EP2674519A2 - Textile machine with a large number of work positions - Google Patents

Abstract

The machine has belt pressure rollers (21) movably mounted in a region of double-twisting spindles (5). A compensation unit (24) i.e. pneumatic cylinder, is set on tangential belts (20). The pressure rollers are arranged around a pivotal axis in an oscillating manner. The compensation unit is attached to an adjustable compressed air feed circuit device that is arranged over a central power supply. A center arrangement of the belt pressure rollers is provided in spacing sections. A pneumatic controllable directional valve (50) is connected to the compensation unit.

Description

The present invention relates to a textile machine with a plurality of jobs according to the preamble of claim 1.

In the textile industry, multi-point textile machines, such as double-twisting or cabling machines, ring spinning machines, open-end rotor spinning machines, etc. have long been known and various embodiments of such textile machines in numerous patents described in relative detail.

Such multi-point textile machines generally have a plurality of identical jobs, which are arranged side by side on both sides of the machine longitudinal axis and the working organs are often driven jointly by machine-length, continuous Endloszugmittel together.

In the case of double-twisting or cabling machines, the individual workstations are each equipped, for example, with a freely rotatable double-twisting spindle, with a machine-length, circumferential tangential belt being used as the drive means for the numerous double-twisting spindles of these textile machines, arranged at one end of the textile machine via the drive wheel of a machine end side Main drive runs and is guided at the other end of the textile machine via a guide wheel.
In order to ensure a secure frictional entrainment of the whorl of the double twisting spindles through the tangential during twisting operation, so-called Riemenandruckrollen are also installed, which ensure that the tangential belt is applied with a sufficiently high contact pressure or with a sufficient wrap angle to the whorls.

The described drive arrangement has proven itself in practice, in particular in connection with double twisting machines or cabling machines as well as ring spinning machines, but has the disadvantage that in such a drive arrangement energy is always consumed uselessly if no yarn is produced at a workstation takes place, that is, when at a job, although there is a yarn break or a similar event, the associated double-twisting spindle or spinning spindle is further driven.

Various suggestions have been made in the past on how to reduce this unnecessary energy consumption.
It has already been proposed, for example, to equip the workstations of such multiple-purpose textile machines either with a so-called swivel spindle arrangement, or to install a belt release roller in the region of the spindle of the workstation so that it can lift the tangential belt from the drive whorl of the affected spindle, if necessary.

Jobs with a swivel spindle assembly, that is, jobs with a spindle which is designed and arranged so that, if necessary, for example in a yarn breakage, the drive whirler of the spindle can be swung out of the path of the tangential, are for example by the CH-PS 510 753 , the DE-GM 75 29 164 and the DE-PS 24 52 939 known.

In the CH-PS 510 753 a swivel spindle assembly is described, in which a rotatably mounted on a pivot pin, which is fixedly fixed to the spindle bank of a multi-purpose textile machine, a manually adjustable pivot bearing arm is arranged, which in turn has a receptacle for freely rotatable mounting a spindle equipped with a drive whorl.
The pivot bearing arm is also provided with a locking device, which allows a secure positioning of the pivot arm and thus the Antriebswirtels the spindle in two end positions. That is, in the first end position, the drive whirler of the spindle bears against the tangential belt with a sufficiently high contact pressure, while in the second end position the drive whirler is positioned at a distance from the tangential belt.

The DE-GM 75 29 164 describes a pivoting spindle assembly in which in a bearing bore of the spindle spindle rotatably a sleeve is arranged, which is a for

Has center axis of the sleeve eccentrically arranged bore for receiving the bearing means of a double twisting spindle.
The sleeve, which is acted upon by a spring element in the sense of "pivoting into an inoperative position", is held by an arresting device in an operating position in which the drive whorl of the double-twisting spindle rests against an associated circumferential tangential belt.
The locking device is in turn connected via a Bowden cable mechanically to a yarn feeler, which ensures that the locking device is released in the event of a yarn breakage, with the result that the sleeve is rotated by the spring element in the inoperative position and thereby the drive whorl of the double twisting spindle out of contact comes with the tangential belt.
In this rotary movement of the sleeve also a braking device is activated, which brakes the double twisting spindle to a standstill.

A comparable swivel spindle assembly is also by the DE-PS 24 52 939 known. In this swivel spindle assembly, a yarn feeler actuates an electromagnetic switching pulse generator in the event of yarn breakage, the switching pulse then ensures that both the package and the double twisting spindle are stopped. That is, in the event of a yarn breakage of the drive whorl of the double twisting spindle is positioned spaced from the rotating tangential belt. Also in the swivel spindle assembly according to DE-PS 24 52 939 At the same time, the double twisting spindle is simultaneously decelerated to standstill.

For example, devices with special belt take-off rollers are known in the art DE-AS 1 239 966 or in the DE 195 49 163 C1 described in relative detail.
The DE-AS 1 239 966 describes a twisting machine with jobs whose spindles, as usual, are driven by a rotating machine-tangential belt. In the area of the spindles is also limited rotatably mounted, each a holder mounted, which is equipped with at least one Riemenabheberolle.

If necessary, the holder and thus a Riemenabheberolle, initiated by an associated thread monitor, can be rotated by a few degrees so that the Riemenabheberolle lifts the Tangentialriemen from Antriebswirtel the spindle and thus the tangential belt has no contact with the drive whorl of the spindle.

During the screwing of the holder, a spindle brake is simultaneously actuated electromagnetically, which brakes the spindle to a standstill.

In the DE 195 49 163 C1 Also, a workstation of a multi-purpose textile machine is described, which has a spindle drivable by a tangential belt.
In this textile machine, in addition to the spindle, in each case a pivot lever is mounted on the spindle bench, which is equipped at the end with a Riemenabheberolle and has an engageable to the Antriebswirtel the spindle brake device.
The pivoting lever, which is biased by a spring during the twisting operation, in an operative position in which the Riemenabheberolle not abutting the tangential tangential belt can be pivoted in the event of yarn breakage by means of a pneumatic cylinder so that the Riemenabheberolle the rotating tangential belt out of contact with the Antriebswirtel brings, wherein the spindle is simultaneously braked by the braking device to a standstill.

However, the devices described above all have the disadvantage that in the case of a yarn breakage, either the drive whorl of the spindle is pivoted away from the tangential belt, resulting in a reduction of the belt tension of the tangential belt and thus to a deterioration of the run of the multi-point textile machine and thus to quality losses in the yarn produced Threading leads, or that in the event of a yarn breakage of the tangential belt is charged by the use of a Riemenabheberolle with an additional belt tension, which leads to an increased energy consumption of the textile machine and to an increased bearing load.

Based on the aforementioned prior art, the present invention seeks to develop a textile machine, which does not have the known, not yet solved deficiencies, that is, in which it is ensured that in connection with a yarn break at a job neither the running behavior yet the energy consumption of the multi-point textile machine is adversely affected.

This object is achieved by a double twisting or cabling machine having the features described in claim 1.

Advantageous embodiments of the invention are the subject of the dependent claims.

The embodiment of the invention has the particular advantage that belt tension changes, especially belt tension changes, as previously unavoidable in connection with a thread break when the whorl taken out of the path of the tangential or the Tangentialriemen was lifted from the whorl, are now automatically compensated immediately.
That is, the movably mounted Riemenandruckrollen, each applied by a compensation unit to the tangential, respond immediately to any kind of change of the belt tension such that the operational default path of the tangential is corrected so that in all production conditions of the double twisting spindles always a largely constant torque is transmitted to the double twisting spindles.
That is to say, the belt pressure rollers mounted according to the invention ensure a proper operation of a textile machine with a plurality of workstations during the entire twisting operation, in particular with regard to the running behavior of the tangential belt and the energy consumption of the drive.

Advantageously, means are provided which detect a variable representing the belt tension of the tangential belt and the compensation units can be acted upon as a function of this variable. That is, there is a control unit which adjusts the belt tension depending on the detected amount, and thus, even if the whorl of a double-twisting machine comes out of contact with the Tangnetialriemen, the belt tension remains constant. At a constant belt tension, the torque acting on the twin-twisting spindles in contact with the tangential belt remains constant.

According to claim 3, it is provided in an advantageous embodiment that the compensation unit is designed as a pneumatic cylinder, which is preferably permanently exposed to compressed air.

The use of a pneumatic cylinder can be implemented in a relatively simple manner, a reliable compensation unit, which also, since such pneumatic cylinders are usually large-scale components, is still inexpensive.

As described in claim 4, it is also provided in an advantageous embodiment that the Riemenandruckrollen are each mounted oscillating about a pivot axis. The Riemenandruckrollen are permanently acted upon in each case by a first pneumatic cylinder and are at a specifiable contact pressure on the tangential belt. Such storage and control of Riemenandruckrollen is straightforward and reliable to produce, that is, the necessary to install the Riemenandruckrollen invention expenses are within reasonable limits.

As described in claims 5 and 6, it is furthermore provided that the pneumatic cylinders forming the compensation units are each connected to a compressed air supply device of the textile machine and that the air pressure in the compressed air supply device can be set in a defined manner via a central energy supply.
Such a design allows in a simple manner accurate adjustment and, if necessary, rapid correction of applied by the Riemenandruckrollen on the tangential contact pressure, through which the belt tension and thus the on the double twisting spindles to be transmitted torque is adjustable. In practice, this means that the operational outlay which is necessary in order to always keep the torque to be transmitted by the tangential belt to the double twisting spindles of a multi-purpose textile machine at an optimum level is low.

According to claim 7, it is provided in a further advantageous embodiment that the pressure prevailing in the compressed air supply device air pressure, depending on the power consumption of the drive for the tangential, defined adjustable. This means that during the twisting operation, the power consumption of the electric motor drive of the tangential belt is constantly monitored and at a power consumption of the drive that is present during normal operation Power consumption exceeds a predefinable limit, which is usually an indication of an incorrect belt tension of the tangential, immediately the air pressure in the compressed air supply device of the textile machine is readjusted. This means that the air pressure in the compressed air supply device of the textile machine, depending on the position, either increased or decreased and thus the contact pressure of Riemenandruckrollen is corrected to the tangential.

Another alternative possibility for optimizing the belt tension of the tangential belt or the torque to be transmitted is described in claim 8, where it is stated that sensor devices are arranged in the region of the empty and / or the load side of the tangential belt, each of which rests on the belt edges Monitor belt tension. If necessary, the belt tension determined by the sensor devices can be readjusted by appropriate adaptation of the air pressure in the compressed air supply device. Also by the use of such sensor devices, it is possible in a relatively simple manner to optimally adapt the belt tension of the tangential belt to the prevailing conditions.

In order to prevent a Riemenandruckrolle can be pivoted too strong by their associated pneumatic cylinder and it may then due to excessive deflection of the tangential belt to a troubled running behavior of the tangential, the maximum swing of oscillating Riemenandruckrolle is limited in each case by a stop (Anspr .9).
By such, preferably fixed stop is reliably prevented that the tangential belt can be deflected too much by a Riemenandruckrolle.

It is described in claim 9 that the belt pressure rollers according to the invention are used in a textile machine designed, for example, as a double-twisting or cabling machine, in which the double twisting spindles are each movably mounted on a spindle bank of the double-twisting or cabling machine. That is, the stored Riemenandruckrollen invention are used in multi-point textile machines in which the double twisting spindles, if necessary, each from an operating position in which the whorl of the double twisting spindle is applied with a predetermined contact pressure on the circumferential tangential, can be converted into a non-operating position in which the whorl of the double-twisting spindle is acted upon by a braking device.
In such trained double twisting spindles, which are often referred to as stop spindles, it comes inevitably to a change of position of the double twisting spindle to a displacement of the tangential and thus, if no appropriate measures are initiated, to a change in the pending belt tension on the tangential.
Such a negative change in the applied belt tension is reliably prevented by the use of the belt pressure rollers mounted according to the invention in that the belt pressure rollers are always tracked immediately and thus prevent the belt tension of the tangential belt from changing.

In an advantageous embodiment, it is provided that the double-twisting spindle is mounted freely rotatably in each case in a bearing device which can be positioned in a defined manner by means of an actuator, for example by means of a second pneumatic cylinder (Anspr.11). That is, the bearing device and thus the double-twisting spindle can be easily and safely positioned by means of such a pneumatic cylinder either in an operating position or when needed in a non-operating position, the transfer to the inoperative position, as will be explained in more detail below, for example by a signal a thread key is initiated.

In the inoperative position of the whorl of the double twisting spindle, as set forth in claim 12, preferably on a spring-loaded brake shoe a Spindelbremseinrichtung, on the one hand ensures that the double twisting spindle is braked quickly to a standstill, but on the other hand also ensures that the double twisting spindle in the Inoperative position is always reliably fixed against rotation.

As described in claim 13, it is provided in a further advantageous embodiment that the spring-loaded brake shoe of the spindle brake device is additionally activated by a foot brake lever.

Such a pedal lever brake allows the operator to shut down the double twisting spindle in case of need at any time, with the triggered by the operation of Fußhebelbremse thread break or initiated by the thread break signal of a thread scanner then ensures that the double twisting spindle is securely positioned in the inoperative position.

In a further advantageous embodiment, the textile machine, as described in claim 14, per machine section function fields of predetermined length, in each of which a predetermined number of double twisting spindles are arranged along with associated Riemenandruckrollen, wherein the installation position of the movably mounted Riemenandruckrollen each by the number of pro Function field installed double twisting spindles results. That is, the belt pressure rollers are each arranged so that the contact pressure of the tangential to the whorls of the numerous double twisting spindles of a function field is largely the same size, with possible pressure losses due to friction losses in the lines through ring lines and large cable cross-sections are compensated. For example, if an even number of twin twisting spindles are installed in a functional field, for example, ten double twisting spindles, the associated belt pressure rollers are preferably located midway between a pair of twin twisting spindles. That is, in such a functional field, the first belt pressure roller is positioned between the 1st and 2nd double-twisting mandrels, the second belt pressure roller is centered between the 3rd and 4th double-twisting mandrels, the third belt pressure roller is centered between the 5th and 6th double-twisting mandrels, etc ..
By means of such an arrangement of the belt pressure rollers, a uniform contact pressure or a uniform wrap angle of the tangential belt on all whorls of the double twisting spindles of a functional field can be reliably achieved in a relatively simple manner.
An even number of double twisting spindles has the advantage that a relatively large number of double twisting spindles can be positioned on a functional field of predetermined length, wherein the double twisting spindles in turn have a size which is suitable to advantageously process most of the feed bobbins customary in the textile industry.

However, if an odd number of double twisting spindles, for example nine double twisting spindles per functional field are installed in a functional field of a double twisting or cabling machine, it is advantageous for at least two of the five Riemenandruckrollen off-center in predetermined by the spindle division, adjacent distance spaces of three consecutive double twisting spindles to position.
Such an arrangement of Riemenandruckrollen can be realized even with an odd number of double twisting spindles in a relatively simple manner, a nearly uniform contact pressure of the tangential to the whorls of all double twisting spindles of a functional field.
The odd number of double twisting spindles also has the advantage that a number of double twisting spindles can be positioned on a functional field of predetermined length, which have an oversize. That is, in this way, nine "oversized" double twisting spindles can be installed on a functional field instead of ten "normal" size double twisting spindles. Such "oversized" double twisting spindles are suitable for processing also bobbins whose diameter significantly exceeds the diameter of "normal" feed bobbins.

As set forth in claim 14, it has proved to be particularly advantageous in such an eccentric arrangement of Riemenandruckrollen when working with distance sections, which have a size ratio which is 1/3 to 2/3.

As further described in claims 15 and 16, the textile machine designed as a double-twisting machine has for activating the further pneumatic cylinder which positions the double-twisting spindle and a third pneumatic cylinder with which the coil frame can be raised via a switching device, preferably works pneumatically.

The pneumatic switching device has a valve which can be activated in the event of a yarn break, for example by a signal of a yarn feeler.

This activated by the thread switch valve is also functionally connected to a first, pneumatically controllable directional valve, to which both the pneumatic cylinder for positioning the double twisting spindle, and a second pneumatically controllable directional control valve for actuating the pneumatic cylinder for lifting the coil frame are connected, that at Fracture the affected workstation is automatically stopped immediately.
That is, in the case of a signal from the thread feeler, the valve which is in blocking position during twisting operation is mechanically opened, that is, switched to passage, which triggers a switching operation in the sense of "valve open" at the first pneumatic switchable directional control valve, whereby the double twisting spindle at the bearing device activating attacking second pneumatic cylinder and the double twisting spindle is moved to the inoperative position. With a certain time delay then also the second pneumatic directional valve is switched to passage, with the result that the creel is raised.

Further details of the invention are the following explained with reference to the drawings embodiments.

Fig. 1

schematisch eine Seitenansicht einer Doppeldrahtzwirn- oder Kabliermaschine mit Arbeitsstellen, deren in einer Spindelbank gelagerten Doppeldrahtzwirnspindeln mittels eines maschinenlangen, durch Riemenandruckrollen beaufschlagten Tangentialriemen angetrieben sind,

Fig. 2

eine Untersicht der Spindelbank der Doppeldrahtzwirn- oder Kabliermaschine gemäß Fig.1, mit einer mittig zwischen zwei Doppeldrahtzwirnspindeln pendelnd gelagerten Riemenandruckrolle, wobei die Lagereinrichtungen für die Doppeldrahtzwirnspindeln als Stoppspindeleinrichtungen ausgebildet sind,

Fig. 3

eine perspektivische Ansicht der in Fig.2 dargestellten Teile der Textilmaschine, wobei die Stoppspindeleinrichtungen jeweils mit einem Fussbremshebel ausgestattet sind,

Fig. 4

eine schematische Draufsicht auf die Antriebseinrichtung einer Doppeldrahtzwirn- oder Kabliermaschine mit Maschinensektionen, die unterschiedlich ausgebildete Funktionsfelder aufweisen,

Fig. 5

in einem größeren Maßstab die Anordnung von pendelnd gelagerten Riemenandruckrollen in einem Funktionsfeld, das mit einer geraden Anzahl von Doppeldrahtzwirnspindeln ausgestattet ist,

Fig. 6

in einem größeren Maßstab die Anordnung von pendelnd gelagerten Riemenandruckrollen in einem Funktionsfeld, das mit einer ungeraden Anzahl von Doppeldrahtzwirnspindeln ausgestattet ist,

Fig. 7

eine pneumatische Schalteinrichtung zum Ansteuern der verschiedenen Pneumatikzylinder einer Arbeitsstelle einer Doppeldrahtzwirn- oder Kabliermaschine, mit Ventilschaltstellungen, wie sie während des Zwirnbetriebs gegeben sind,

Fig. 8

die pneumatische Schalteinrichtung gemäß Fig.8, mit Ventilschaltstellungen, wie sie sich nach einem Fadenbruch einstellen.

It shows:

Fig. 1

1 schematically shows a side view of a double-twisting or cabling machine with workstations, the double-twisting spindles of which are mounted in a spindle bank being driven by means of a machine-length tangential belt acted on by belt pressure rollers;

Fig. 2

a bottom view of the spindle bank of the double twisting or cabling according to Fig.1 with a belt pressure roller oscillating in the middle between two double twisting spindles, wherein the bearing devices for the double twisting spindles are designed as stop spindle devices,

Fig. 3

a perspective view of in Fig.2 shown parts of the textile machine, the stop spindle devices are each equipped with a foot brake lever,

Fig. 4

FIG. 2 is a schematic top view of the drive device of a double-wire twisting or cabling machine with machine sections having function fields of different design, FIG.

Fig. 5

on a larger scale, the arrangement of oscillating belt pressure rollers in a functional field equipped with an even number of double twisting spindles,

Fig. 6

on a larger scale, the arrangement of oscillating belt pressure rollers in a functional field equipped with an odd number of double twisting spindles,

Fig. 7

a pneumatic switching device for controlling the various pneumatic cylinders of a workstation of a double-twisting or cabling machine, with valve switching positions, as they are given during the twisting operation,

Fig. 8

the pneumatic switching device according to Figure 8 , with valve switching positions, as they adjust after a thread break.

The Fig. 1 schematically shows a side view of two work stations 2 designed as a two-ply twisting or cabling machine textile machine. 1
Such textile machines have, as is known, a plurality of such jobs 2, which are arranged side by side on both sides of the machine longitudinal axis.
The workstations 2 of such textile machines each have, inter alia, a double-twisting device 3 and a winding device 4. In the in the Fig.1 illustrated embodiment are mounted on a spindle rail 22 of the double twisting or cabling machine 1 double twisting spindles 5, with their whorls 25 abut a machine-length, circumferential tangential belt 20 and are driven by this frictionally.
The tangential belt 20 is in turn acted upon by a plurality of oscillating Riemenandruckrollen 21 and is in the operating state of the double twisting spindle 5 with a defined contact or contact pressure on the whorls 25 of the double twisting spindles 5 at.
That is, to the Riemenandruckrollen 21, as will be explained in more detail, compensation units 24, for example in the form of pneumatic cylinders, connected, which are constantly acted upon by a predetermined, constant pneumatic pressure and ensure that the Riemenandruckrollen 21 tangential belt 20 always with Apply a predetermined force and thereby keep the belt tension constant.

How out Fig.1 can be seen running in the operating state a deducted from the double twisting spindle 5, designed as a thread thread 6 via a thread guide 7 to the winding device 4, where the yarn 6 is wound into a cheese 10.
The thread guide 7 limits a resulting during the twisting operation in the field of double twisting device 3 thread balloon 8 with respect to its height.

The winding device 4 has a coil frame 12 for freely rotatable holding the cross-wound bobbin 10, wherein the coil frame 12 can be raised by means of a pneumatic cylinder 18 in case of need.
Furthermore, the winding device 4 has a fixed on a friction shaft 14 friction roller 13 for rotating the cheese 10 in the direction of rotation R and a Fadenchangiereinrichtung 11 for traversing the incoming thread 6. In the thread running direction F before the Fadenchangiereinrichtung 11 is a lead roller 9 is arranged in the Embodiment via an endless drawing means 19 to a machine-length drive shaft, in the present embodiment, to a friction shaft 14 of the Doppeldrahtzwirn- or cabling machine 1, is connected.

Between the thread guide 7 and the advance roller 9, a thread feeler 15 is also arranged, which monitors the proper course of the thread 6 during the twisting operation.

The yarn feeler 15 is connected via a signal line 16 with a pneumatic switching device 17, whose operation later on the basis of FIGS. 7 and 8th will be explained in more detail. That is, in the illustrated embodiment, the thread sensor 15 detected during the twisting operation possibly occurring yarn breaks and is in such a case, for example, via the signal line 16, an electrical signal i to a (in Fig.1 not shown) valve of the pneumatic switching device 17 from. The pneumatic switching device 17 then ensures inter alia that the pneumatic cylinder 26 (see Fig.2 ) in the sense of "stopping the double-twisting spindle" and the pneumatic cylinder 18 in terms of "swinging up the creel" are activated, which, inter alia, causes the cross-wound bobbin 10 is lifted from the rotating friction roller 13.

After removing a thread break, the pneumatic cylinder 18 and 26 are controlled by the pneumatic switching device 17 again so that the double twisting spindle 5 again transferred to its working position, that is, the whorl 25 of the affected double twisting spindle 5 again applied to the tangential 20 and the creel 12 is lowered again.
The cheese 10 is then back on the friction roller 13 and can be rotated by this again frictionally in the direction R.

The Fig.2 shows in bottom view a section of a spindle bank 22 of a double twisting or cabling 1 and some, the bank 22 slidably installed in the spindle bearing assemblies 23 for freely rotatable mounting a double twisting spindle 5. These in the area of each of the jobs 2A, 2B, 2C, etc. installed Bearing arrangements 23 can by means of a pneumatic cylinder 26 from an operating position I, which is shown in the present embodiment at the jobs 2A and 2C, and in which the whorl 25 of the double twisting spindle 5 rests on the rotating tangential belt 20 and this deflects something, transferred to an inoperative position II which is shown at station 2B.

As can be seen, in the inoperative position II, the bearing assembly 23 and thus the double-twisting spindle 5 by a measure a in the direction of the associated spindle brake device 27 relocated. That is, in the inoperative position II of the whorl 25 of the double-twisting spindle 5 abuts a supported by a spring element 30 brake shoe 28 and is braked by this in a standstill.
At the same time, the Riemenandruckrolle 21, which, arranged on a lever arm 33, oscillating about a pivot axis 29 and is acted upon by a working as a compensation unit pneumatic cylinder 24 with an adjustable, constant pressure in the direction of the tangential belt 20 ensures that the tangential belt 20 tracked and so that a belt tension loss is avoided.
A corresponding with the lever arm 33 fixed stop 31 limits the maximum pivoting of the Riemenandruckrolle 21st

The Figure 3 shows the spindle bench cutout according Fig.2 in a perspective view, also from below.
The workplaces 2A, 2B, 2C, etc. are each supplemented by a footbrake lever 32, which enables the operating personnel to immediately decelerate the double-twisting spindle 5 of a workstation 2 to standstill if necessary or to initiate the braking of the respective double-twisting spindle 5.

In Figure 4 is shown in a schematic plan view of an embodiment of the drive means of a Doppeldrahtzwirn- or cabling machine 1.
In the present exemplary embodiment, the double-twisting or cabling machine 1 has two machine sections 40, 41 each with a length L1 and two machine end frames 42, 43.
In the machine end frame 42, an electromotive drive 70 and an associated drive wheel 71 for the machine-length tangential belt 20 are arranged, inter alia, while the machine end frame 43 has a deflection wheel 72 for the tangential belt 20.
As indicated, sensor means 73, 74 may also be installed in the region of the belt room of the tangential belt 20 which, connected to a machine control (not shown), monitor the respective belt tension of the tangential belt 20.

The machine sections 40, 41 of the two-for-one twisting or cabling machine 1 are in each case subdivided into function fields 40A, 40B and 41A, 41B, wherein the individual function fields are each equipped with a multiplicity of double twisting spindles 5 respectively displaceably mounted as explained above.

In the exemplary embodiment, the functional fields 40A, 40B of the machine section 40 each have an even number of double-twisting spindles 5, for example, in each case ten double-twisting spindles 5.
By contrast, the functional fields 41A, 41B of the machine section 41 are each equipped with an odd number of double twisting spindles 5, for example with nine double twisting spindles 5.
How out Figure 4 further seen, the functional fields 40A, 40B; 41A, 41 B each also equipped with a plurality of oscillating belt pressure rollers 21.
In the function fields 40A, 40B, which, as explained above, each have an even number of double-twisting spindles 5, the Riemenandruckrollen 21, as for example also from Figure 5 can be seen, arranged so that they act on the tangential 20 each between a pair of twin twisting wire pair centered. That is, the distance of the Riemenandruckrollen 21 for whorl 25 of the 1st and 2nd, 3rd and 4, 5th and 6th etc. double twisting spindle 5 is each half a spindle pitch, so that the wrap angle to the whorls 25 of the double twisting spindle is the same.

As in Figure 5 1, the Riemenandruckrollen 21 deflect the tangential belt 20 in the regular operating state of the Zweikrahtzwirn- or Kabliermaschine 1 between a double twister pair by an angle β, with the result that at each whorl 25 of a double twisting spindles 5 of the function fields 40A, 40B a wrap angle α is given ,

In the function fields 41A, 41B, each having an odd number of double-twisting spindles 5, the Riemenandruckrollen 21, as for example also from Figure 6 can be seen, arranged so that two of the five belt pressure rollers 21 a functional field 41 A, 41 B arranged eccentrically between three adjacent Double twisting spindles 5 are positioned. That is, two of the Riemenandruckrollen 21 are each arranged at a distance 1/3 spindle pitch to 2/3 spindle pitch between two double twisting spindles 5.
Such an arrangement of the belt pressure rollers 21 also results in approximately the same wrap angles α, α ₁ , α _{2 of} the tangential belt 20 at the whorls concerned.

The Figure 7 shows an embodiment of one of each arranged in the region of a job 2 pneumatic switching devices 17 for actuating the various pneumatic cylinders 18, 24, 26th
As indicated, a pneumatic cylinder 24 having an associated (in Figure 7 not shown) Riemenandruckrolle 21 positively applied, connected via a connecting line 34 to a machine-length, pressurized main line 35 of a compressed air supply device, not shown.
In the area of each of the jobs 2 also one of the pneumatic switching devices 17 shown in dashed lines is arranged. The Figure 7 shows the switching device 17 in a switching state, which is given during the regular twisting operation.

The pneumatic switching device 17 is connected to a further machine-length main line 36 of the compressed air supply device of the double twisting wire or cabling machine 1. That is, to the main line 36 of the compressed air supply device, the compressed air level defined by a corresponding (not shown) control device is defined, via a pneumatic line 37 with its input side, a pneumatically switchable 3/2-way valve 50 is connected, which also equipped with a spring element 62 is.
From the pneumatic line 37 also branches off a pneumatic line 38 and 38A, wherein the input side of the pneumatic line 38, a throttle element 55 is arranged. The pneumatic line 38A is in turn connected to a pressurizable switching piston 51 of the 3/2-way valve 50. The pending during the twisting operation in the pneumatic line 38, 38A air pressure holds the 3/2-way valve 50 in the switching position 0, in which the 3/2-way valve 50 is closed.

To the pneumatic line 38 is further connected to its input side, a valve 52 which is acted upon by a spring element 53, during the twisting operation is also positioned in the switching position 0, in which the valve 52 is closed. The valve 52, which is connected on the output side to the atmosphere, in the exemplary embodiment has a switching piston 54, which, as in connection with the Fig.1 described, for example, via a signal line 16 with the yarn probe 15 of the job 2 is in communication.

The pneumatically switchable 3/2-way valve 50 is the output side via a pneumatic line 39, in which also a throttle element 44 is turned on, connected to a further, pneumatically switchable 3/2-way valve 56, which also held by a spring member 57 in the switching position is.
The pneumatically controllable switching piston 58 of the 3/2-way valve 56 is connected via a feed line 46, in which a further throttle point 45 is turned on and also a compressed air tank 47 is connected, also connected to the pneumatic line 39.

On the output side, the 3/2-way valve 56 is also connected via a compressed air line 48 to the pneumatic cylinder 18, which raises the coil frame 12 with appropriate pressurization.

In front of the orifice 44, a supply line 49 is connected to the pneumatic line 39, which is connected to the piston chamber 59 of a pneumatic cylinder 26 whose annular space 60 is permanently pneumatically connected via a pneumatic line 61 to the main line 36 of the compressed air supply device of the double twisting or cabling machine 1 ,

The pneumatic cylinder 26, which, as already explained above, if necessary, the bearing device 23 of the double twisting spindle 5 is in the illustrated switching state of the pneumatic switching device 17 in the region of its annular space 60 via the main line 36 and the pneumatic line 61 is pressurized and retracted, that is , the associated storage device 23 for the double-twisting spindle 5 is in working position.

In the illustrated switching state of the pneumatic switching device 17, in which the pneumatically controllable 3/2-way valves 50 and 56 and the valve 52, as explained above, each in the switching position 0, and the pneumatic cylinder 18 is compressed air and is by a in his annulus arranged spring element held in the retracted state. That is, in the illustrated switching state of the pneumatic switching device 17, the coil frame 12 and thus also the cross-wound bobbin 10 is lowered into the working position.

The pneumatic cylinder 24, which acts on the Riemenandruckrolle 21, however, is constantly acted upon on its piston chamber side with a predetermined pneumatic pressure, so that the Riemenandruckrolle 21 constantly tangential to the tangential belt 20 acts.

The Figure 8 shows how the pneumatic switching device 17 operates when it comes to one of the jobs 2 of the double twisting or cabling machine 1 to a yarn break, which is detected in each case by the yarn probe 15 of the affected job 2.

In such a case, the yarn probe 15 sends via the signal line 16 either a signal i to an electromagnetically operable 2/2-way valve 52 or the thread switch 15 mechanically actuates a correspondingly designed valve 52 of the pneumatic switching device 17. That is, the controlled valve 52 is brought against the force of the spring element 53 in the switching position 1, in which the valve 52, as shown, is on passage, that is, the output side is connected to the atmosphere.

In the switching position 1 of the valve 52 and the pneumatic lines 38, 38A are connected to the atmosphere, with the result that it comes in the pneumatic lines 38 and 38A to a pressure drop.

The input side of the pneumatic line 38 arranged throttle element 55 favors the pressure drop in the pneumatic lines 38 and 38A and allows the pneumatic control piston 51 of the 3/2-way valve 50 is suppressed by the valve's own spring element 62 and the 3/2-way valve 50 characterized in the switch position 1 is switched.

In the switching position 1 of the 3/2-way valve 50, the pneumatic line 39 of the pneumatic switching device 17 is then pneumatically connected via the pneumatic line 37 to the main line 36 of the compressed air supply device.
The now pending in the pneumatic line 39 air pressure now passes on the one hand via the supply line 49 into the piston chamber 59 of the pneumatic cylinder 26, which then extends and thereby displaced the bearing device 23 of the double twisting spindle 5 in an inoperative position II.
In addition, the pressure in the pneumatic line 39 pending air pressure passes with a certain, desired delay via the supply line 46 to the control piston 58 of the 3/2-way valve 56, which then switches to the switching position 1, in which also connected to the pneumatic cylinder 18 compressed air line 48 pressurized air is. The then extending pneumatic cylinder 18 raises the creel 12 and thus takes the cheese 10 from its associated friction roller thirteenth
The desired delay when switching the 3/2-way valve 56 results on the one hand by the input side of the supply line 46 arranged throttle element 45 and in particular by the use of a pneumatic tank 47, the necessary filling time ensures that the switching piston 58 of the 3/2-way valve 56th activated with a certain delay and thus the 3/2-way valve 56 is slightly delayed in the switching position 1 is switched.

After completion of the switching process described above, the double twisting spindle 5 of the affected job 2 is braked to a standstill and the associated cross-wound bobbin 10 lifted from its drive.
Since the pneumatic cylinder 24, which ensures a proper conditioning of the Riemenandruckrolle 21 on Tangentialriemen 20 is unaffected by the switching process described above, is constant in the pneumatic cylinder 24 of the predetermined pressure on the main line 35 of the compressed air supply air pressure available, thereby ensuring that belt tension changes the tangential 20, which could result from the displacement of a double twisting spindle 5, are compensated immediately.

Claims (18)

Textile machine with a plurality of jobs, each having a drivable by a tangential double twisting spindle and are equipped with a device that ensures that the whorl of the double twisting spindle out of contact with the tangential belt and the double twisting spindle is braked to a standstill,
characterized,
that in the region of the double twisting spindles (5) movably mounted belt tensioners (21) are arranged, which in each case by a compensation unit (24) at the tangential belts (20) are applied, wherein the compensating units (24) are permanently applied so that the tangential belts (20 ) transmits during the twisting operation, in all production states of the double twisting spindles (5), always a largely constant torque on the double twisting spindles (5). Textile machine according to claim 1, characterized in that there are means (70, 73, 74) which detect a variable representing the belt tension of the tangential belt (20), and the compensation units can be acted upon in dependence on this size. Textile machines according to claim 1 or 2, characterized in that the compensation unit (24) is designed as a pneumatic cylinder. Textile machine according to one of the preceding claims, characterized in that the Riemenandruckrollen (21) are each mounted oscillating about a pivot axis (29). Textile machine according to one of Claims 3 or 4, characterized in that the pneumatic cylinders forming the compensation unit (24) are connected to a compressed air supply device of the textile machine (1). Textile machine according to claim 5, characterized in that defined by a central power supply of the air pressure in the compressed air supply device is adjustable. Textile machine according to claim 6, characterized in that in the central compressed air supply device of the textile machine (1) required air pressure, depending on the measured power consumption of an electric motor drive (70) for the tangential (20) is adjustable. Textile machine according to claim 6, characterized in that in the central compressed air supply device of the textile machine (1) required air pressure, by means of sensor means (73, 74) can be determined which, in the region of the empty and / or the load strand of the tangential (20) each detecting the present belt tension. Textile machine according to one of claims 4 to 8, characterized in that the maximum pivoting of the oscillating belt pressure rollers (21) mounted in each case by a stop (31) is limited. Textile machine according to one of the preceding claims, characterized in that the double twisting spindles (5) in each case movably mounted on a spindle bank (22) of a textile machine (1) designed as a double twisting or cabling machine and from an operating position (I), in which the whorl (25 ) of the double twisting spindle (5) with a predetermined contact pressure on the rotating tangential belt (20), into an inoperative position (II) can be transferred, in which the whorl (25) of the double twisting spindle (5) by a spindle brake device (27) is acted upon. Textile machine according to claim 10, characterized in that the double-twisting spindle (3) is freely rotatably mounted in a bearing device (23) which can be positioned in a defined manner by means of an actuator, for example by means of a further pneumatic cylinder (26). Textile machine according to claim 10, characterized in that the spindle brake device (27) has a spring-loaded brake shoe (28) against which the whorl (25) of the double-twisting spindle (5) rests in the inoperative position (II). Textile machine according to claim 12, characterized in that the spring-mounted brake shoe (28) is part of a spindle brake device (27), which is additionally activated by a foot brake lever (32). Textile machine according to one of the preceding claims, characterized in that per machine section (40, 41) function fields (40a, 40B, 41A, 41B) of predeterminable length (L1) are present in which a predetermined number of double twisting spindles (5) together with associated Belt pressure rollers are arranged, and that with an even number of double twisting spindles (5) per function field (40A, 40B) the Riemenandruckrollen (21) each centrally between the 1st and 2nd, 3rd and 4th, 5th and 6th, etc Double twisting spindle (5) are arranged. Textile machine according to one of the preceding claims, characterized in that per machine section (40, 41) function fields (40a, 40B, 41A, 41B) of predeterminable length (L1) are present in which a predetermined number of double twisting spindles (5) together with associated Belt pressure rollers are arranged, and that at an odd number of double twisting spindles (5) per functional field (41 A, 41 B) at least two of the belt pressure rollers (21) are positioned off-center in predetermined by the spindle division, adjacent spaces of three consecutive double twisting spindles (5). Textile machine according to claim 15, characterized in that the eccentric arrangement of the belt pressure rollers (21) takes place in distance sections of 1/3 to 2/3. Textile machine according to one of claims 10 to 16, characterized in that for activating the further pneumatic cylinder (26) which positions the bearing device (23) of the double-twisting spindle (5) and for activating a third pneumatic cylinder (18) comprising a coil frame (12 ), a switching device (17) is provided which has a valve (52) which can be activated by a signal (i) of a yarn feeler (15) during a yarn breakage. Textile machine according to claim 17, characterized in that the valve (52) is functionally connected to a first, pneumatically controllable directional control valve (50), to which both the further pneumatic cylinder (26) for positioning the bearing device (23) of the double-twisting spindle (5), as well as, via a second pneumatically controllable directional control valve (56), the third pneumatic cylinder (18) for lifting the coil frame (12) are connected.

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