US3904140A

US3904140A - Apparatus for changing the end structural configuration of thread packages

Info

Publication number: US3904140A
Application number: US413727A
Authority: US
Inventors: Peter Hermanns
Original assignee: FMN Schuster GmbH and Co KG
Current assignee: FMN Schuster GmbH and Co KG
Priority date: 1972-11-10
Filing date: 1973-11-07
Publication date: 1975-09-09
Anticipated expiration: 1992-09-09
Also published as: JPS49124344A; GB1451774A; CH575877A5; FR2206752A5; JPS5417066B2

Abstract

A delivery mechanism feeds a thread to a spool driven by a friction roller. The thread delivery means includes a thread guide element movably mounted for back and forth motion along the length of the spool by means of a reverse thread roller. The thread guide element includes means contacting a pivotally mounted guide rail during said back and forth movement. An operating rod is connected at one end to the guide rail and connected at the other end thereof via a retainer arm to the rotational axis for the thread package so that the guide rail will pivot around its pivot pin in response to an increase in the thread package diameter. A control mechanism is disposed between the spool rotational axis and the guide rail to influence the pivotal deflection of the guide rail. The control mechanism includes a cam surface and a lever means connected at one end to the guide rail at a point displaced from the pivotal axis of the guide rail and connected at the other end thereof to the operating rod. The cam surface is in contact with the lever means along its length thereof.

Description

United States Patent 1191 Hermanns APPARATUS FOR CHANGING THE END STRUCTURAL CONFIGURATION OF THREAD PACKAGES Peter Hermanns, Stommeln, Cologne, Germany [73] Assignee: FMN Schuster & C0.,

Hurth-Efferen. Germany 22 Filed: Nov. 7, 1973 [2| App|.No:4l3,727

{75] Inventor:

[ 51 Sept. 9, 1975 Primary Exuminer$tanley N. Gilreath Attorney. Agent, or Firm-Markva & Smith [57] ABSTRACT A delivery mechanism feeds a thread to a spool driven by a friction roller. The thread delivery means in cludes a thread guide element movably mounted for back and forth motion along the length of the spool by means of a reverse thread roller. The thread guide element includes means contacting a pivotally mounted guide rail during said back and forth movement. An operating rod is connected at one end to the guide rail and connected at the other end thereof via a retainer arm to the rotational axis for the thread package so that the guide rail will pivot around its pivot pin in response to an increase in the thread package diameter. A control mechanism is disposed between the spool rotational axis and the guide rail to influence the pivotal deflection of the guide rail. The control mechanism includes a cam surface and a lever means connected at one end to the guide rail at a point displaced from the pivotal axis of the guide rail and connected at the other end thereof to the operating rod. The cam surface is in contact with the lever means along its length thereof 14 Claims, 16 Drawing Figures PATENTEDSEP ems 3 904 140 SHEET 1 [1F 8 PATENTED SEP 9 I975 SHEET 3 BF 8 PATENIED E 91975 3.904.140

SHEET u or 8 FIG. 7

PATENTEB 9i975 '3 904 140 SHEET 5 BF 8 FIG. 9

FIG. 10

PATENTEI'iSEP 91975 3.904.140

swan s or 8 FIG.

F-MENI'EF B 9 SHEET 8 BF FIGJL FIG.16

APPARATUS FOR CHANGING THE END STRUCTURAL CONFIGURATION OF THREAD PACKAGES BACKGROUND OF THE INVENTION Winding machines are generally designed so that the thread is passed to a driven spool through a thread guide which moves back and forth by means of a reverse thread roller. The thread is fed at constant speed and the spool upon which the thread package is formed is driven by a friction roller. Consequently. the thread is wound up on the spool at a uniform speed independcntly of the increasing diameter of the roll being wound. The end structural configuration of thread packages formed on such a winding machine is straight. Such thread rolls or packages are used in particular for the process of dyeing the thread.

When the thread packages are intended for subsequent use on a processing machine. it is desired to form a conically shaped end structural configuration. It is known to swing the thread guide in the vicinity of the turning region so that conically shaped end configurations are formed on the thread package. That is. thread package is said to have a biconical structure. A guide rail is used in conjunction with the moving thread guide so that the thread guide will swing in varying amounts as the diameter of the thread package increases. The guide rail is pivotally mounted and controlled via an operating rod. The spool core or thread package is maintained in position against the friction roller by a spool retaining arm. The operating rod is connected to the spool retaining arm. As the spool retaining arm changes position as a result of the increase in the thread package diameter. the operating rod is moved thereby causing the guide rail to pivot around its pivotal axis.

When biconical thread packages are to be used directly on a processing machine, it is necessary to have different forms of conically shaped end configurations for the thread package. For some threads or yarns. a biconical structure of the roll or package must have a relatively steep angle with respect to the spool core. In other biconical rolls or packages used for other processing machines, the conicity of the end configurations for the packages should have a considerably fiatter angle. That is. they should tend to be toward a substantially perpendicular relationship with respect to the axis of the spool core.

There are prior art winding machines which may be used for producing rolls with a biconical end configuration. These prior art machines may be used to produce thread packages having end configurations having different angles of inclination including sides that are per pendicular with respect to the axis of the spool core. However. it is necessary to dismantle and refit these prior art winding machines in order to obtain the differing degrees of steepness in the sides of a biconical roll. This requires considerable outlay of time and labor. Moreover. these prior art winding machines have a multiple number of winding stations and each of the winding stations must be refitted individually. Another disadvantage of these prior art winding machines is that thread packages having identical side or end structural configurations are not assured. At the least. a consider able outlay in apparatus is necessary in order to obtain thread packages having identical end structural configurations.

PURPOSE OF THE INVENTION The primary object of this invention is to provide a winding machine including apparatus for changing the end structural configuration of thread packages through the use of a control mechanism.

SUMMARY OF THE INVENTION As disclosed herein. the invention is directed to the use ofa control mechanism used in conjunction with a winding machine. The winding machine has a thread guide driven by a reverse thread roller. A guide rail is used for providing additional swinging of the thread guide at the point on the reverse thread roller where the thread guide changes directions. The guide rail is pivoted about a pivot point. A retaining arm for the spool core carrying the thread package is moved in a swinging motion about another pivot point as the thread package diameter increases. The control mechanism provides a means for additionally acting upon the deflection of the guide rail about its pivot point. The control mechanism has a lever which rocks about a moving point located on a cam surface that is movably supported along the length of the lever.

In accordance with another feature of the invention.

a cam support element having a cam surface which contacts the lever is designed as a slide block. On the side of the slide block facing away from the lever. at least one oblique surface cooperates with intersecting oblique surfaces located on a positioning mechanism. In a specific embodiment. the cam support element includes intersecting slope portions forming a roofshaped projection that engages the intersecting oblique surfaces forming an annular recess on said positioning mechanism.

The slide block is fixedly mounted on a rod means which extends in a direction of movement of the thread guide element. Means is provided to cause the rod means to move in a continuous back and forth move ment. When the rod mem s is in continuous back and forth movement within a region of one angular recess in the positioning mechanism. an edge displacement of the thread can be achieved by the interengagement of the oblique shaped projection with the annular recess. The so-called edge displacement of the thread at the side or ends of the thread package has the purpose of distributing the turning point of the thread on the spool sides over a certain inward area. That is. the threads are brought to the extreme outside edges of the thread package and then the extreme turning point for the thread guide is changed to lay thread at a point displaced inwardly from the outermost edge of the thread package. This process is continued for the entire winding operation so that a soft edge configuration is formed and a thread build up is avoided at the extreme outer edge of the thread package.

In other words. the guide rail is continuously moved back and forth within a predetermined range of fluctuation. When the stroke length of the thread guide is al tered within the predetermined range of fluctuation. the required edge displacement of the thread on the thread package results. This is achieved on every attainable roll structure formed on the winding machine.

In another embodiment of this invention. a cam support element is slidably engaged with a carrier member movably disposed on a rail means. The carrier means includes stop means for locating the cam carrier means along said rail means at any predetermined location. The carrier means includes a first cam surface having a delimited length and the cam support element includes a second cam surface movably contacting the first cam surface and having a shorter length than the first cam surface. When the cam support element is in an operative position, the second cam surface activates the stop means in the carrier means. When the cam support element is in an inoperative position, the stop means is released so that the carrier means may be relocated at any desired location along the rail means.

A further feature of the invention is directed to the stop means which includes a spring biased bolt that engages holes located in a strip member of the positioning mechanism. The carrier has a first cam surface that cooperates with the second cam surface on the cam support element independently of the stopping means. Through the use of this feature of the invention, it is possible to allow a longer path than previously for the continuous back and forth movement of the guide rail. Consequently. the region of edge displacement motion for the thread being placed on the spool core becomes greater.

A further feature of the invention is to provide a concave end configuration on the thread package by providing a curved cam surface on the slide block on the side facing the lever. The lever is held in contact with the curved cam surface. A spring provides the necessary biasing force against the guide rail to draw the guide rail and lever toward the cam surface of the slide block during movement of the rod means. Through the use of this structural configuration, a certain displacement of the point of contact on the curved cam surface is effected between the cam support element and the lever. Although the slide block remains within a certain delimited area on a positioning mechanism. the point of contact between the lever and the curved cam surface moves as the thread package diameter increases. This results in a corresponding additional displacement of the thread guide in such a way that a concave edge formation results on the end surface of the thread package. The less curvature there is on the curved cam surface of the slide block, the more intense the concavity on the end of the thread package.

The slide block is advantageously provided with an interchangeable head piece containing the curve. Thus. it is simple and convenient to prc'dcterminc the degree of concavity on the end of the thread package. When the point of support for the lever is formed as a point of rotation. no concave structure is formed. i.e. when the support point on the lever is very sharply curved. The concave spool level can be produced in all types of thread packages to be made on the winding machine.

BRIEF DESCRIPTION OF DRAWINGS Other objects of this invention will appear in the following description and appended claims, reference being made to the accompanying drawings forming a part of the specification wherein like reference characters designate corresponding parts in the several views.

FIG. I is a diagrammatic perspective view ofan apparatus made in accordance with this invention;

FIG. 2 is a diagrammatic side elevational view of an apparatus of the type shown in FIG. I;

FIG. 3 is a diagramatic side elevational view ofa fur ther embodiment of an apparatus made in accordance (ill with this invention incorporating a control mechanism therein;

FIG. 4 is a diagrammatic top plan view of the apparatus as shown in FIG. 1;

FIGS. 5 and 6 are diagrammatic top plan views showing the operation ofa control mechanism for producing a thread package having an end configuration with sides disposed perpendicular to the spool axis;

FIG. 7 is a diagrammatic sectional view of the thread package formed in the operation as shown in FIGS. 5 and 6;

FIGS. 8 and 9 are diagrammatic top plan views of a control mechanism used for producing thread packages having biconical end configurations;

FIG. 10 is a diagramatic sectional view of a thread package as formed during the operation of the process depicted in FIGS. 8 and 9;

FIG. I I is a top plan view showing a control mechanism for effecting edge displacement of the thread to form a soft edge on the thread package;

FIG. 12 is a diagrammatic top plan view showing the operation of a control device for producing a concave spool level or thread package end configuration;

FIG. I3 is a diagrammatic elevational view of a thread package having a concave end configuration made in accordance with the process depicted in FIG. I2;

FIG. I4 is a diagrammatic elevational view of another embodiment of the control mechanism made in accordance with this invention;

FIG. 15 is a side elevation view partially in section of the control mechanism as shown in FIG. I4, and

FIG. 16 is a cross-sectional view along the line XVI- XVI of FIG. I4.

DESCRIPTION OF SPECIFIC EMBODIMENTS More specifically, referring to the drawings, a winding machine for producing thread packages from synthetic or textile threads includes a changeover r traversing thread guide device I. A slide 4 moves back and forth on a guide rod 3 by means of a runner (not shown) which engages a spiral groove of a reverse thread roller 6. The guide rod 3 is fixedly mounted within the casing 2. The thread guide is pivotally mounted on slide 4 around the point of rotation 8. Slide block 9 is mounted on thread guide 7 and engages a guide rail having a generally U-shaped cross-section. The guide rail I0 is pivotally mounted at the pivot pin 11 that is disposed in the aperture located in the free end of block I2 which is screwed or otherwise secured to the casing 2.

The thread package I4 is wound onto the spool core 13 that is pivotally mounted on spool retaining arms to pivot around rotary axis I6 of block 17. This structural configuration for mounting the spool core I3 is a conventional prior art structure. The thread package is driven by a friction roller I8 which is itself driven by a motor 19 by means of pulleys 20 and 2] and the transmission belt 22. The reverse thread roller 6 is in a predetermined drive ratio to the friction roller [8. The drive for the reverse thread roller 6 is derived from the gear motor I) by means of transmission members 23. 24 and 25.

An operating rod 26 is connected at one end to the guide rail [0 and at the other end to a pivotal spool retainer arm 15 that is attached to the rotational axis of thread package I4. The stroke length of the thread guide 7 is influenced by the position of the pivotal guide rail 10 which pivots around pin 11. The pivotal movement of guide rail 10 is controlled by the deflection of the spool retainer arm 15. As the diameter of the thread package 14 increases thereby laterally moving the rotational axis thereof, the spool retainer arm 15 pivots upwardly away from the friction roller 18 and moves the operating rod 26. Thus, the thread package is given a biconieal form with a strictly predetermined shape. That is, as the diameter of the thread package 14 increases, the distance of travel for the thread guide 7 along the casing 2 becomes shorter resulting in the biconieal form.

Thread 27 is fed to the thread guide 7 which directs the thread for winding onto the package 14. An additional control device, generally designated 28 and shown in FIG. 4, also influences the movement of guide rail 10 about the pivot pin 11. Control device 28 includes a lever 29 connected at one end to the operating rod 26 by means ofjoint 30 and at the other end to the guide rail 10 by means ofjoint 3t. Lever 29 is contiguous to and rides along the cam surface 38 of element 32. The cam element 32 is fixedly connected to a push rod 33 which is displaceable and therefore the position of the cam element 32 may be changed with respect to the length of lever 29.

The support cam element 32 is formed as a slide block and cooperates with a catch device 34. In this specific embodiment there are four catch points on the catch device 34. A roof-shaped oblique cam surface 35 is located on the cam slide lock 32 and engages the oblique angular recessed surfaces 36 of the catch device 34. The surfaces 36 at each of the four catch points on the catch device or rail 34 include oblique angular recessed surfaces 36a and 3612 which intersect at an angle with respect to each other. The oblique surfaces 36u and 36/) may have the same or a different angular position with respect to one another or with respcct to the axis of the push rod 33. Spring 37 is connected to the guide rail 10 and biases the guide rail 10 so that the lever 29 is brought into contact with the cam slide block 32. In other Words, as the lever 29 rocks along on the cam surface 38. the guide rail 10 is correspondingly pivoted about the pin ll as shown.

The lever 29 may contact the cam surface 38 of the cam slide block 32 at a point shaped connection point so that the lever 29 substantially rests on a cutting edge as in a balance beam. Thus. the lever 29 rocks back and forth ab ng various contact points on the cam surface 38 since it is rotatable around this cutting edge. In this specific embodiment, the cam surface 38 has an areaate curve configuration. In addition. a head piece 39 is placed over the cam slide block 32 thus providing the direct contact between the cam surface 38 and the lever 29. The head piece 39 is interchangeably mounted on the cam slide block 32.

The catch rail 34 may also be easily interchanged since it is secured by screws at an appropriate point to the casing 2. The casing 2 advantageously has a troughshapcd housing which extends across a series ofjustaposed winding machines. The traversing thread guide device 1 is defined by insertablc or interchangeable side wall elements 40. The particular configuration of the casing 2 may be constructed in accordance with the applicant's copending US Pat. application No. 413.725. filed on Nov. 7. I973 in the United States Patent Office. A push rod 33 can likewise extend across the series ofjuxtaposed winding machines as shown in FIG. 4. In the diagrammatic views shown in the figures, the thread package 14 and friction roller 18 are shown as turned through into the plane of the drawing in order to clarify the motion of the linkage.

Referring to FlGs. 5 through 7, the thread package as shown in FIG. 7 having vertically disposed end configurations is produced in accordance with the operations diagrammatically shown in FIGS. 5 and 6. The cam slide block 32 is in contact with the lever 29 under the connection point 31 at which point the pivotal guide rail 10 is connected to the lever 29. Thus, the stroke length of thread guide 7 does not change as the spool diameter increases. That is, while the operating rod 26 may move because of an increase in the diameter of the thread package 140. the resultant movement of lever arm 29 does not change the position of the guide rail 10 about its pivot pin 11. Consequently. the thread guide 7 turns at the same point along line 41 when the thread package 144: is small as shown in FIG. 5 and when the diameter of the thread package is large as shown in FIG. 6. The same functional result applies for the turning point located at the other end of the reverse thread roller where the thread guide 7 changes directions.

To form the biconieal spool structure 14!) as shown in FIG. 10. reference is made to the operation as set forth in FIGS. 8 and 9. The slide block or cam support element 32 is pushed a greater or smaller distance away from the point of connection 31. This movement is effected by changing the position of the push means con stituted by push rod 33. The adjustment is made to have the slide block 32 maintained at the working position in the extreme right side of the positioning mechanism 34 as shown in FIGS. 8 and 9. Lever 29 bears on the curved cam surface of block 32 at point 42. It is also possible to provide a cutting edge rather than a curved cam surface.

The lever 29 serves as a path changeover in this particular embodiment. The path length of operating rod 26 is transmitted in proportion to the lever arm lengths of lever 29 to the point of connection 31 between the guide rod 10 and lever 29. In this way, the diameter of the thread package 1411 increases and the stroke of the thread guide 7 is reduced across the length of the spool core. The thread guide 7 begins with a long stroke at line 42 corresponding to the contact point 42:! on the lever 29. The distance 4212 is shown on the biconieal structure of FIG. 10 and corresponds to the line stroke 42 made by thread guide 7. The final and shortest stroke of thread guide 7 extends along the thread spool to a line 43 which is also shown in length on the thread package depicted in FIG. 10.

Depending upon which catch or stopping position 36 the slide block 32 occupies, the conical shape of thread package 14h will differ. The nearer the slide block or cam support element 32 lies to the point of connection 31, the steeper will be the conicity of thread package 1411. The further away the slide block is provided from the point of connection 31, the flatter will be the conical shape of the thread package 14h, Thus. the various stops or operating positions 36 on the positioning mechanism 34 allows for the production of thread packages having vertical sides and conical sides of various angular configurations. Depending upon the particular operational position of the slide block outside the connection point 31. the sides of the thread packages will take on a differing angle.

The slide push rod 30 moves back and forth axially along a short delimited path during the operation ofthe apparatus as shown in FIGS. through It). The slide block 32 moves on each of the oblique surfaces 36 in the direction of its longitudinal extension In this way. the pivotal guide rail 10 is continually altered in its angle of incidence in a predetermined small area. This correspondingly influences the stroke length of the thread guide 7. There is an edge displacement of the thread obtained during production of the thread package clue to the back and forth movement of the push rod 33. This edge displacement is referred to as breathing. That is. the build up of thread is obviated along the edge of the thread package.

Traction spring 37 continuosuly pulls lever 29 against the slide block 32. Consequently, lever 29 is always in contact with slide block 32 during the biconical construction of the thread package. The slide block 32 operates correctly in each of the recesses formed by the intersecting oblique surfaces on the operational positions of positioning mechanism 34. The direction of movement for the push rod 33 is not axial with respect to the thread package 14 because of the contacting of the oblique surfaces on the block 32 and the positioning mechanism 34. See the double-headed arrow 44 in FIGS. 4. 11. and 14. The edge displacement of the thread can be effected in any operational catch position 35. In other words. the edge displacement of the thread can be effected in end configurations having a perpendicular end configuration and in thread packages having different biconical shapes. The back and forth movement of a push rod 33 may be effected by an eccentric or the like within a small predetermined range.

A concave spool level or end configuration can also be obtained on the thread package 14. A curved cam surface 38 having a predetermined arcuate form enables a linear movement of operating rod 26 to be nonlinearly transmitted to the pivotal guide rail 10 as the diameter of the spool package I40 increases as shown in FIG. 12. This linear movement of operating rod 26 is effected as the lever 29 rolls down the curved cam surface 38 in dependence on the increase in diameter of the thread package I40 In this way. the lever ratio between link points and 31 alters continuously. This is visually shown in FIGS. 12 and 13. The various diam eters of thread package 14c are shown by A. B. C and D. Thus, there are four different positions of length point 30 from Al to D]. The result of these positions is that lever 29 comes into contact at various points along the curved cam surface 38. These points are shown in succession as A2 to D2. This results in an alteration in proportion of the lever arms to the support point A2 to D2 on the slide block 32.

Guide rail 10 is correspondingly influenced so that depending upon the diameter of thread package 141'. the thread guide 7 adopts the positions A3 to D3. There results a concave end configuration on the thread package as shown in FIG. 13 according to the stroke lengths A3 to D3. A concave spool level or end configuration can also be obtained with a vertical end structure or a thread package having flat ends with an angle ofinclination of 90. If a nonconcave end configuration is re quired on the thread package. the flat slide are 38 may be replaced by a curve of greater curvature so that lever 29 has a knife-like contact on slide block 32.

The embodiment as shown in FIG. 3 includes a cow trol mechanism having a lever 29a that is not housed in the casing 2. Lever 29a is flexibly connected by a bell crank 29b to a rod 45 which engages on link point 31 of guide rail 10 by way of an intermediate rod 46. All of the adjustments which were possible on the embodiments as discussed hereinabove may be made on this embodiment including edge displacement and various types of end configurations on the thread package.

The control mechanism as shown in FIGS. 14 through I6 includes a control device. generally designated 2811, used to affect the deflection of guide rail 10. The lever 29 is interposed between the actuating rod 26 and the guide rail 10 by means of

joints

30 and 31 as in the earlier embodiments. Lever 29 is supported on the cam surface of a cam support element 320 which can be moved along the lever 29. The cam support element 32a is fixedly connected to the push rod 33 which is moved back and forth and to a desired longitudinal location along lever 29 by suitable cam means. Cam support element 32a is designed as a slide block and co operates with a positioning mechanism which is cured to the casing of the winding machine.

The positioning mechanism includes a carrier member 49 disposed on a strip member 48 that is rigidly connected to a rail 34a. Screws 50 connect the strip member 48 to the rail 34a. A series of holes 51 are located along the strip member 48. The carrier member 49 is movable along the strip member 48 and includes an oblique wedge or first cam surface 52. the cam support element 3211 includes a complimentary wedge or second cam surface 53 which is in sliding engagement with the first cam surface 52.

The carrier 49 includes a stop means for locating the cam carrier 49 along the rail 3411. Stop means includes a spring bolt or pin 54 engaging the catch holes 5] located in the strip member 48. The spring 54a causes the pin 54 to be spring loaded as shown. As shown in FIG. 15. the carrier 49 engages around the strip member 48 on both longitudinal sides thereof. the carrier 49 is securely pressed against the strip member 48 by means of a spring 55. The wedge or first cam surface 52 has a delimited lcngth defined by end stops 52a and 52/1. The length of the first cam surface 52 is considerably greater than the length of the second cam surface 53. Garrier 49 may be displaced from one lock position or hole 51 to another by manually seizing and moving carrier 49 along rail 340 when the spring load on pin 54 is manually overcome. At each lock position or hole 51, the pin 54 automatically moves into engagement with the hole 51. Thus. carrier member 49 may be moved to a different position where the catch bolt 54 may be pushed into another hole 51 at a different opcr ating position. Alternatively. each cam surface 53 may abut either of the stops 52a or 52h with further movement while contacting either of the stops 520 or 52h will overcome the spring load and carrier 49 will be moved along rail 34a.

Push rod 33 makes a continuous back and forth motion thereby causing the edge displacement of the thread on the thread package as discussed hereinabove. At the same time. the second cam surface 53 slides back and forth along the first cam surface 52 on the carrier 49. the shape of the end configuration for the thread package is determined by the position of carrier 49 along the rail member 48. The carrier member 49 may be appropriately moved by pushing the push rod as far as possible in one direction or another so that the slide block 32a moves against the stop 520 or stop 5212. Thus, the pusher rod 33 will push the carrier 49 along the strip 48. The spring loaded pin or bolt 54 will auto matically drop into the hole 51 at the new operating or catch position. Once the new position has been reached. the second cam surface 53 is brought into the middle position of the first cam surface 52 where short back and forth movement is effected for edge displacement of the thread on the thread package.

ADVANTAGES OF THE INVENTION By using a control mechanism as set forth in the present application, the movement of the guide rail can be effected in such a way that rolls of vertical or conical structure may be achieved. That is, thread packages may be formed wherein the conicity of the end surfaces of the thread packages can be selected at will. If the movable support portion or cam support element on the lever is provided at the point of connection of the lever with the guide rail, the additional control mechanism transmits no movement to the guide rail. Consequently. the influence of increasing spool ddiameter in altering the stroke length of the thread guide is eliminatcd. The further the movable cam support element is removed from the connection point on the guide rail, the more intense is the biconical structure of the roll. That is. the thread package is given conical sides which are at a relatively small angle to the spool core axis. Therefore. thread packages having varied structures can be produced very simply on one and the same machine.

No other type of winding machine is necessary. Further it is not necessary to dismantle and refit a Winding machine for producing thread packages having a conical structure of any type. Depending on the requirements one and the same winding machine can be used immediately for windings of different structures. All that is necessary is the displacement of the cam support element for the relevant lever.

Advantageously. the cam support element for the lever acting on the guide rail can be shifted along several notches or catch points on a positioning mechanism. The number of working locations depends on the number of different structures on the thread package. An infinitely variable system may be provided in accor dance with the apparatus of the present invention. In general, however. several displacement stages are sufficient along the positioning mechanism. The cam support element may be appropriately shifted by means of a rod that is rigidly connected to the cam support element.

There are several advantages associated with the embodiment set forth in FIGS. 14 through l6. Such a design of the interacting parts enables separation between the catch engagement and stopping means which carry out a continuous back and forth movement with respect to each other. It is also possible to provide the sliding cam surfaces which are in continuous motion with respect to each other with large contact areas. This considerably decreases the risk of wear. It is possible to provide more reliable catching and stopping at the selected operating position along the positioning means. It is now independent of the oblique sliding surfaces located on the cam support element and the car rier means which are in continuous contact and relative motion. The desired effect in this particular embodi ment is much more reliable and permanent.

While the apparatus for changing the end structural configuration of thread packages has been shown and described in detail. it is obvious that this invention is not to be considered as being limited to the exact form disclosed, and that changes in detail and construction may be made therein within the scope of the invention, without departing from the spirit thereof.

What is claimed is:

1. An apparatus for changing the end structural configuration of thread packages formed on winding machines of synthetic or textile threads, comprising:

a. a reverse thread roller, a guide rail. a friction r0l ler, a spool driven by the friction roller about means defining a rotational axis and means for delivering thread to the spool,

b. said thread delivery means including a thread guide element movably mounted for back and forth motion along the length of the spool by means of the reverse thread roller,

c. said thread guide element including means contacting the guide rail during said back and forth movement,

d. said guide rail being pivotally mounted,

e. means responsive to lateral movement of said rotational axis means as the diameter of the thread package increases about the spool and a control mechanism disposed between the responsive means and the guide rail to influence the pivotal deflection of the guide rail,

e. sau control mechanism including a cam means and a lever means connected at one end to the guide rail at a point displaced from the pivotal axis of the guide rail and connected at the other end thereof to said responsive means,

h. said cam means including a cam surface being in contact with the lever means along its length thereof.

2. An apparatus as defined in claim I wherein said control mechanism includes a cam positioning mechanism and said cam means comprises a cam support element including said cam surface,

said cam support element being displaceablc along several locations of said positioning mechanism.

3. An apparatus as defined in claim 2 wherein said support cam element includes at least one oblique surface on a side facing away from the lever means and interacting with catch points defined on said positioning mechanism.

4. An apparatus as defined in claim 2 wherein said cam support element includes intersecting oblique surfaces forming a roof-shaped projection engaged with intersecting oblique surfaces forming an annular recess located on said positioning mech anism.

5. An apparatus as defined in claim 4 wherein either the intersecting oblique surfaces of the positioning mechanism or the intersecting oblique surfaces of the cam support element have different angular positions with respect to each other.

6. An apparatus as defined in claim 2 wherein said control mechanism includes a rod means extending in a direction of movement of the thread guide element and a cam positioning means for interaction with said cam support element.

said cam support element being fixedly mounted on tional axis means as the diameter of the thread said rod means, package increases about the spool, and

said control mechanism further including means for e. a control mechanism disposed between the responsubjecting the rod means to a continuous back and sive means and the guide rail to influence the pivforth movement within a delimited length on said 5 otal deflection of the guide rail. positioning means. f. said control mechanism including a cam position- 7. An apparatus as defined in claim 1 wherein ing mechanism, a cam support element including a said cam surface is curved and is disposed contigucam surface and a lever means connected at one ously against the lever means. and end to the guide rail at a point displaced from the said apparatus includes means for maintaining the n pivotal axis of the guide rail and connected at the lever means in contact with said curved cam surother end thereof to said responsive means, face. g. said cam surface being in contact with the lever 8. An apparatus as defined in claim 1 wherein means along its length thereof, said cam means includes a removably mounted head h. said positioning mechanism including a rail means.

portion which includes a curved cam surface that a strip member and a carrier means movably discontacts said lever means. posed on said rail means 9. An apparatus as defined in claim 1 wherein i. said cam support element being slidably engaged a spring means holds the guide rail in contact with the with said carrier means which include stop means lever means which is in contact with the cam for locating said carrier means at several locations means. 30 along said rail means.

It). An apparatus as defined in claim 2 wherein 12. An apparatus as defined in claim 11 wherein the apparatus includes a casing. and said stop means includes a spring biased bolt which said positioning mechanism is detachably connected interengages with holes located in said strip mem to the casing. bcr,

ll. An apparatus for changing the end structural 2 said carrier means including afirst cam surface which configuration of thread packages formed on winding interacts with a second cam surface on the side of machines of synthetic or textile threads, comprising: the cam support element opposite the lever means.

a. a reverse thread roller, a pivotally mounted guide 13. An apparatus as defined in claim ll wherein rail. a friction roller a spool driven by the friction said carrier means includes end stop means defining roller about means defining a rotational axis and 30 a delimited length of a first cam surface thereon means for delivering the thread to the spool. and

b. said thread delivery means including a thread said cam support element includes a second cam surguide element movably mounted for back and forth face movably contacting said first cam surface and motion along the length of the spool by means of having a shorter length than said first cam surface. the reverse thread roller, 14. An apparatus as defined in claim 11 wherein said c. said thread guide element including means concarrier means engages around both sides of the strip tacting the guide rail during said back and forth member and is biased thereagainst by means of a movement, spring.

d, means responsive to lateral movement of said rota-

Claims

1. An apparatus for changing the end structural configuration of thread packages formed on winding machines of synthetic or textile threads, comprising: a. a reverse thread roller, a guide rail, a friction roller, a spool driven by the friction roller about means defining a rotational axis and means for delivering thread to the spool, b. said thread delivery means including a thread guide element movably mounted for back and forth motion along the length of the spool by means of the reverse thread roller, c. said thread guide element including means contacting the guide rail during said back and forth movement, d. said guide rail being pivotally mounted, e. means responsive to lateral movement of said rotational axis means as the diameter of the thread package increases about the spool and f. a control mechanism disposed between the responsive means and the guide rail to influence the pivotal deflection of the guide rail, e. said control mechanism including a cam means and a lever means connected at one end to the guide rail at a point displaced from the pivotal axis of the guide rail and connected at the other end thereof to said responsive means, h. said cam means including a cam surface being in contact with the lever means along its length thereof.

2. An apparatus as defined in claim 1 wherein said control mechanism includes a cam positioning mechanism and said cam means comprises a cam support element including said cam surface, said cam support element being displaceable along several locations of said positioning mechanism.

4. An apparatus as defined in claim 2 wherein said cam support element includes intersecting oblique surfaces forming a roof-shaped projection engaged with intersecting oblique surfaces forming an annular recess located on said positioning mechanism.

6. An apparatus as defined in claim 2 wherein said control mechanism includes a rod means extending in a direction of movement of the thread guide element and a cam positioning means for interaction with said cam support element, said cam support element being fixedly mounted on said rod means, said control mechanism further including means for subjecting the rod means to a continuous back and forth movement within a delimited length on said positioning means.

7. An apparatus as defined in claim 1 wherein said cam surface is curved and is disposed contiguously against the lever means, and said apparatus includes means for maintaining the lever means in contact with said curved cam surface.

8. An apparatus as defined in claim 1 wherein said cam means includes a removably mounted head portion which includes a curved cam surface that contacts said lever means.

9. An apparatus as defined in claim 1 wherein a spring means holds the guide rail in contact with the lever means which is in contact with the cam means.

10. An apparatus as defined in claim 2 wherein the apparatus includes a casing, and said positioning mechanism is detachably connected to the casing.

11. An apparatus for changing the end structural configuration of thread packages formed on winding machines of synthetic or textile threads, comprising: a. a reverse thread roller, a pivotally mounted guide rail, a friction roller, a spool driven by the friction roller about means defining a rotational axis and means for delivering the thread to the spool, b. said thread delivery means including a thread guide element movably mounted for back and forth motion along the length of the spool by means of the reverse thread roller, c. said thread guide element including means contacting the guide rail during said back and forth movement, d. means responsive to lateral movement of said rotational axis means as the diameter of the thread package increases about the spool, and e. a control mechanism disposed between the responsive means and the guide rail to influence the pivotal deflection of the guide rail, f. said control mechanism including a cam positioning mechanism, a cam support element including a cam surface and a lever means connected at one end to the guide rail at a point displaced from the pivotal axis of the guide rail and connected at the other end thereof to said responsive means, g. said cam surface being in contact with the lever means along its length thereof, h. said positioning mechanism including a rail means, a strip member and a carrier means movably disposed on said rail means, i. said cam support element being slidably engaged with said carrier means which include stop means for locating said carrier means at several locations along said rail means.

12. An apparatus as defined in claim 11 wherein said stop means includes a spring biased bolt which interengages with holes located in said strip member, said carrier means including a first cam surface which interacts with a second cam surface on the side of the cam support element opposite the lever means.

13. An apparatus as defined in claim 11 wherein said carrier means includes end stop means defining a delimited length of a first cam surface thereon, and said cam support element includes a second cam surface movably contacting said first cam surface and having a shorter length than said first cam surface.

14. An apparatus as defined in claim 11 wherein said carrier means engages around both sides of the strip member and is biased thereagainst by means of a spring.