EP1948855B1 - Ring spinning frame comprising drawing systems - Google Patents

Description

Technical area

The invention relates to a ring spinning machine with drafting systems, which have a plurality of draw rolls.

For example, with drafting systems of great length, with five hundred jobs or more, the problem arises that their drafting rollers twist differently under the torque applied to them and the different rotational resistance. From which length this problem occurs depends on various factors such as roller diameter, bearing friction, inhibition by pulled straps, etc. When running the drafting system, this different torsion does not adversely affect. Acceleration or deceleration of the drafting system, such as during start-up and during discharge, during which these different torsions can build up or break down, however, leads to distortion errors. Depending on whether the torsion of a draw roll to that of a pre- or a downstream draw roll leading or trailing, this leads to thinning or thick spots in the yarn, which can lead to quality losses or even yarn breaks.

State of the art

It is therefore known to prevent different torsions in the drafting rollers of a drafting system of great length or at least to reduce a harmless amount that at the end remote from the drafting gear end of the drafting rollers of the gear transmission of the drafting gear equal (auxiliary) gearbox is arranged by that the respective mutual angular positions of the drafting rollers are maintained even during start-up, at the outlet or at standstill of the drafting system. The torsions are therefore not canceled, but held in default ( DE 26 41 434 ).

In this case, of course, it must be ensured that a change in the draft conditions in the drafting main gear is made approximately in a change of the yarn number corresponding to the auxiliary gear. This not only represents additional work, but also a dangerous source of error, which can lead to damage to the drafting system, if this Change is not carried out in the same direction and if not fuses are installed against this.

It has therefore also been proposed not to use an auxiliary gear with gear transmission, but by auxiliary motors at the end of the drafting gear remote from the drafting rollers, are introduced by the torques in the draw rolls, the torsions of the draw rolls if not to prevent, then at least below critical values to keep. So is out of the DE 26 41 434 A1 a drafting system of great length for ring spinning machines known, in which the drafting mechanism, are driven by the drafting all drafting rollers, is arranged approximately in the longitudinal center of the drafting system. Each of the long drafting rollers is driven to reduce the torsion occurring at at least one of its free ends by a torque introducing auxiliary motor.

The arrangement of the drafting in the longitudinal region of the draw rolls, however, has the disadvantage that the sequence of division of the jobs is interrupted at this point. This not only complicates the structure of the ring spinning machine. It also requires particular measures, when devices are provided for automatically changing the roving bobbins and / or the cops, special measures, since automatic feeders for such changing devices must have an area with vacancies at these locations.

Even with the use of terminal coupling gear can be very long drafting with, for example, 750 and more jobs in the central region of the workstations torsional sagging of the drafting rollers occur that can cause at least distortion in the yarn produced.

From the DE 100 40 420 A1 For example, a drafting arrangement has become known in which at least one of the drafting sub-rollers is driven at more than two driving locations along its length. In this arrangement, expressly dispenses with a drafting main drive at the end of the drafting rollers, the drive of which is exclusively by the multiple individual drives. As drives are helical or helical gear or linear motors ( FIGS. 1 to 3 ) intended. It is obvious that the wheels (27, 29, 31) shown in the drafting system in a small mutual, determined by the processed fiber length distance space found. This is very expensive.

The invention was therefore based on the object to provide a device by means of which in a simple manner between the ends of very long drafting rollers whose torsion preventing or at least reducing torques can be initiated.

General description of the invention

Solutions according to the invention are specified in claims 1, 2 and 7.

Characterized in that long drafting both a arranged at one end drafting device main drive device, by which the drafting rollers the distortion-oriented speeds is pressed, and optionally associated with a plurality of distributed over the length of the drafting rollers stretch roller auxiliary drive devices, the inclination of the drafting rollers for twisting counteracted over its entire length. In this case, the drives of the draw roller auxiliary drive devices need not exert the drives of the drafting device main drive devices corresponding speeds on the draw rolls, which greatly simplifies their embodiment and their application of electrical energy.

A preferred embodiment provides that the drafting of a short base ring spinning machine, in which no torsion occurs in the drafting system, is provided with a drafting device main drive device, which covers the torque requirement of this drafting system. At each ring spinning machine, which has a greater length than the base ring spinning machine, the additional torque requirement for speed-accurate drive of the drafting rollers is covered by a corresponding number of drafting roller auxiliary drive devices.

The narrow design of the draw roller auxiliary drive devices or their transfer organs on the draw rolls allows them to be attacked between the jobs on the draw rolls, without the pitch of the jobs of the ring spinning machine would have to be increased or jobs would have to be eliminated. This also opens up the possibility of setting the draw roller auxiliary drive devices anywhere along the draw rolls and in any number and to introduce additional torque into the draw rolls and to reduce their torsion.

The drive motors of the drafting roller auxiliary drive devices can be designed as rotary field magnets, as speed-controlled or speed-controlled asynchronous motors or as synchronous motors or reluctance motors. In particular, rotary field magnets and variable-speed asynchronous motors offer the advantage that in many cases they do not require a function-dependent change in the application of feed energy.

Since the draw roller auxiliary drive devices can be easily inserted at any points in a drafting, they can be provided in any and each draw roll in different numbers. They can be equipped with low power, which accommodates their narrow design.

For the sake of uniformity, the gearboxes of the drafting roller auxiliary drive devices can be designed to be identical for all drafting rollers. However, since the speeds of the input roller and the output roller are usually very different, it may be advantageous to maintain at least for these two drafting rollers draw roller auxiliary drive devices with gearbox with different reduction ratios.

In particular, the center roller which has to move the straps, which has to overcome high resistance when sliding over the deflecting edges of the Riemchenkäfige, equipped with draw roller auxiliary drive devices. However, it is advisable to provide on all drafting rollers of a drafting system with draw roller auxiliary drive devices. The rotational speeds of the drafting rollers driven by these drafting roller auxiliary drive devices are then still determined by the drafting system main drive device.

With the derivation of the feed frequency of the drafting drive motor, the intention is to run the draw roller auxiliary drive devices on the arrival and departure of the drafting system drive speed up and down run. This avoids distortion errors during start-up and at the outlet of the drafting system.

In drafting systems, the drafting rollers are not driven by a gear train, but by separate, exactly speed-controlled (synchronous) motors, have a power supply device that feed these motors with the appropriate frequencies. In this case, the drive motors of the draw roller auxiliary drive devices are subjected to frequencies corresponding to or derived from the frequencies of the associated draw roller motors. Since in this case the exact, causing the delays speeds of the drafting rollers are determined by the synchronous drive motors of the drafting rollers, is sufficient in most cases the use of Asynchronous motors on the draw roller auxiliary drive devices to reduce their torsion by introducing torque sufficiently.

It is understood that the draw roller auxiliary drive devices may also be equipped with synchronous or reluctance motors.

For the drive of drafting systems electric motors from standard series are usually used, which have certain power levels. Since a suitable electric motor is rarely offered, usually the next stronger is used, but is more expensive and unfavorably runs only under partial load. Also in the present invention, it is obvious to provide uniform performances of the electric motors. Here, however, there are no problems in adapting the number of uniform drafting roller auxiliary drive devices very closely to the required total power input, so that their motors are loaded close to their rated power.

For practical reasons, it is advisable to equip all drafting rollers of a drafting system adjacent with drafting roller auxiliary drive devices. This simplifies their wiring. However, there is nothing wrong with providing a drafting roller which has higher torsion than others at a smaller distance and accordingly with a larger number of drafting roller auxiliary drive devices. In this way, different torsions of drafting rollers can be compensated for with the least possible number of draw roller auxiliary drive devices with optimally loaded drive motors.

Frequently, the draft roller and the center roller are driven by separate synchronous motors on drafting systems, while the input roller is driven by gear translation of the center roller, since the bias between input roller and center roller is rarely changed. In this case, the drive motors of the draw roller auxiliary drive devices of the output and center rollers could be acted upon by frequencies derived from the (master) frequencies of the master motor of the center roller.

Due to the proposed narrow design at least of the drive energy transmitted to the drafting rollers transmission elements of the drafting roller auxiliary drive devices, it is possible to attack this between two jobs on drafting rollers without having to increase the spindle pitch of the ring spinning machine or jobs have to be omitted.

This opens up the possibility of introducing additional torque into the draw rolls at any point along the draw rolls and preventing or at least reducing their torsion. In this case, according to the invention, the tendency of a drafting roller to torsion, i. to balance it at least approximately. This can be done by the number of draw rollers associated with a draw roller auxiliary drive devices, by the action of the draw roller auxiliary drive devices with electrical energy, in particular their feed frequency or supply voltage or by the transmitted torque.

The choice of supply frequency or supply voltage can also be adapted to the operating state of a draw roller: it can be temporarily increased during startup of a machine or higher at higher speeds.

Since the draw roller auxiliary drive devices can be easily inserted at any points and / or in any number in a drafting system, they can be equipped with low power, which accommodates their narrow design. They can also be executed uniformly - they can be used in larger numbers if the torque requirement is higher.

If under a support and loading arm of a drafting system no sufficient space for coupling a transfer member of a drafting roller auxiliary drive device should be present, it is proposed to arrange these between two adjacent support and loading arms associated upper roller pairs. A draw roller auxiliary drive device is thus preferably arranged between the second and third riffelfeld lying to the right or left of a punch.

If between two adjacent jobs of a drafting system no sufficient space for the coupling of a transfer member of a draw roller auxiliary drive device should be present, it is proposed to reduce the distance between two serviced by the same Oberwalzenzwilling jobs, thereby increasing the distance between the serviced by other Oberwalzenzwillinge jobs while maintaining the spindle pitch increased. This creates space for the coupling of the transmission members in this enlarged space.

The free allocation to drafting rollers also makes it possible, if several drafting rollers are to be provided with such drafting roller auxiliary drive devices, to insert them between staggered workstations of the drafting rollers.

The drafting roller auxiliary drive devices must be mounted so as to receive the reaction momentum of the transmitted energy. Advantageously, they are therefore fastened to the punches or the roller bearing carriage assigned to the punches. As a result, it is unnecessary that they must be readjusted when changing the roll distance.

In order to achieve staggered arrangement here, it is proposed to arrange the draw roller auxiliary drive devices on a punch alternately right and left.

The possible plurality of drafting roller auxiliary drive devices along the drafting rollers can also reduce the diameters of the drafting rollers, if desirable, without the risk of increased torsion with the adverse consequences thereof.

If the draw roller auxiliary drive devices have transfer members between a drive member and a draw roller, they may be housed in a closed housing for protection against runoff of the draw roller auxiliary drive devices and contamination of the machined material.

Since the speeds of the input roller and the output roller are usually very different, it may be advantageous to provide common draw rollers auxiliary drive devices with gearbox with different reduction ratios on the two drafting rollers at least for these two drafting rollers.

The stretch roller auxiliary drive devices may be used as drive motors in the form of synchronous motors, which may also be designed as reluctance motors, or of variable speed asynchronous motors.

In a stretch roller motor, maximizing the axial length of both the stator and rotor causes both components to fully occupy the clearance between two adjacent corrugated fields by eliminating bearings provided on either side of the stator and rotor or by making these bearings as narrow as possible form.

This is possible because the rotor is mounted on the draw roller and between stand and rotor no unilaterally radially directed forces occur.

Minimizing the outside diameter of the stand implies that it takes full advantage of the smallest pitch available for adjacent draw rolls. This is possible because the diameter of the draw roll roller carrying the draw roll motor is reduced in the region in which the runner is mounted on it. As a result, not only the electromotive components can be moved further inward, but also those of the stator. Since the inclination of the drafting roller for torsion by the stretched roller motors used is avoided or reduced.

In this maximization or minimization, care must be taken that the delivered torque of the drafting roller motor remains as large as possible.

By dispensing with own bearing of the rotor whose axial length can be increased because such, to be arranged in special end shields bearing axial length would claim. The waiver is made possible by the fact that the runner is mounted on the draw roll to which he is assigned and makes their already existing storage with use. This bearing is spaced from the rotor and connected to it only indirectly via the draw roll.

The drafting rollers in drafting systems have an extremely low impact for textile technology reasons. Out-of-roundness in the course of the drafting rollers would lead to periodic distortion errors and impair the quality of the yarn produced until it is useless. The straightening of the draw rolls to exact concentricity without impact represents a separate operation in their production.

By inserting projecting pins of the rotor into the draw roller sections adjoining the draw roller motor, an extremely precise, impact-free running of the rotor is achieved. Alternatively, one of the draw roll sections may comprise a cylindrical stud on which the runner may be secured. When a thread connects to this pin with which the draw roll section can be screwed into the subsequent draw roll section, the runner is clamped on this pin.

Also, the stator of the drafting roller motor preferably has no bearings. It is attached to a fixed component, which is a carrier of the drafting equipment, a carrier the carrying and loading arms or a strap turn bar can act. It is preferably a component which contains a bearing of the draw roll to which the draw roll motor is assigned. In particular, the stand can be arranged on a punch of the drafting system or on a roller carriage of one of the output roller upstream drafting rollers.

The interaction of the stator and rotor requires a precise axial position of the two motor parts to each other. To make this possible, the stand is adjustable to the runner and adjustable attached to the component.

For this purpose, a Einstelllehre is proposed in a further embodiment of the invention, by means of which the stator is aligned very precisely to the rotor and fastened in this position on the component provided for this purpose. Preferably, two identical setting gauges are provided, which are insertable from both end sides of the engine forth in the annular gap between the stator and rotor.

In order to prevent the ingress of dust and flight in a heavily loaded by these contaminants drafting into the interior of the engine, the annular gap between the stator and rotor can be provided with a seal.

If the motor is arranged at a greater distance from the punch or a roller carriage and, accordingly, its attachment has a large projection, the motor can be provided on one side with a support bearing. It does not have the task to store the engine, but only to prevent accidental unilateral loading of the stand comes into contact with the runner.

In an alternative embodiment bearings are arranged in the rotary gap between the stator and rotor, which can be made weak, since no radial or axial forces occur between the stator and rotor. This offers the advantage that the stand does not have to be fixed and does not need to be adjusted and can not touch the runner. The stand only has to be supported on a non-rotatable component in order to apply the reaction to the torque. This may be, for example, to the support bar of Unterriemchen-tension brackets.

Finally, it is possible to attach laterally to stand and runner thin metal shields that do not significantly increase the axial length of the components and in which directly on the draw roll supporting bearing can be arranged.

Specific description of the invention

• Fig. 1 die Draufsicht auf den Anfangsbereich eines Streckwerkes mit Streckwerks-Hauptantriebsvorrichtung und mit Streckwalzen-Hilfsantriebsvorrichtungen;
• Fig. 2 eine Darstellung wie in Fig. 1 mit Drehzahlsteuerung der Antriebe der Streckwalzen-Hilfsantriebsvorrichtungen;
• Fig. 3 eine Darstellung wie in Fig. 1 mit Hauptantrieb der Streckwalzen mittels Synchronmotoren.

In the drawing, embodiments of the invention are shown purely schematically. Show

• Fig. 1 the top view of the beginning of a drafting with drafting device main drive device and draw roller auxiliary drive devices;
• Fig. 2 a representation like in Fig. 1 speed control of the drives of the drafting roller auxiliary drive devices;
• Fig. 3 a representation like in Fig. 1 with main drive of the drafting rollers by means of synchronous motors.

In the FIGS. 1 to 3 The drawings show the starting areas of three drafting rollers A2, A3 and A4 from a drafting system A1, which extend even further to the right. They are stored in punches A5 at regular intervals. In the embodiments of the Figures 1 and 2 they are drivingly connected to one another in a form-locking manner at their left end by a drafting device main drive device A6 in the form of a change gear train A8 driven by an electric motor A7. The change-gear transmission gives the drafting rollers angular accuracy to the revolutions, in order to reach between the rollers the default draft stages.

The drive motor A7 is energized from the network A9. The grid also powers a power supply A10 which powers drive motors A11 of draw roller auxiliary drive devices A12. The draw roller auxiliary drive devices engage and transmit torque to transfer rollers A13 on the lower rollers A2, A3, A4. The power supply device 10 is connected via separate lines A14, A15, A16 to the drive motors A11, so that they can act on these with different supply voltage and / or supply frequency.

Since the rotational speeds of the drafting rollers A2, A3, A4 and their relationships with each other are determined exactly the gearbox A8, it is sufficient if the drafting roller auxiliary drive devices A12 exert only torque on the drafting rollers. In the simplest embodiment, therefore, they can be rotary field magnets which assist the rotational movement imparted to the drafting rollers by the gearbox A8 and thereby reduce the torsion of the rollers. Greater or lesser torque can be achieved by different supply voltage and / or supply frequency.

In the embodiment of the FIG. 2 are arranged on the drafting rollers A2, A3, A4 preferably in the vicinity of the gear train A8, where there is no torsion, the speed sensor A17, A18, A19, whose outputs are connected to the power supply device A10. In this case, it can act on the drive motors A11 of the draw roller auxiliary drive devices A12 speed-controlled, so that they drive the draw rolls at the intended speed.

In this embodiment, it is also illustrated that the population of the various drafting rollers A2, A3, A4 may be different with drafting roller auxiliary drive devices A12. It is believed that the torsion of the middle lower roll A3 is higher than that of the others, as it must tow the slips that are slidingly guided over deflections. It is therefore, for example, provided on every second punch A5 with a draw roller auxiliary drive devices A12, while the other bottom rollers, for example, only on every third punch such.

In the embodiment of the FIG. 3 the draw rolls A2, A3, A4 each have a synchronous motor A20, A21, A22 as drafting main drive device A6. The power supply device A10 feeds this synchronous motors with those supply frequencies, are driven by the drafting rollers exactly with the intended speeds. With these frequencies, the drive motors A11 of the drafting roller auxiliary drive devices A12 designed as synchronous motors are also acted upon here and driven synchronously.

Reference numeral list for Fig. 1 to 3

A1

drafting system

A2, A3, A4

bottom rollers

A5

punch

A6

Drawing frame main driving device

A7

drive motor

A8

gearing

A9

network

A10

Power supply means

A11

drive motors

A12

Drawing rollers auxiliary drive devices

A13

transmission members

A14, A15, A16

cables

• Fig. 4 die Draufsicht auf einen Abschnitt eines Streckwerkes;
• Fig. 5 die Vorderansicht des Streckwerkes der Fig. 4;
• Fig. 6 die Vorderansicht einer Variante eines Streckwerkes;
• Fig. 7 die Vorderansicht einer weiteren Variante eines Streckwerkes.

In the FIGS. 4 to 7 The drawing is a further embodiment of the invention shown schematically. Show

• Fig. 4 the top view of a portion of a drafting system;
• Fig. 5 the front view of the drafting of the Fig. 4 ;
• Fig. 6 the front view of a variant of a drafting system;
• Fig. 7 the front view of another variant of a drafting system.

In FIG. 4 are sections of three bottom rollers B1, B2 and B3 of a drafting B4 shown, which are mounted in a punch B5. To the right of the punch is a support and loading arm B6 recognizable in which three upper roller twins B7, B8 and B9 are mounted, which press on the lower rollers. To the left of the punch is another support and loading arm B6 recognizable, whose upper coil twins are however broken away. In the main drafting zone between the lower rollers B2 and B3 a Riemchen turn rail B10 is located.

How out FIG. 5 can be seen below the output roller pair B3 / B9 via an arm B11 of the drive motor B12 a draw roller auxiliary drive device B13 attached to the punch B5. The drive motor drives via a spur gear B14 designed as StirnradVorgelege transmission member B15, the other spur gear B16 sits on the lower roller B3. Thus, the transfer member engages a portion of the lower roller B3, which lies between the twin upper roller B9 of the left support and loading arm B6 and the twin top roller of the next support and load arm, not shown, left. This prevents the transmission member B15 from coming into contact with a support and loading arm B6.

The spur gear B14 / B16 of a draw roller auxiliary drive device B13 is advantageously accommodated in a dust-tight housing B17.

The draw roller auxiliary drive device B13 assigned to the middle roller pair B2 / B8 is fastened to the right of the punch B5 on the roller carriage assigned to this roller pair and engages the bottom roller B2 in addition to the twin top roller B8. Thereby, it is avoided that the transfer members B15 of the two draw roller auxiliary drive devices B13 associated with each other adjacent lower rollers interfere with each other when the roller pairs B2 / B8 and B3 / B9 are brought close to each other at a small distance.

The draw roller auxiliary drive device B13 assigned to the input roller pair B1 / B7 is again arranged to the left of the punch B5 on the roller carriage assigned to this roller pair. The arrangement on the roller carriage has the advantage that the draw roller auxiliary drive devices B13 migrate with an adjustment of the roll spacing and require no special adjustment.

The transfer members B15 of the draw roller auxiliary drive devices B13 are designed so narrow that they can engage between adjacent Riffelfeldern B18 a draw roller to this without a rifflange and thus a job of the drafting would have to be omitted.

Due to the fact that the drafting roller auxiliary drive devices B13 can be inserted as a result of their narrow construction between virtually any desired work stations of a drafting system, there is the advantage that they can be made small and with low power. A required performance can be achieved by appropriate number of pieces.

There is also the advantage that the draw roller auxiliary drive devices B13 to be attached to a lower roller B1, B2, B3 can be adjusted in their number of units to the tendency of the draw roller to torsion. There is no use of full-performance drafting roller auxiliary drive devices.

In some cases, the distance between two work stations of a drafting system B4 corresponding to the pitch T of the ring spinning machine is too small to allow engagement of the transfer member B15 of a drafting roller auxiliary drive device B13. In such cases, as can be FIG. 6 it can be seen that the distances between three working points of the drafting system are reduced on the one hand to a distance t ₂ and increased to a distance t ₁ . In the interval t _1, the draw rolls auxiliary driving device B13 may be mounted between the corrugating fields B18. The attack of the drafting roller auxiliary drive device B13 is advantageously carried out at the connection points of the roller sections. As can be seen from FIG. B6, not every connection point has to be equipped with an auxiliary drive device.

In this case, the pitch of the jobs of the ring spinning machine relative to the pitch T of their spindles B19 remain unchanged, it also eliminates in this case no job. One of the threads B20 runs slightly obliquely towards its yarn guide B21.

How out FIG. 7 As can be seen, the increase in the distance can be distributed over two adjacent Riffelfeldabstände. Here, the distance 3T of three rifling fields is divided into two reduced distances t ₄ and a more extended distance t ₃ , in which a wider draw roller auxiliary drive device B13 is arranged. Two threads B20 run obliquely to the thread guides B21.

Reference numeral list for Fig. 4 to 7

B1

bottom roll

B2

bottom roll

B3

bottom roll

B4

drafting system

B5

punch

B6

loading arm

B7

Top roller twin

B8

Top roller twin

B9

Top roller twin

B10

Strappy turning rail

B11

poor

B12

drive motor

B13

Drawing rollers auxiliary driving device

B14

spur gear

B15

transmission member

B16

spur gear

B17

casing

B18

corrugated box

B19

spindles

B20

threads

B21

thread guides

• Fig. 8 die Ansicht eines Abschnittes eines Streckwerkes mit in einen Walzenstrang eingefügtem, geschnittenen dargestellten Streckwalzenmotor;
• Fig. 9 eine Variante der Ausführungsform der Fig. 8;
• Fig. 10 eine weitere Variante des Streckwalzenmotors mit Lagern;
• Fig. 11 noch eine weitere Variante des Streckwalzenmotors mit Lagern;
• Fig. 12 eine Einzelheit der Streckwalzenmotoren;
• Fig. 13 eine Lehre zum zentrischen Einstellen der Ständers zum Läufer.

In the FIGS. 8 to 13 The drawing shows two further embodiments of the invention are shown schematically. Show it

• Fig. 8 the view of a section of a drafting system with inserted in a roll train, cut shown draw roller motor;
• Fig. 9 a variant of the embodiment of the Fig. 8 ;
• Fig. 10 Another variant of the drafting roller motor with bearings;
• Fig. 11 yet another variant of the drafting roller motor with bearings;
• Fig. 12 a detail of the draw roll motors;
• Fig. 13 a lesson for centric adjustment of the stand to the runner.

How out FIG. 8 Recognizable, the draw roller motor C1 is inserted between two rifling fields C2, C3 of two sections C4, C5 of a lower roller C6 of a drafting system. This can be any lower roller of a drafting system. The axial length L of the drafting roller motor is so small that the given pitch T of the work stations of the drafting system and the ring spinning machine need not be increased.

The drafting roller motor C1 has a rotor C7 and a stator C8. The runner C7 is mounted on the draw roller C6. This can - as in FIG. 8 indicated by the fact that the roller portion C4 has a cylindrical pin C9 with subsequent threaded pin C10, by means of which it can be screwed into a bore of the roller portion C5. The bush-shaped rotor then lies on the cylindrical pin C9 and is clamped between the roller sections C4, C5.

In FIG. 9 a solution is shown in which the drum-shaped rotor has on both sides of two retaining pins C11, by means of which it can be inserted or screwed non-positively into bores of the adjacent roller sections C4 and C5. As not shown in detail, the rotor C7 can also be divided in an axis-parallel plane and be placed and fastened on the area between two Riffelfeldern C2, C3.

The runner C7 is so long that its end faces abut directly on the subsequent Riffelfeldern C2, C3. The available space between the adjacent Riffelfeldern is thus maximally utilized by the torque-applying parts stator C8 and rotor C7.

In the embodiment of the FIG. 8 the stand C8 has no bearings. It has a tab C12, by means of which it is usually fastened via a spacer C13 indicated by only with their center lines C14 screws to a non-rotatable member C15 which is connected to a bearing C16 of the lower roller C6. As a rule, this involves the punch of the drafting system or roller carriages which are displaceable on this punch and which also contain bearings of drafting rollers. The connection with a roller carriage has the advantage that the connection of the stator to the component does not have to be readjusted when a draw roller is displaced when changing roller distances.

It is understood, however, that the stand can also be connected to another, stationary, non-rotatable component. For example, the drafting system can be provided with a separate holding device for the stands C8.

The draw roller motor C1 itself, as mentioned, does not have its own bearings. The traveler C7 is mounted on the rotary draw roll C6, the stand C8 is fixed to a component C15 which is advantageously in firm contact with a bearing C16 of the draw roll C6 associated with the draw roll motor. The draw rolls of ring spinning machines have such a small impact that even in this way a very narrow gap between the stator C8 and rotor C7 is possible and an accurate concentricity of the drafting roller motor is ensured.

However, it is necessary to set the stand C8 exactly axial to the rotor C7. This is an in FIG. 13 For example, illustrated setting gauge C17 provided. It has a handle C18 and on a circular arm C19 three offset by 120 °, the course of the gap C20 between stator 8C and rotor C7 corresponding, wedge-shaped tabs C21. These tabs will, as in FIG. 12 indicated, pressed in the direction of the arrow P in the gap C20 and thereby center the stand to the runner. Advantageously, two setting gauges are provided, whose tabs C21 can be inserted from both sides into the column C20. In the thus achieved coaxial position of the stator to the rotor former can be attached to the stationary or rotationally fixed component C15.

In particular, the cotton processing drafting systems are heavily burdened by short fibers and dust. So that this flight does not penetrate into the interior of the engine C1, seals C22 can be provided around the two gaps C20 between stator C8 and rotor C7. The seals are preferably formed as a felt ring and can lie in grooves C23 of the stator or the rotor.

The drafting roller motor C1 can not be arranged directly next to the punching element C15, since there is a corrugated field there. He can attack between the two by the first top roller twins C24 next to the punch operated jobs on a drafting roller C6 and sits on the short spacer C13. However, since he often intervenes in the area of the axes of the upper roller twins C24 or the Oberwalzentrag- and loading arm C25, he often has to be moved into an intermediate riffler field on. For this purpose, a long spacer C26 is required, which can project the drafting roller engine far. In these cases, a clearance bearing C27 may be provided between the stator C8 and the rotor C7, which prevents touching sensitive parts of the drafting roller motor in case of unintentional one-sided loading of the stator C8. The spacer bearing C27 is not used to support the rotor C7 in the stator or the stator 8 on the rotor, but only to comply with the distance or gap C20 between the stator and rotor.

In FIG. 9 the spacer bearing C27 is shown as a ball bearing. In view of the low rotational speeds of the drafting rollers and its only exceptional load, the distance bearing can also be designed as a sliding bearing. Due to its arrangement in the gap C20 between stator C8 and rotor C7, it requires no bearing plate and can even be kept so narrow that it does not extend the length of the engine significantly.

FIG. 10 shows an embodiment in which two bearings C28 are provided in the gap C20 between the rotatable with the draw roll C6 runners C7 and the non-rotatably supported stand C8. Since the forces occurring between rotor and stator are small, the bearings can be made narrow and accordingly reduce the achievable torque only slightly.

The stator C8 mounted on the rotor C7 must be supported on a non-rotatable component in order to apply the reaction force of the drafting roller motor C1. In FIG. 10 this is the handrail C29 of the strapping clamp C30. The tab C12 on the stand engages around the support bar like a fork. When displacing the draw roller C6, the tab C12 remains engaged with the support bar C29.

To FIG. 11 For example, the embodiment may be such that the stator C8 has narrow terminal sheet-shaped end shields C31 in which are also arranged narrow bearings C32 running on the drafting roller C6. In particular, on the slow-speed input roller and possibly also on the center roller bearings C32 be designed as a sliding bearing. The end shields C31 are so narrow that they do not reduce the electromotive forces between stator C8 and rotor C7. To minimize the diameter of the outer diameter of the stator 8, it may be provided to reduce the diameter of the cylindrical pin C9 on which the rotor C7 is mounted. As a result, the diameter of the drafting roller motor C1 is expanded to some extent inwardly, the components of the rotor slip inwards and those of the stator can also be expanded inwards. Thereby, the outer diameter of the stator 8 is kept at a minimum level and yet maximizes the torque output by the drafting roller motor C1.

The invention can be practiced with all types of electric motors suitable for driving drafting rollers: synchronous and reluctance motors, variable speed or non-speed controlled asynchronous motors, stepping motors, rotary solenoids. The feeding of their stand is done for speed adjustment, preferably with controlled frequency. In general, the stator includes field windings, the rotor permanent magnets, which are not shown in detail in the figures, rotor C7 and stator C8 are indicated in the figures only by hatching.

Reference numeral list for FIGS. 8 to 13

C1

Draw roll motor

C2

Riffelfeld a Unterwalze

C3

Riffelfeld a Unterwalze

C4

Under reel section

C5

Under reel section

C6

bottom roll

C7

Runner of the drafting roller motor

C8

Stand of the drafting roller motor

C9

cylindrical pin on the lower roller section

C10

Threaded pin on the lower roller section

C11

Retaining pin on the rotor 7

C12

Tab on the stand 8

C13

spacer

C14

centerlines

C15

stationary component

C16

Bearing of the lower roller 6

C17

Einstelllehre

C18

Handle

C19

circular arm

C20

Gap between rotor 7 and stator 8

C21

tabs

C22

Seal in the gap 20

C23

Groove for the seal 22

C24

Top rollers twin

C25

Oberwalzentrag- and load arm

C26

Long spacer

C27

Spacer bearing in the draw roller motor 1

C28

camp

C29

Handrail of strapping clamp

C30

Riemchenspannbügel

C31

end shields

C32

camp

Claims (19)

1. A ring spinning frame with drawing frames with a plurality of draft rollers, the top rollers of which comprise twin top rollers loaded by means of support and loading arms and whereby each drawing frame includes a plurality of drawing frame auxiliary drive units spaced apart at intervals characterised in that the interval (t1) between two adjacent work surfaces of the drawing frame arranged in a longitudinal direction along the drawing frame (B4), in which the drawing frame auxiliary drive units (B13) engages a bottom roller (B3), is increased such that the interval (t2) to the next adjacent work surface of the drawing frame is reduced such that the entire interval of the three adjacent work surfaces corresponds to twice the normal interval (T) of two of the work surfaces.
2. A ring spinning frame with drawing frames with a plurality of draft rollers, the top rollers of which comprise twin top rollers loaded by means of support and loading arms and whereby each drawing frame includes a plurality of drawing frame auxiliary drive units spaced apart at intervals characterised in that the interval (t3) between two adjacent work surfaces of the drawing frame arranged in a longitudinal direction along the drawing frame (B4), in which the drawing frame auxiliary drive units (B13) engages a bottom roller (B3), is increased such that the interval (t4) to the two adjacent work surface of the drawing frame is reduced such that the entire interval of the four adjacent work surfaces corresponds to three-times the normal interval (T) of two of the work surfaces.
3. A ring spinning frame according to claims 1 or 2, characterised in that the drawing frame auxiliary drive units (B13) engage between the work surfaces on drawing frames (B1, B2, B3) that are arranged in an offset manner in a longitudinal direction along the ring spinning frame.
4. A ring spinning frame according to one of claims 1 to 3 with support bearings supporting the drawing frames and drawing frame carriages, characterised in that the drawing frame auxiliary drive units (B13) are affixed to the support bearings (B5) and/or on the moveable drawing frame carriages in the support bearings.
5. A ring spinning frame according to of claim 4, characterised in that the drawing frames (B1/B2, B2/B3) adjacent to the drawing frame auxiliary drive units (B13) are arranged left and right on a support bearing (B5) and on the moveable drawing frame carriages in the support bearings.
6. A ring spinning frame according to one of claims 1 to 5, characterised in that the drawing frame auxiliary drive units (B13) and/or the transmission members (B15) are arranged on the drawing frames (B1, B2, B3) preferably in a dust-tight housing (B17).
7. A ring spinning frame with a drawing frame motor for drawing frames in the ring spinning frame with stators and rotors to be arranged on and between drawing frames, characterised in that the drawing frame motor is arranged between two adjacent riffle fields (C2, C3) of a drawing frame (C6) and at an interval to one adjacent drawing frame and that bearing plates are not used in that the rotor (C7) of the drawing frame motor (C1) is affixed directly to the drawing frame (C6) to which it is associated and the stator (C8) of the motor (C1) in affixed and/or supported by a non-rotating component (C15, C29) of the drawing frame.
8. A ring spinning frame according to claim 7, characterised in that the rotor (C7) of the drawing frame motor (C1) is affixed directly to the drawing frame (C6) to which it is associated and the drawing frame motor (C1) includes only a bearing (C27) that maintains the interval within the rotation gap (C20) between the stator (C8) and the rotor (C7) as a result of which contact between the stator and the rotor is prevented.
9. A ring spinning frame according to claim 7, characterised in that the rotor (C7) of the drawing frame motor (C1) is affixed directly to the drawing frame (C6) to which it is associated and the drawing frame motor (C1) includes a bearing (C28) in the gap (C20) between stator (C8) and rotor (C7) which supports the stator on the rotor and whereby the drawing frame motor is supported by a non-rotating component (C29) of the drawing frame.
10. A ring spinning frame according to claim 7, characterised in that the rotor (C7) of the drawing frame motor (C1) is affixed directly to the drawing frame (C6) to which it is associated and the drawing frame has a reduced diameter (d) in the area where the rotor is affixed to it.
11. A ring spinning frame according to claim 10, characterised in that a frame thread section (C4) of the drawing frame (C6) includes a cylindrical intake (C9) to fasten the rotor (C7) of the drawing frame motor (C1) between two riffle fields (C2, C3) and may be screwed into an adjoining frame section (C5) by means of threading (C10) located on the cylindrical intake.
12. A ring spinning frame according to claim 10, characterised in that the rotor (C7) of the drawing frame motor (C1) includes retaining pins (C11) protruding on both sides that may be inserted into frame thread sections (C4, C5) using adjoining drill holes.
13. A ring spinning frame according to claim 8, characterised in that the non-rotating component (C15) includes a bearing (C16) for the drawing frame (C6).
14. A ring spinning frame according to claim 9, characterised in that the non-rotating component is a punch (C15) of the drawing frame or is a frame carriage located in a punch.
15. A ring spinning frame according to claim 8, characterised in that the component is a rod (C29) that holds the bottom apron clamp (C30).
16. A ring spinning frame according to claim 8, characterised in that the component is a bottom apron tilting bar serves as the non-rotating component.
17. A ring spinning frame according to claim 7, characterised in that the rotor (C7) and the stator (C8) occupy as much of the clearance between the two adjacent riffle fields (C2, C3) of a drawing frame (C6) as possible.
18. A ring spinning frame according to claim 8, characterised in that the stator (C8) of the motor (C1) may be adjusted laterally and is moveable coaxially to the rotor on a component (C15) arranged on a bearing (C16) of the drawing frame (C6).
19. A ring spinning frame according to one or more of claims 7-18, characterised in that seals (C22) are arranged in the gaps (C20) between the stator (C8) and the rotor (C7) that prevent the entry of dust and debris into the interior of the motor (C1).

Images