DE2217369A1 - MULTIPLE TWISTED SPINDLE - Google Patents

Description

Specimen copy

May not be changed n Patentanwälte Dipl.-Ing. F. Weickmann, -.

Dipl.-Ing. H. Weicxmann, DJPL.-PHYS. Dr. K. FiNCKE CGO Dipl.-Ing. F. AAVeickmann, Dipl.-Ckem. B. Huber

8 MUNICH 86, DEN 2217369

POST BOX S60 820

MÖHLSTRASSE 22, CALL NUMBER 48 3921/22

<9S392I / 22>

Kamel G.m.b.H. Twisting machines, 44 Münster, Dahlweg 102

Multiple twisting spindle

The invention relates to a multiple wire twisting spindle, comprising a rotatably mounted at one end in a main bearing, connected to a rotary drive Spindle shaft and a bobbin carrier that is rotatably mounted on this spindle shaft and prevented from turning, the material to be twisted coming from at least one bobbin seated on the bobbin, Via a standing clamping or braking point through the coil body and into the end remote from the main bearing of the S!> indelschafts is introduced at the main bearing side End of the bobbin out of the spindle shaft and as a circumferential material path within a The surrounding jacket is guided back over the coil body into the> area of the spindle axis.

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Multiple-wire twisting spindles of this type are particularly widespread as double-wire twisting spindles.

From the German patent specification 902 946 a two-for-one twisting spindle is known in which the axis is arranged horizontally or at a small acute angle to the horizontal. With this well-known Arrangement, the coil carrier is already inhibited from turning with the spindle shaft in that an eccentrically arranged weight is connected to the coil carrier, so that the center of gravity of the system consisting of the coil carrier, coil and weight is eccentric. The focus is looking always take the lowest possible position, which prevents the coil carrier from rotating. This known arrangement has a perpendicular spindle axis compared to the most widespread arrangements the advantage of using a magnet system, as is the case with spindles with a vertical axis, to inhibit the bobbin against rotation is common, can be dispensed with.

From the German Offenlegungsschrift 1 930 207 a twisting machine is known in which the twisting spindles are arranged with a horizontal axis, in particular with regard to a low overall height of the overall machine, which allows even medium-sized operators to operate all of them in normal operation gripping parts from the ground without special tools. In this known arrangement a surrounding jacket enclosing the coil is also provided so that the circumferential Material route inevitably developed wind outside the machine for that on the machine does not noticeably disturb the operating personnel.

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From the German patent specification 1 268 031 it is Knows, with a two-for-one twisting spindle, rotate around the casing jacket with the rotating spindle shaft to leave, so that the on the inner circumferential surface of the surrounding jacket applying material to the inner circumferential surface of the surrounding jacket only executes that frictional relative movement that originates from the thread take-off, but no relative movement, that of the relative rotation of the rotating material path with respect to a stationary surrounding jacket according to the German Offenlegungsschrift 1 930 207 is to be expected.

In the arrangement according to German patent specification 1 268 031, in which the spindle shaft axis is perpendicular stands, however, the inhibition of the coil carrier from rotating with it causes difficulties insofar as the magnetic flux between the magnetic bodies of the magnetic system causing the inhibition not only the rotating ones Enclosing jacket must enforce, but also a surrounding jacket enclosing this, fixed housing which is provided around one of the circumferential surrounding jacket to avoid the development of wind and the effects of wind on the operating personnel. The order a rotating surrounding shell and a fixed housing between the magnets of the die Rotation of the coil carrier inhibiting magnet system inevitably leads to the effective rotation inhibition a particularly strong magnet system must be used, which takes up a lot of space and is expensive is.

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The invention is based on the object, the advantages of the known two-for-one twisting spindle !! to take advantage of However, avoid their disadvantages.

In order to achieve this object, the combination of the following features, which are known per se, is used according to the invention suggested:

a) The axis of the spindle is horizontal or inclined at a small acute angle to the horizontal arranged.

b) The surrounding jacket runs with the spindle shaft

c) The coil carrier is due to eccentric weight distribution prevented from turning with the spindle shaft.

The special effect of this combination of features is that the unavoidable difficulty of a two-for-one twisting spindle with a vertical axis in the formation of the magnetic system causing the rotation inhibition of the spool carrier, which is caused by the need for both a rotating ventilation casing and a stationary housing) -> ^for braking magnetically, simply avoided by braking through an eccentric center of gravity.

The circumferential matorial path can be used in the case of the invention Mehrfachdj ^ bt-Zv / irnspindel in a guide channel of the Unifas? ungsmanfc.? ls. Such Arrangement is from US Patent No. 3,007,299

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The guide channel of the surrounding jacket running in the axial direction can be connected to a radial one Connect the guide channel, which takes over the guidance of the material from the spindle shaft to the surrounding jacket.

To a wind action from the rotating surrounding jacket on the coil body and in particular on the Avoid material path that lies between the bobbin and the inlet in the spindle shaft, can between the surrounding jacket and the stationary bobbin radially within the circumferential thread path a fixed jacket can be arranged.

If the rotating material path runs within the rotating surrounding jacket in a guide channel, it can be advantageous to let this guide channel end in the axial direction in front of the end of the primary bearing remote from the main bearing for the following reasons the guide channel is only gradually detected by the air resistance that the standing air exerts on it outside the rotating surrounding jacket, because namely in the area of the rotating surrounding jacket the air is set in rotation and this rotating air vortex only moves axially from the outlet of the guide channel gradually degrades. On the other hand, there is the possibility of obtaining a helical course of the circumferential material path in the axial area of the rotating surrounding jacket lying outside the end of the guide channel, which has a balancing effect on ^{yarn tension fluctuations with respect to v.}

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The surrounding jacket with the spindle shaft is exposed to considerable centrifugal forces. It should be borne in mind that the spindle often has a number of revolutions of 10,000 revolutions / min, and more revolves and that the diameter of the rotating surrounding jacket can be up to 450 mm. These centrifugal forces are all the more to be charged as unavoidable imbalances of the rotating surrounding shell must be expected. As a result of this unfairness The centrifugal forces do not make themselves as pure tensile stresses acting in the circumferential direction of the surrounding jacket but noticeable as bending stresses, which can quickly lead to the destruction of the rotating jacket.

In order to reduce the stresses caused by the centrifugal forces of the rotating mass while keeping the rotating mass low To get a grip on the rotating surrounding jacket is proposed in a further development of the invention, that the surrounding jacket is made in a double-shell construction is under installation of connecting means between the two shells, which at least in the circumferential direction Can transfer shear forces from shell to shell. So important is this training in its application on the combination invention defined by the above-mentioned combination features a to c, it should be noted that the double-shell construction can be used regardless of which direction the spindle axis is occupies in the room and what type of anti-rotation device is used to lock the bobbin.

The connecting means between the two shells of the Surrounding jacket can be formed, for example, from a corrugated material, which in the corrugation crests with the is connected to both shells. The connection between

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the corrugated material and the shells can be achieved in particular by gluing. The gluing will preferred because it has the advantage over other types of connection that the two shells of the Umfassungsmantels are at least deformed. In addition, however, there is also welding of the corrugated material conceivable with the bowls.

Preferably, a corrugated material is arranged between the two shells, the direction of which the corrugation progresses in the direction of the axis. In this embodiment, namely, an optimal transmission of thrust is from Shell to shell ensured, which in turn is responsible for the flexural strength of the two-shell surrounding jacket. In addition, of course an arrangement is also conceivable in which the corrugation direction of the corrugated material is in the circumferential direction lies.

The two shells can be made of thin-walled sheet metal, according to any desired Production method; for example, the shells can be drawn or pressed from a sheet metal blank be or be formed from a Butze in the cold flow process.

The inside diameter of the surrounding jacket is usually between approx. 150 mm and approx. 420 mm. the The sheet metal thicknesses used are between 0.2 and 1.0 mm, preferably between 0.3 and 0.6 mm, the smaller wall thickness values being assigned to the smaller diameter values.

The distance between the individual shells is between 5 and 15 mm, with the smaller distance values here as well are assigned to the smaller diameter values. 309845/0 5 38

The two-shell design of the surrounding jacket allows the guide channel for the circumferential To accommodate material path between the shells of the surrounding jacket. Used as a lanyard between the two shells a corrugated material with a circumferential direction of corrugation, so you can, for example, the guide tube between the opposite Place the ends of the corrugated material designed as an open ring. But you can also simply use the guide tube Arrange in the apex area of a wave of the corrugated material.

It was indicated above that the guide tube could end in the axial direction in front of the end of the surrounding jacket. To the double-shell training the surrounding jacket and the placement of the guide tube between the two shells, this means that the radially inner shell and the thrust-transmitting connecting means in axial direction before the main bearing remote end of the radially outer shell ends so that the radially inwardly facing surface of the outer shell in its protruding area for the plant of the guide tube leaked material is available.

If the outer shell protrudes axially beyond the inner shell and the connecting means arranged between the two shells, a centering ring can be arranged at the end of the radially inner shell and the thrust-transmitting connecting means. This can also be a Zentrierunsring Unwuchtausgleichs- ^N "function can be transmitted, for example, the induced through the guide tube to compensate for unbalance.

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The unbalance compensation takes place, for example, in that material is removed in the centering ring through bores will. In addition, a material outlet eyelet at the end of the axially extending guide tube can be in the centering ring be trained.

A particularly useful, because simple and stable structure is obtained when the two shells each with one Shell bottom are executed and a spacer disk is arranged between the two shell bottoms, within which the radial guide channel adjoining the axial guide channel can run.

The shell bottom of the outer shell can be mounted on a carrier disk, which in turn is rotatable on the spindle shaft is mounted, be attached by means of an elastic damping layer; the damping layer takes over the damping of unavoidable vibrations caused by imbalances.

To the inevitable by the circumferential outer jacket to localize the generated wind and to protect the operating personnel from the effects of wind Veiter suggested that the circumferential surrounding jacket is surrounded by a stationary housing. This too The housing is expediently designed with a cylindrical cross-section.

When the material path rotating around the spindle shaft axis on a substantial part of their length in guide channels, namely first a radial and then an axial guide channel, is guided, so the storage length is omitted, the one on the so-called storage disk with conventional double-wire Zvirnspindeln is wound up and the compensation of

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Voltage fluctuations are used. In many cases it will Although the storage length of the material is sufficient, which is in a helical course to the over the end of the axial guide tube protruding rotating surrounding jacket applies. In other cases however, additional tension compensation will be desirable. This can in a further development of the invention be achieved that in the extension of the spindle shaft a fixed, leading to a thread brake Inlet pipe is arranged, which is telescopically displaceable in the axial direction against spring resistance. It is easy to see that this solution is particularly useful in conjunction with the other features of this invention, especially when there is no storage disk, this feature is on the other hand but it can be used with success anywhere and whenever stress peaks are detected on the material and these voltage peaks should be compensated.

The end of the surrounding jacket remote from the main bearing can pass through a material passage opening removable cover to be lockable. Such a lid that by no means provides a hermetic seal must deliver the interior of the surrounding jacket, forms the prerequisite for a development of the Invention, which is particularly important with regard to the horizontal position of the spindle shaft. As a result of the horizontal position of the spindle shaft, the main bearing must absorb a moment that is of the Dead weight of the system made up of the spindle shaft, bobbin carrier, material bobbin and surrounding jacket originates. In order to remove the main camp from this moment

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load, you can put a lid on the lid for the purpose of take off releasable support bearing device attack. For example, you can use the support bearing device run with a pivotable support arm, which carries the cover in a support bearing. To if present a support bearing device to avoid a geometric overdetermination, the main bearing can be elastic form. This can be done in such a way that when building the main bearing with two in the axial direction single bearings lying next to one another, at least the single bearing closer to the support bearing device is elastic, that is to say e.g. is arranged in a rubber-metal sleeve.

If the main bearing is arranged elastically, this means that the spindle shaft when the support bearing device is removed due to the weight of the spindle shaft, bobbin carrier, bobbin and outer casing one opposite assumes a position offset from the normal position. In order to prevent this, one can in many cases already need one Use the brake to stabilize the spindle shaft; this can be done in the same way that in training of the rotary drive with a spindle whorl arranged in a rotationally fixed manner on the spindle shaft and a tangentially above this Whorl running drive belt a shoe brake is provided for attack on the spindle whorl, which at Ineffective support bearing device takes over the stabilization of the spindle shaft.

The brake shoes of such a shoe brake can sit on actuating levers arranged like scissors; at These actuating levers can release cams or rollers, arranged for lifting the drive belt from the whorl be.

The accompanying figures explain the invention on the basis of exemplary embodiments. They represent:

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FIG. 1 shows a longitudinal section through a two-for-one twisting spindle according to the invention;

FIG. 2 shows a longitudinal section through the double-shell surrounding jacket removed from the spindle a line which corresponds to the line II-II of Figure 1;

FIG. 3 shows a view of the removed double-shell surrounding jacket in a viewing direction which corresponds to viewing direction III-III of FIG. 1;

FIG. 4 shows a longitudinal section through another embodiment of a two-for-one twisting spindle according to the invention;

FIG. 5 shows a shoe brake device for a two-for-one twisting spindle according to the invention in a first Operating position;

FIG. 5a shows a modification of the actuating lever according to FIG. 5;

6 shows the shoe brake device according to FIG. 5 in one second operating position;

FIG. 7 shows another embodiment of a shoe brake device;

FIG. 8 shows a first embodiment of a telescopically shortenable inlet pipe;

Figure 9 shows the telescopically shortenable inlet pipe according to FIG. 8 in a shortened position;

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Fig. 10 shows a second embodiment of the telescopic ■ shortenable inlet pipe;

FIG. 11 the inlet pipe according to FIG. 10 in a shortened form Position.

In Figure 1, a continuous rectangular profile support 10 of a spindle bench can be seen. A spindle shaft is mounted on this profile support 10 by means of a main bearing 12a, 12b. On the left end of the spindle shaft 14 in FIG. 1, a spindle whorl 16 is arranged, which is in frictional engagement with a tangential to it . passing drive belt 18 is. On the right end of the spindle shaft 14 in the figure, a coil carrier 22 is mounted by means of a coil carrier bearing 20a, 20b. This coil bobbin 22 is shaped conically on its outer surface and receives a bobbin 24 to $ which in turn carries a bobbin 26th

A carrier disk 28 is non-rotatably connected to the spindle shaft 14. On this carrier disk 28 is with the mediation of a damping layer 30 made of rubber-like or felt-like material, a double-shell Enclosing jacket 32 arranged. This double-shell Enclosing jacket 32 consists of an inner shell 34 and an outer shell 36. The inner shell v / eis an inner shell bottom 38, while the outer shell bottom the outer shell 36 is denoted by 40. Between the inner shell 34 and the outer shell 36, a corrugated cylinder 42 is arranged, the direction of wave propagation in the axial direction of the spindle arrangement lies. The corrugation crests 44 of the corrugated cylinder 42 are glued to the inner shell 34,

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while the apex 46 is glued to the outer shell 36 are. The bond is made shear-proof. In this way one of the outer shell 36 is the corrugated cylinder 42 and the inner shell 34 formed composite body of high flexural rigidity is created, in particular a bending stiffness about bending axes, parallel to the axis of the spindle arrangement.

Between the inner shell base 38 and the outer shell base 40, a spacer disk 48 is arranged, in which a radial channel 50 formed by an inserted tube runs. On the importance of this radial channel. will have to be entered. An axial channel 52 is formed between the inner shell 34 and the outer shell 36 in the area of an interruption in the corrugated jacket 42, the significance of which will also be discussed later. The inner jacket J> k ends in the axial direction before the end of the outer jacket 36. The corrugated cylinder 42 ends where the inner jacket 3 ^ ends. A centering ring 54 centers the end of the inner jacket 34 in the outer jacket 36 and there is an eyelet 56 which forms the end of the axial guide channel 52. The piece of the outer shell 36 protruding beyond the end of the inner shell 3 has a polished contact surface 58.

The spindle shaft 14 is hollow over part of its length and forms a spindle channel 60 which is connected to the radially inner end of the radial guide channel 50 connects. On the coil carrier 22 is a so-called Thread brake 60 put on. The actual thread brake sits in the thickened part 62 to which a Inlet pipe 64 connects.

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• a ···

Finally, an eccentric 66 is arranged on the coil carrier 22, which ensures that the heavy « point of the formed by the coil carrier 22, the coil sleeve 24 and the coil body and eccentric 66 System, which center of gravity is denoted by S, is below the axis, with the result that this The system always tries to stop even when the spindle shaft 14 is rotated. On the eccentric 66, a stationary jacket 68 is arranged.

The device described so far works as follows:

The spindle shaft 14 is driven by the drive belt 18 running over the whorl <16. The carrier disk and the surrounding jacket 32 rotate with the spindle shaft 14. The system, which is rotatably mounted on the spindle shaft 14 and consists of the bobbin carrier 22, bobbin tube 24, bobbin 26, eccentric 66, jacket 68 and thread brake 62, is stationary within the surrounding jacket.

The thread material wound to form the bobbin 26 is drawn off from the stationary bobbin 26 and runs into the inlet pipe 64. It then runs through the actual thread brake 62, which counteracts the thread Turning. The formation of such a thread brake is for example in the German patent application P 20 50 490 .. 9 described by the applicant. From the thread brake 62, the thread runs through the spindle channel 60, the radial guide channel 50 and the axial guide channel 52 in order to finally exit the axial guide channel through the eyelet 56. After exiting the eyelet 56, the thread is subject to air resistance over a short distance. The one

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occurs in the area of air resistance but is a gradual one, which is due to the fact that on the inside of the outer shell 32 in the region of the polished surface 58 there is an air vortex which extends to the end of the outer shell only gradually decreases. From the eyelet 56, the thread runs through a thread guide eyelet 70 to a non shown delivery plant and a take-up reel.

The stretch, aireiche the thread between the eyelet 56 and the thread guide eyelet 70 has to pass freely through is relatively short, since the thread is on the largest one Part of its rotating path through the radial thread guide tube 50 and the axial thread guide tube 52 is led. Since the force acting on the thread as a result of the air resistance depends on the length of the the thread length exposed to the air resistance is dependent, can with a relatively small, i. gentle thread tension.

The fixed jacket 68 prevents the vortex of air generated by the rotation of the surrounding jacket 352 acts on the bobbin and on the thread engaged in unwinding from the bobbin. That the covering coat 32 enclosing, fixed to the carrier 10 fixed housing 72 prevents the through the circumferential surrounding jacket 32 formed vortices as Makes wind noticeable to the operating personnel standing in front of the machine.

The surrounding jacket 132 shown in FIG. 2, like that of the embodiment according to FIG. 1, is made of ν an inner shell 134 and an outer shell 136 are formed. Between the two shells 13 ^ and 136 is for stiffening a corrugated cylinder 142 arranged, the

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However, the direction of wave propagation is now different extends from the embodiment of Figure 1 in the circumferential direction. One recognizes between each other facing ends of the corrugated cylinder 142, the axial pad guide channel 152, which is formed by U-profile strips 172 is limited.

FIG. 3 shows the centering ring 54 of the embodiment according to FIG. 1 with the eyelet 56. This centering ring can be used for the embodiment according to FIG Change will be accepted.

A thread storage on the runway from the bobbin 26 up to the thread guide eyelet 70 is provided at most insofar as the one emerging from the eyelet 56 Thread can apply to the polished surface 58 with a helical course.

The embodiment of Figure 4 differs from the embodiment of Figure 1 only insofar as than a cover 274 is placed on the rotating surrounding jacket 232. This cover 274 engages with its edge 276 with the mediation of an elastic sealing and securing ring 278 in an extension 278 at the axially outer end of the outer jacket 236. The thread 268 leaves the lid 274 rotating with the surrounding jacket 232 through a lid " eyelet 280. The cover 274 is carried by a support bearing device 282. This support storage facility comprises a support arm 284 which supports the cover 274 by means of a ball bearing 286. The support arm 284 is pivotally mounted at 288. An over-center spring 288 holds the cover 274 in two stable positions Layers, one of which corresponds to the closed position of the cover on the surrounding jacket 232 (drawn out

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shown) and the other is shown in dashed lines.

Thanks to the »support bearing device, the main bearing 212a, 212b is relieved of the moment that is generated due to the horizontal position of the spindle shaft axis from the dead weight of the spindle shaft, the bobbin case, the bobbin case, the bobbin case, the surrounding casing and the cover of the surrounding casing. However, in order to prevent geometric overdetermination due to individual bearings 212a, 212b and 286 that are not exactly aligned, at least one of the two individual bearings 212a, 212b is elastically arranged in the radial direction, for example by being seated in a rubber ring (not shown) .

The mode of operation of the two-for-one twisting spindle shown in FIG is otherwise the same as that of the two-for-one twisting spindle according to Figure 1, but with the additional advantage that the thread tension is further reduced, as a result, that the rotating thread path 268 is encapsulated practically over its entire length.

In FIG. 5, a shoe brake is shown which is intended to act on the spindle whorl 216 according to FIG is determined. The shoe brake comprises two scissors arranged operating levers 290a, 290b, on which brake shoes 292a, 292 b and belt lifting rollers 294a, 294b for lifting the belt 218 from the quarter 216 are arranged. The belt lift-off rollers 294a, 294b can, as can be seen from FIG. 5a, be replaced by lifting cams 296a or 296b. The operating levers 290a, 290b are at their ends remote from the jaws

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with the core 298 or the jacket 300 of a Bowden cable connected and held by a helical compression spring 302 in the brake release position. A foot pedal 304, which is mounted about a pivot point 306 and is under the action of a helical spring 308, is used for Applying the shoe brake. To produce a symmetrical tightening is between an abutment 310 and Another helical compression spring 312 is arranged at the end of the Bov / denzugseele 298.

FIG. 6 shows the arrangement according to FIG. 5 with the shoe brake released.

In the figure 7 a differently designed actuating device for the shoe brake is shown. To the Actuating levers 490a, 490b are engaged by a lifting magnet 493 via intermediate links 491a, 491b. A coil spring 495 is used to release the shoe brake.

In Figures 8 and 9, an embodiment of the thread brake inlet tube assembly is shown. That Inlet pipe 564 is telescopic here in the outer part of the thickening that accommodates the actual thread brake guided and biased by a helical compression spring 566 to the outside. This way it will run in the thread A storage section is created between the bobbin and the thread guide eyelet, which is thereby available it is made that when the voltage increases, the inlet pipe 564 telescopes into the actual Thread brake absorbing thickened body 562. is pushed. The actual thread brake is also not shown in FIGS. 8 and 9.

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In the embodiment according to FIGS. 10 and 11, 662 again denotes the thickened body, which takes up the actual thread brake, not shown again, while with 664 a multi-part here formed inlet pipe is designated. This inlet pipe is composed of a piece of pipe 669 fixed to the thickened body 662 and one on this tube piece 669 displaceable cap 671. This cap 671 carries at its outer end a Thread inlet eyelet 673 and, next to this eyelet 673, a bushing 675 which telescopically engages in the fixed piece of pipe 669. A helical compression spring 677 biases the sleeve 671 in its outer position. The storage section is also here in the event of voltage peaks effective in the thread in that the sleeve 671 is pushed into the position according to FIG. 11, see above that the thread path is shortened.

To the embodiment according to Figures 1, 2 and 3 is still to be added that the corrugated cylinder 42 or 142 between the shells 34 and 36 or 134, 136 next Spring steel can preferably also be made from sheet aluminum. For example, sheet aluminum is suitable with a wall thickness of 0.3 mm. The use of aluminum sheet between two trays that also consist of aluminum sheet, has the advantage that in addition to the preferred gluing also a Welding is relatively easy.

It should be added that the stationary housing, in addition to the draft shield, also serves as a protection against accidental contact takes over.

It should also be mentioned that the stationary housing 72 widens conically towards its end on the bearing side

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can be. Such a conical enlargement has proven itself in terms of on the draft protection of the operating personnel proved to be favorable, because then an air movement takes place towards the warehouse, which also has the advantage of bearing cooling. To avoid a build-up of air at the end of the fixed housing on the bearing side 72, air openings can be provided in the bottom of the stationary housing on the bearing side.

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Claims (30)

Claims 1. A multiple-wire twisting spindle comprising one on one End rotatably mounted, connected to a rotary drive spindle shaft and one on this spindle shaft rotatably mounted and prevented from turning, the material to be twisted, coming from at least one bobbin seated on the bobbin, via a standing clamp or Braking point passed through the bobbin and into the end of the spindle shaft remote from the main bearing is, at the main bearing-side end of the spool out of the spindle shaft and as a circumferential material path within a surrounding jacket over the coil body into the area of the spindle axis is characterized by the combination of the following known features: a) The axis of the spindle is horizontal or inclined at a small acute angle to the horizontal, b) the surrounding jacket (32) rotates with the spindle shaft (14) and c) the coil carrier (22) is due to eccentric weight distribution prevented from turning with the spindle shaft (14). 2. Kehrfachdraht-Zv / irnspindel according to claim 1, characterized characterized in that the circumferential material path in a guide channel (52) of the surrounding jacket (32) is performed. 309845/0538 3. Multiple wire twisting spindle according to claim 2, characterized characterized in that the guide channel (52) of the surrounding jacket (32) connects to a radial guide channel (50). 4. Multiple-wire twisting spindle according to one of the claims 1 to 3 »characterized in that between the surrounding jacket (32) and the stationary bobbin (26) radially within the circumferential thread path a fixed jacket (68) is arranged. 5. Multiple-wire twisting spindle according to one of the claims 2 to 4, characterized in that the guide channel (52) of the surrounding jacket (32) in the axial direction before The end of the surrounding jacket (32) remote from the main bearing ends. 6. Multiple-wire twisting spindle according to one of the claims 1 to 5, characterized in that the surrounding jacket (32) is made in a two-shell construction with the installation of connecting means (42) which transmit thrust at least in the circumferential direction between the two shells (34, 36). 7. Multiple-wire twisting spindle according to claim 6, characterized in that that the connecting means are formed by a corrugated material (42) which is inserted into the shaft washer means (44, 46) is connected to the shells (34, 36). 8. Multiple-wire twisting spindle according to claim 7, characterized characterized in that the corrugated material (42) is glued to the shells (34, 36). * 9. Multiple-wire twisting spindle according to claim 7 »characterized in that that the corrugated material (42) is welded to the shells (34, 36). 309845/0538 10. Multiple-wire twisting spindle according to one of the claims 7 to 9, characterized in that the wave continuation direction of the corrugated material (42) runs in the circumferential direction or in the axial direction. 11. Multiple-wire twisting spindle according to one of the claims 7 to 11, characterized in that the two shells (34, 36) are made from thin-walled sheet metal are. 12. Multiple-wire twisting spindle according to claim 11, characterized characterized in that with an inner diameter of the surrounding jacket (32) of 170 to 380 mm, the wall thickness of the two shells each 0.2 to 1.2, preferably 0.3 to 0.6 mm, and the distance between the two shells (34, 36) 5 to 15 mm, the smaller sheet thicknesses and spacing values the smaller Correspond to diameter values. 13. Multiple-wire twisting spindle according to one of claims 7 to 12, characterized in that the guide channel (52) for the circulating material path between the two shells (34, 36) of the surrounding jacket (32). 14. Multiple-wire twisting spindle according to claim 13, characterized characterized in that when using a corrugated material (142) with a corrugation extending in the circumferential direction direction a guide tube (172) between the opposite ends of the arranged as an open ring YJellmaterials is housed. 15. Multiple-wire twisting spindle according to one of the claims 7 to 14, characterized in that the radially inner shell (34) and the thrust-transmitting connection 3 0 9 8 U B / 0 5 3 8 means (42) end in the axial direction in front of the end of the radially outer shell (36) remote from the main bearing. 16. Multiple-wire twisting spindle according to claim 15 »thereby characterized in that at the end of the radially inner shell (34) and the thrust-transmitting connecting means (42) a centering ring which may be used to compensate for unbalance (54) is arranged. 17. Keptile twisting spindle according to claim 16, characterized characterized in that the centering ring (54) has a material guide eyelet (56), the end of the guide channel (52) defining passage. 18. Multiple-wire twisting spindle according to one of the claims 6 to 17, characterized in that the two shells (34, 36) each have a shell bottom (38, 40) "are executed" and that a spacer disk (48) is arranged between the two shell bottoms (38, 40) is, within which the radial guide channel (50) runs. 19. Multiple-wire twisting spindle according to claim 18, characterized in that the shell bottom (40) of the outer Shell (36) is attached to a carrier disk (28) through the intermediary of an elastic damping layer (30). 20. Multiple-wire twisting spindle according to one of claims 1 to 19, characterized in that the circumferential Umfassffiantel (32) is surrounded by a stationary housing (72). 21. Multiple-wire twisting spindle according to claim 20, characterized in that the housing (72) is cylindrical Has cross-section. 309845/0538 Sb 22. Multiple-wire twisting spindle according to one of the claims 1 to 21, characterized in that an elastic, length compensation in the material guide path serving guide member (564) is provided. 23 .. Multiple-wire twisting spindle according to claim 22, characterized in that characterized in that in the extension of the spindle shaft (14) a stationary, leading to a thread brake Inlet pipe (564) is arranged, which is displaceable in the axial direction against spring resistance (567) is. 24. Multiple-wire twisting spindle according to one of claims 1 to 23, characterized in that the main bearing remote End of the surrounding jacket (232) through a material passage opening (280) removable cover (274) can be closed. 25. Multiple-wire twisting spindle according to claim 24, characterized characterized in that the removable cover (274) can be disengaged in one for the purpose of removing the cover Support bearing device (282) is mounted. 26. Multiple-wire twisting spindle according to claim 25, characterized in that the support bearing device (282) has a pivotable support arm (284) which carries the cover (274) in a support bearing (286). 27. Multiple-wire twisting spindle according to one of claims 25 and 26, characterized in that the main bearing (212a, 212b) is designed to be elastic. 28. Multiple-wire twisting spindle according to claim 27, characterized in that when the main bearing (212a, 212b) from two single-oil bearings lying next to one another in the axial direction, at least that of the support bearing 309845/0538 device (282 ^ ~ closer single bearings (212b) elastic is arranged. 29. Multiple-wire twisting spindle according to one of the claims 27 and 28, characterized in that when the rotary drive is designed with one on the spindle shaft, it is non-rotatable arranged spindle whorl (216) and a tangential Drive belt (218) running over this whorl, a shoe brake (292a, 292b) for attacking the spindle whorl (216) is provided which, when the support bearing device (282) is ineffective, the stabilization of the Spindle shaft (214) takes over. 30. Multiple-wire twisting spindle according to claim 29, characterized in that the brake shoes (292a, 292b) of the Shoe brake sit on actuating levers arranged like scissors and that actuating levers on these actuating levers (290a, .29Ob) Release rollers (294a, 294b) or cams · (296a, 296b) for lifting the drive belt off the Whorls (216) are arranged. 30 9 845/0538