invention for solving the above problem is that the rotating disk is made of a spring-elastic thin metal plate, and has a ring-shaped inner section forming a hub, and a ring-shaped outer section forming a friction ring. an intermediate section located between the hub and the friction ring, the intermediate section being cut so as to create a flexible joint section consisting of a plurality of webs between the sections of the hub and the section of the friction ring. It has a notch or notch, and the stiffness, number and length of the webs are such that the friction ring can be deflected relative to the hub by an axis-parallel force. If the rotary disk is constructed in this way, it is possible to mold it in one piece, for example by stamping, from one piece with corresponding notches or notches. It is therefore advantageous for the rotating disc to be made from a high-strength, spring-elastic, steel sheet with a thickness of 0.1 to 0.5 mm, in which case the flexible connecting sections are formed by notches,
Manufactured by notching or cutting out.

The webs may, for example, extend secantly or tangentially with respect to the hub, or be constructed in the form of a double hook. When configured in the form of a double hook, each web has two substantially radial ends connected to the friction ring on one side and the hub on the other side, and one substantially concentric end to the hub. It consists of a middle part. What these embodiments aim to achieve is to configure the flexible coupling section to be rigid for the transmission of torque from the hub to the friction ring and flexible for the transmission of bending moments from the hub to the friction ring. be. It is also possible, by a combination of embodiments of the invention, to configure the flexible coupling section only for centering the friction ring and the flexible foil for torque transmission.

In a preferred embodiment, the webs are constructed as parallel springs. This ensures that the friction ring deflects parallel to itself.

Another embodiment of the flexible coupling section is as defined in claim 4, on a circle concentric to the hub of a rotating disk made of a one-piece piece of material, for example sheet steel. The point is that notches of equal length are provided in the . These cuts each leave one web between adjacent ends. This reduces the bending stiffness between the hub region of the rotary disk and the friction ring.

Such cuts may be provided on two or more circles of different diameters concentric to the hub, with the webs between adjacent parts of the cuts being offset between the circles.

For example, if the cuts are configured so that each cut extends over a center angle of 180° including the web at one end, the webs on adjacent circles are 90° from each other.
It has been shifted by The advantage that the friction ring is deflected parallel to itself is that, according to an embodiment of the invention, the rotating disk is composed of two flexible, spring-elastic disks, both disks being This is obtained by fixedly connecting the inner and outer circumferences to each other in the form of parallel springs, in which case the friction lining is fitted in the ring-shaped outer circumferential area of the friction-acting end face of the rotary disk, or The two discs form a flexible connecting section between the hub and the friction ring.

If the rotary disk is made from a one-piece piece of material, for example a sheet of steel, a plurality of cuts are provided in the rotary disk to form the flexible coupling sections, and the cuts are connected to the hub. A substantially circumferentially extending tongue is formed between the friction ring and the tongue, which at one end is connected by a web to the outer periphery of the hub and at the other end by a web to the friction ring. It is connected to the inner circumference of. This improves the torque transmission without increasing the bending stiffness between the hub and the friction ring.

In all embodiments, it is advantageous that the friction ring itself is also spring-elastic, which improves quiet and stable rotation compared to a single flexible disk, while the friction ring is sufficiently deformable that it can be deflected relative to itself and substantially parallel to the yarn travel path, or it can conform to the yarn travel path and counter-rotating opposing friction surfaces.

All these measures allow mechanical decoupling of the hub area and the ring-shaped friction area from each other in the case of a flexible disk clamped to the shaft, so that the friction ring can be removed even by a light pressure force. Serves for the advanced purpose of reducing the bending stiffness between the hub and the friction ring while ensuring the torque transmission between the hub and the friction ring so as to contact the thread easily and linearly .

Starting from this point, another object of the invention is to ensure that the friction ring does not significantly impede the deformations that it inevitably undergoes when it deflects (swings) out of its normal plane of rotation relative to the hub. It is to constitute a friction ring.

In order to solve this problem, in the present invention, the friction ring is made of a spring-elastic material such as a thin plate of spring steel, and is divided into a plurality of segments by a plurality of cuts, and these segments are connected to each other by a web. Therefore, they are connected to each other. As a result, the segments form a unit that is fixed in the circumferential direction, but which can be easily twisted approximately around a center line (torsion line). This circular torsion line has a diameter between the largest and smallest diameter of the friction ring.

If such an easily twistable friction ring is swung out of the normal plane of rotation relative to the hub under the pressure force, it first comes into point-like contact with the yarn.
However, since the friction ring exhibits only a small opposing moment to its torsion, only a small pressing force is required to bring the friction ring into line contact with the thread.

The segments are formed by a plurality of inward radial cuts starting from the outer periphery of the friction ring, in which case a circumferentially closed annular portion remains on the inner periphery of the friction ring. The segments may also be formed by a plurality of outward radial cuts starting from the inner periphery of the friction ring so as to leave a circumferentially closed annular portion on the outer periphery of the friction ring. Furthermore, a plurality of outward radial cuts starting from the inner periphery of the friction ring and a plurality of inward radial cuts starting from the outer periphery of the friction ring are provided in approximately the central area of the friction ring, in other words, between the friction ring and the torsion. It is also possible to leave an annular portion closed in the circumferential direction within the range of the line. The outward radial incisions and the inward radial incisions are offset from one another (particularly preferably evenly). These radial cuts result in a plurality of radial tongues that are fixed to the circumferentially closed toroidal section, the radial tongues having a small diameter compared to said closed toroidal section. It only has bending stiffness. Overall, this means that the friction ring can be easily twisted about the torsion line.

In addition, in order to facilitate twisting, the friction ring is divided into a plurality of individual rings by a plurality of concentric cuts, and these individual rings are connected to each other by a plurality of webs offset from each other in the circumferential direction. It is also possible to leave it as is. As a result, the friction ring does not lose its strength properties as a spring-elastic surface body, and thus has a particularly low torsional stiffness. The individual rings have a width of 1 to 2 mm, whereas the notches are about 1/10 mm wide.

On the thread contact side, the friction ring is provided with a friction lining made of, for example, rubber, polyurethane or other material with the desired friction and wear properties. Advantageously, the friction lining made of rubber or other reticulated material is vulcanized to completely or partially fill the notches in the friction ring. This treatment is particularly effective for vibration damping.

In order to facilitate the deformability of the friction ring and the line contact with the thread, the friction ring is constructed as a rotating body part with a convex outer circumferential wall, for example a mitral-shaped spherical part or a parabolic part. is advantageous. In this case the radius of curvature of the convex surface is chosen to ensure line contact.

According to the invention, it is possible to manufacture the rotating disk from a single spring-elastic thin metal plate, for example a spring-elastic high-strength steel plate, to make cuts in it, and/or to punch out parts of it from the steel plate. become.

As in known friction false twisting machines, the pressing force is applied in particular by means of plungers or rollers, etc.
The plunger resiliently contacts the back side of the friction ring. In this case, good frictional conditions between the friction ring and the plunger must be taken into account. In order to obtain this good frictional state, the surface of the plunger is made of a material with favorable frictional properties, for example graphite, or air or liquid lubrication is provided between the plunger and the friction ring, or
The plunger can be brought into contact with the friction ring by a roller. In a particularly advantageous embodiment, a further thin flexible disk is arranged on the rear side of the rotary disk, at least in the area of the friction ring, which has favorable frictional properties, in particular good sliding properties, in contrast to the plunger. In this way, scarfing and other wear and tear will not occur even if the lubricating action is lost.

In order to enhance stable and quiet rotation, it has been found advantageous to crimp such a flexible friction disk from its rear side as follows. That is, the pressing force is made to act in front of the thread travel path line when viewed in the rotational direction of the friction ring. In the embodiments of the friction ring according to claims 9 to 14, the point of force application of the plunger lies on the line of symmetry between the two friction discs, and the running path line of the thread lies on the line of symmetry. It is advantageous to be located behind the Otherwise, the running path line of the thread must be guided on the line of symmetry and the point of force application of the plunger must be located in front of the line of symmetry.

In order to increase the stable and quiet rotation of the rotary disk, in particular its friction ring, a substantially rigid disk is arranged on the rear side of the friction ring which the plunger presses, the outer diameter of which is equal to the inner diameter of the friction ring. However, it does not extend to the outer periphery where the plunger contacts. This rigid disk is
The deflection of the friction ring from its normal plane causes an opposite movement on the side offset by 180° relative to the crimping device, preventing it from swinging out of said normal plane.

The friction lining used for the friction ring consists of an elastically flexible material with good sliding properties, for example a selected rubber mixture. But again,
It is also possible to coat the cushion-like material with a sheet having good frictional and sliding properties. It is also possible to embed hard particles, such as ceramic particles or diamond particles, as rotational entrainers in the elastic, flexible matrix.

The present invention provides a flexible spring-elastic property for false twisting synthetic fiber yarns in a textured machine while twisting the yarns by the friction of the yarns in a ring-shaped area (friction ring) on the end surface of a rotating disk. The present invention also relates to a circular friction disk made of a material, characterized in that it is made of the constituent elements set forth in any one of claims 1 to 18.

Next, embodiments of the present invention will be explained in detail with reference to the drawings.

1 and 2 show two friction discs 1, 2 of a friction false twister, which in a clamping area 6 tighten the yarn 5 between the friction linings 3 and 4. The friction disk 1 is rotatably driven by a shaft 8.
can be elastically deflected against. Friction disk 2
is fixedly mounted on a rotationally driven shaft 9. In FIGS. 1 and 2, only the fixed bearing housing 10 of the shaft 8 is shown. The drive devices for the shafts 8 and 9 are not shown. Friction discs 1 and 2
are relatively inclined in this embodiment so as to tighten the thread 5 between the friction linings 3 and 4 in the upper tightening region 6. In the lower overlap region 7 the friction linings 3 and 4 do not come into contact with the thread 5. This non-contact state is caused by the crimping device 17,
A plunger 18 of the crimping device presses against the back side of the elastically deflectable friction disk 1 in the clamping region 6 via a spring 19 . Due to this pressure, the friction disk 1 is swung out of a plane perpendicular to the axis 8 in the tightening region 6, so that a force in the perpendicular direction is applied to the thread 5. In the variant shown in FIGS. 3 and 4, the plunger 18 of the crimping device 17 is moved in the area of the friction ring with the friction lining 3, viewed in the direction of rotation of the elastic spring-like friction disk 1 or the friction lining 3. It comes into contact with the back surface of the soft friction disk 1 before the running line of the thread 5. In this regard, as can be seen from FIG.
may be located in front of the line of symmetry 41,
Or, as can be seen from Figure 4, the plunger 18
may be located on the line of symmetry 41 and the thread 5 may be located behind this line of symmetry.

Embodiments of deflectable friction discs 1 according to the invention are described below.

According to FIG. 2, a deflectable friction disk 1 with a substantially immobile friction lining 3 is supported on a shaft 8 by means of a rubber-like elastic hub 21. It is mounted in Cardan style. Due to the axis-parallel acting force exerted on the clamping area 6, the friction lining 3 of the friction disk 1 can therefore be deflected out of a plane perpendicular to the axis 8. In other respects, the embodiment of FIG. 2 corresponds to the embodiment of FIG.

Friction disk 1 shown as an example from Fig. 3 onwards
ensures a torque transmission from the hub to the friction lining 3 in the circumferential direction, even though it is particularly well movable in the axial direction relative to the shaft. To this end, according to the invention, the friction disk 1 consists of a hub 20 and a friction ring with a friction lining 3, said hub and friction ring being connected to each other by a flexible connecting section 22. This is illustrated in FIGS. 3 and 4 and especially in FIGS. 9 and 10. This provides a mechanical decoupling between the hub and the friction ring, which allows the required torque to be transmitted from the hub to the friction ring, while the friction ring is connected to the hub. Based on the flexible bond, it can be deformed while applying an appropriate pressure force until it comes into linear contact with the thread.

The embodiments of the friction disk 1 shown in FIGS. 5 to 8 differ primarily in the construction of the flexible coupling section 22. As shown in FIGS.

In short, this configuration serves to reduce the required axial force on the friction ring in order to bring it into linear contact with the thread.

In the embodiment shown in FIG. 5, the flexible coupling section 22 between the hub 20 of the deflectable friction disk 1 and the friction ring (friction lining 3) is produced as follows. That is, a pair of notches 23 and 25 are provided along two circles of different diameters in a disc made of a single elastic spring metal thin plate, respectively.
Each cut spans approximately 180°, and there is a pair of webs 2 between each pair of cuts 23 and 25 on the same circle.
4.26 remain. Both web pairs 24 and 26
are advantageously offset from each other by 90°. This allows the friction ring to be moved relative to the hub.

In the embodiment shown in FIG. 6, a plurality of semi-circular tongues 27 are provided as the flexible connecting section 22, which tongues are formed by hook-shaped notches 28 and have one end. Then, by web 29, hub 2
0 and at the other end to the friction ring by a web 30. This provides for a cardanic movement of the friction ring relative to the tension hub. In this case as well, it is advantageous to manufacture the disc from a single elastic sheet of metal and to provide the disc with the predetermined incisions 28.

In FIG. 7, the flexible coupling section 22 is formed by a web extending between the hub 20 and the friction ring, the length of which is advantageously greater than the width. These webs may be radial webs 34 (sector divisions), tangential or secant webs 35 (sector divisions), or alternatively hook-shaped webs 36
(sector division -
). When formed in the shape of a hook, each web 36 consists of two generally radial ends 29' and 30' and a portion 27' interposed between the ends and substantially concentric to the hub, with one of said ends The portion 29' is connected to the hub 20 and the other end 30' to the friction ring.
Although such a hook-shaped connecting web is extremely flexible, it has high torsional stiffness and reliably transmits torque.

In the embodiment of FIG. 8, the flexible coupling section 22 is again formed by a radial web 34. In the embodiment of FIG. In order to obtain the desired flexibility, only four thin webs 34 with a length to width ratio of 5:1 are provided.

It is also possible to form a flexible coupling section by connecting a friction ring made of elastically springy sheet metal to the hub by means of a flexible foil or diaphragm or the like and additionally by means of a web. You can also do it. In this case, primarily adhesive or vulcanized foils or diaphragms serve for torque transmission and for flexible connections;
The web serves to center the friction ring against the hub.

It should also be noted that in the present invention, the friction disks can also be manufactured not from sheet metal materials but from non-metallic materials, in particular elastic plastics.

In the embodiment shown in FIGS. 11 to 13, 2
Parallel ring disk-shaped thin metal plates (Figs. 11 and 13) or parallel web-shaped thin metal plates (Fig. 1
2) to attach the shaft or hub to the friction lining 3.
This ensures that the friction ring deflects parallel to itself. These ring disk-shaped or web-shaped thin metal plates 42, 43 are fixed to each other at both ends to form one parallel spring 40. In the embodiment according to FIG. 13, the friction lining 3 is attached directly to the outer edge area of the disc-shaped leaf spring formed in this way. 11 and 12, the parallel springs 40 are connected to the hub 20 of the friction disk 1 and the friction ring 3.
forming a flexible connecting section 22 between the two.

The shape of the friction ring is deformed by deflecting (swinging) the friction ring in the axial direction with respect to the plane perpendicular to the axis 8 or the hub, but this deformation generally impedes the deflection and, in particular, reduces the tightening range. Preventing line contact of the friction ring to the thread at 6.

For this reason, another object of the invention is to make the deformation forces that have to be overcome for deflection as small as possible, so that even if the crimping force applied by the crimping device 17 (FIGS. 2 to 4) is small, the The aim is to be able to overcome deformation forces and, above all, to limit the crimping forces taking into account the threads.

7 and 8, the friction disk 1, in particular the friction ring 3, is constructed, i.e. it is divided into a plurality of elements which are only flexibly connected to each other. As a result, the deformation forces can be significantly reduced. In the embodiment of FIG. 7, the friction ring is divided into a plurality of radial sectors by a plurality of deformation cuts 38, 39. Of course, the density of the cuts determines the stiffness of the friction ring. These cuts are made from the outer circumferential side of the friction ring toward the inward deformation direction.
and/or can be provided radially outward from the inner circumferential side. These inward radial cuts 38 and outward radial cuts 39 are offset from each other in the circumferential direction. In any case, a closed annular portion 37 remains which connects the individual sectors to each other in the circumferential direction and ensures the rigidity of the friction ring in the circumferential direction. The division of the friction ring into a number of sectors by the notches 38, 39 allows each sector to be easily deflected relative to its fixed annular portion 37. The friction ring as a whole can therefore be easily twisted about a circular line extending within the closed annular portion 7.

In the embodiment shown in FIG. 8, the friction ring 3 is divided into a plurality of thin individual rings (four in this example), and these individual rings are connected to each other by radial webs, thereby reducing the deformation force. be made smaller. The radial webs, as can be seen from the drawing, are offset from one another, the width of the individual rings being approximately 2 mm and the gap width between the individual rings being only 1/10 mm.

These individual rings of the friction ring can also be easily moved and deflected relative to each other parallel to the axis. This means that the friction ring as a whole can be twisted about a circular line between the outer diameter and the inner diameter of the friction ring.

According to FIG. 4, a friction disk 1 having spring elasticity
is a friction ring 3 configured in a mitral shape.
With its convex side, the friction ring presses the thread 5 across the rigid friction disk 2 and against its friction lining. The curvature deformation of the friction ring 3 is dimensioned such that a virtually line contact occurs. Easier deformability is provided by the vine-like configuration. The friction disks can also be designed with a spherical or parabolic cross section. In FIG. 14, the entire friction disk having spring elasticity is constructed in a crochet shape. It should be noted that in this case the friction lining 3 of the friction ring can also be constructed in a straight line in the axial cross-section of the friction disk 1, so that the Line contact is guaranteed. In the embodiment shown in FIG.
It is also possible for the axes to be mounted parallel to each other, as shown in FIG. 1, or slightly intersecting each other, as shown in FIG.

As shown in FIGS. 1, 2, 9 and 10, the friction ring 3 in all embodiments is
It is coated with a friction material that has a suitable (often high) coefficient of friction against the yarn. In the embodiment of the friction ring shown in FIG. 7 or 8, the friction material is subjected to a vulcanization treatment to at least partially fill the notches between sectors or individual rings of the friction ring, thus Advantageously, a substantially smooth contact surface for the pressure plunger 18 also occurs on the back side.

Although the frictional action between said plunger 18 and the rear surface of the friction ring is reduced by suitable means, for example by static or dynamic air lubrication, the frictional circle nevertheless remains It is advantageous to arrange a sliding disk 33 on the back side of the plate 1 (No. 9
Figure and Figure 10). This sliding disc 33 must have good frictional properties against the plunger 18, in particular properties to cope with emergency situations.

Particularly if the friction ring is made of a flexible, spring-elastic material, such as sheet steel, the friction ring should be oriented in the direction of arrow 31 in FIG. Without movement, it may not be deflected from the plane perpendicular to the axis. This opposing movement is avoided in the embodiment of FIG. 10 by a disc-shaped plate 32, which is arranged on the rear side of the flexible friction disk 1 and is sufficiently rigid to absorb the opposing movement. have. The diameter of this disc-shaped plate 32 exceeds the inner diameter of the friction ring. As a result, the flexible friction disc, in particular the friction ring, contacts the rigid disk-like plate 32 in the opposite range of movement. The deflection from the above-mentioned vertical standard plane is therefore limited to the clamping area 6 of the thread 5, ie to the area of action of the crimping device 17. This measure serves to promote a stable and quiet rotation of the friction disc 1.

[Brief explanation of drawings]

Figures 1 and 2 are schematic diagrams, partially in section, of a false twisting machine having a friction disk mounted on the shaft in a Cardan style, and Figures 3 and 4 are yarn traveling paths. Figures 5, 6, 7 and 8 are schematic diagrams each showing a false twisting machine with a crimping device in front of the line; Figures 9 and 10 are diagrams showing how the friction disc is attached to the shaft, Figures 11, 12, and 13 are friction discs with parallel spring-like components. Diagrams showing each disk, 1st
FIG. 4 is a partial view of a false twisting machine equipped with a mitral-shaped friction disk, and FIGS. 15 and 16 are views showing the structure of the friction lining, respectively. 1... Deflectable friction disk, 2... Friction disk,
3, 4...Friction lining, 5...Thread, 6...Tightening range, 7...Lower overlap range,
8, 9...Shaft, 10...Bearing casing, 11...
... Rotating axis, 17 ... Crimping device, 18 ... Plunger, 19 ... Spring, 20, 21 ... Hub, 22
... Flexible connection section, 23 ... Notch pair, 24 ...
Web pair, 25... Incision pair, 26... Web pair, 27... Tongue, 28... Incision, 29,3
0... Web, 29', 30'... Web end, 3
1... Opposing movement direction, 32... Plate, 33...
...Sliding disk, 34...Radial web, 35...
Tangential web, 36... Hook-shaped web, 37...
Closed annular portion, 38... Inward radial cut, 39... Outward radial cut, 40... Parallel spring, 41... Line of symmetry, 42, 43... Parallel thin metal plates.

Claims (1)

[Claims] 1. Friction for applying false twist to synthetic fiber yarn in a textured machine while twisting the yarn by tightening the yarn between the moving member surface and the end surface of the rotating disk 1. The false twisting machine is such that the rotary disk is tilted toward the moving member surface with respect to the traveling path 15 of the yarn by means of a crimping device 17 for tightening the yarn. , the rotating disk 1 is
A type consisting of a hub 20 and a friction ring 3 concentric to the hub and having a friction lining, in which a flexible coupling section 22 is provided between the inner circumference of the friction ring 3 and the outer circumference of said hub 20. In this friction false twisting machine, the rotary disk 1 is made of a spring-elastic thin metal plate, and has a ring-shaped inner section forming a hub 20, a ring-shaped outer section forming a friction ring 3, and the hub. 20 and an intermediate region located between the friction ring 3, which creates a flexible connection section 22 consisting of a plurality of webs between the region of the hub 20 and the region of the friction ring 3. and the rigidity, number, and length of the webs are such that the friction ring 3 can be deflected relative to the hub 20 by a force parallel to the axis. A friction false twisting machine featuring: 2. The friction false twisting machine according to claim 1, wherein the webs 34, 36 extend in a spoke-like manner in the cleavage direction or the connection direction with respect to the hub 20. 3. The web 36 is bent in the shape of a double hook with a portion 27' substantially concentric with respect to the hub 20 and radial portions 29', 30'. friction false twisting machine. 4. The flexible coupling section 22 is formed by concentric notches 23, 25 of equal diameter and length in the hub 20;
2. A friction false twister according to claim 1, wherein one radial web 24, 26 each remains between adjacent ends of these cuts. 5. Two concentric pairs of notches 23 and 25 of different diameters and equal lengths are provided on the hub 20, respectively, and radial webs 24 and 26 remain between adjacent ends of each pair of notches, respectively. , the web 24 remaining between the ends of the pair of notches 23 provided on one circle.
5. The friction false twisting machine according to claim 4, wherein the web 26 is offset in the circumferential direction with respect to the web 26 remaining between the ends of the pair of notches 25 provided on the other circle. 6 The center angle of each cut including the web on one end
Friction false twisting machine according to claim 4 or 5, wherein the webs on adjacent circles extend over 180° and are offset from each other by 90°. 7 The flexible coupling section 22 is formed by a plurality of substantially circumferentially extending tongues 27, each tongue connecting at one end to the inner circumference of the friction ring 3 by a web 30 and at the other end. The friction false twister according to claim 1, wherein the friction false twister is connected to the outer periphery of the hub 20 by a web 29. 8. The friction ring 3 is made of a spring-elastic material, such as a sheet of spring steel, and is divided by a plurality of cuts into a plurality of sector sections, which are separated by a radial web. Friction false twisting machines according to any one of claims 1 to 7, which are connected to each other. 9 Sector divisions are formed by a plurality of inward radial cuts 38 starting from the outer periphery of the friction ring 3, and furthermore, a circumferentially closed annular portion 37 remains on the inner periphery of the friction ring 3. A friction false twisting machine according to claim 8. 10 Sector divisions are formed by a plurality of outward radial cuts 39 starting from the inner periphery of the friction ring 3, and furthermore, a circumferentially closed annular portion remains on the outer periphery of the friction ring 3. A friction false twisting machine according to claim 8. 11 sector divisions are formed by a plurality of outward radial cuts 39 starting from the inner circumference of the friction ring 3 and a plurality of inward radial cuts 38 starting from the outer circumference of the friction ring 3; 9. The friction false twisting machine according to claim 8, wherein a circumferentially closed annular portion 37 remains in a substantially central region of the friction ring 3. 12. The friction false twister of claim 11, wherein the plurality of outward radial incisions 39 are circumferentially evenly offset with respect to the plurality of inward radial incisions 38. 13 Patent, in which the friction ring 3 is divided by a plurality of concentric cuts into a plurality of separate rings, which are connected to each other by a plurality of circumferentially offset webs. A friction false twisting machine according to claim 8. 14 The friction ring 3 is coated on the yarn contact side with a friction lining such as polyurethane or rubber,
A friction false twisting machine according to any one of claims 1 to 13. 15. The friction lining 3 is vulcanized so as to at least partially fill the notch in the friction ring 3 and/or the notch between the friction ring and the hub 20. The friction false twisting machine according to item 14. 16. Any one of claims 1 to 15, wherein the rotating disk 1 is made of a spring-elastic thin metal plate such as a thin steel plate with a thickness of 0.1 to 0.5 mm. Friction false twisting machine as described. 17 The friction disk 1 is formed in the area of the friction ring 3 as a spherical part, a parabolic part or a similar rotating body part so that the thread is tightened on the convex side, and the radius of curvature of the thread contact area is such that the thread is A friction false twister according to any one of claims 1 to 16, which has a size that ensures line contact.