US3661019A

US3661019A - Device for transforming a rotary motion into a linear reversing motion, particularly for textile machines

Info

Publication number: US3661019A
Application number: US35316A
Authority: US
Inventors: Josef Kacalek; Josef Bartos; Miroslav Stransky
Original assignee: Elitex Zavody Textilniho
Current assignee: Elitex Zavody Textilniho
Priority date: 1970-05-07
Filing date: 1970-05-07
Publication date: 1972-05-09
Anticipated expiration: 1989-05-09
Also published as: JPS5179286U; JPS545987Y2

Abstract

A device for transforming a rotary motion into a reciprocatory linear motion. The device is useful, for example, for use as a yarn laying traverse mechanism for textile machines such as winding machines. Two spaced parallel cylinders are driven, usually at constant speed. The cylinders are provided with helical grooves, corresponding elements of which are in transverse alignment. A yarn guide member is mounted for travel between and longitudinally of the cylinders. The yarn guide member is provided with a transversely slidable pin; means is provided for shifting one end of the pin into the helical groove in one of the cylinders at the end of a forward stroke of the guide member, and for shifting the other end of the pin into the helical groove in the other of the cylinders at the end of the reverse stroke of the guide member.

Description

[451 May 9,1972

United States Patent Kacalek et al.

ROTARY MOTION INTO A LINEAR 284,158 1/1928 Great Britain.............................74/58 REVERSING MOTION, PARTICULARLY FOR TEXTILE MACHINES [72] Inventors:

Primary E.\'aminerWilliam F. ODea Josef Kacalek; Josef Banos; Mimslav jssislant Exmlginelggesley S. Ratliff, Jr. Stransky, all of Usti Nad Orlici, Czechoslovakia ABSTRACT [73] Assignee: Elitex, Zavody textllniho strojirenstvl,

Liberec Czechoslovakia A device for transforming a rotary motion into a reciprocatory linear motion. The device is useful, for example, for use as a Flledl y 7, 1970 yarn laying traverse mechanism for textile machines such as winding machines. Two spaced parallel cylinders are driven, usually at constant speed. The cylinders are provided with helical grooves, corresponding elements of which are in trans- [21] Appl. No.:

'm74/58 verse alignment. A yarn guide member is mounted for travel 'F16h25/12 between and longitudinally of the cylinders. The yarn guide 74/58 57 member is provided with a transversely slidable pin; means is provided for shifting one end of the pin into the helical groove in one of the cylinders at the end of a forward stroke of the guide member, and for shifting the other end of the pin into [51] Int. [58] FieldofSearch.....................

References Cited the helical groove in the other of the cylinders at the end of the reverse stroke of the guide member.

4 Claims, 10 Drawing Figures m m a f Ea SG 379 266 999 uww Mum 275 746 133 ill ll ll ll llllll'lllll llllll ll] 1 llllllllll] PATENTEDMAT 9 I972 3, 661 O 1 9 sum 1 OF 2.

l V I I/ gose KACALEK ATTORNEY PATENTEDMAY 9:972 3,661,019

SHEET 2 OF 2 /NVENTORS'- ma/Q ATTORNEY DEVICE FOR TRANSFORMING A ROTARY MOTION INTO A LINEAR REVERSING MOTION, PARTICULARLY FOR TEXTILE MACHINES The present invention relates to a device for transforming a rotary motion into a linear reversing motion; it is particularly useful for textile machines, as e.g., winding, twisting, texturing and similar machines.

Many devices are known for transforming rotary motion to linear motion, of which, however, only a few are applicable to textile machines. Most frequently, winding drums, winding eccentrics, winding cylinders with reverse grooves or even two winding cylinders with reversing helical grooves, in which the crossing points are mutually overset, are known.

The winding drums are used for winding classical materials, e.g. cotton. They can also be used for winding textured yarns from synthetic fibers. The advantage of the winding drums consists in that they are simple in their construction and thus operate without failures; on the other hand, however, they have also disadvantages consisting particularly of the fact that they are not suitable for winding smooth and fine yarns of synthetic fiber because it is impossible to shorten the winding strokes for forming inclined front surfaces on windings; such windings are used when the yarn is to be further processed, as, for example, in knitting machines.

Winding eccentrics are used particularly for precise cross winding machines for synthetic yarns, in which also the winding stroke can be shortened; this device thus meets the requirements as to the shape and construction of the winding. The disadvantage of such device consists in that when a winding 200 to 250 mms long is required, which is a usual requirement in view of the present winding speeds, a winding eccentric of large size must be used. This, however, prevents the achievement of the necessary operating speed, as well as the necessary high frequency of reciprocation of the yarn guide, in view of the considerable mass of the reciprocating parts.

Winding cylinders with a reverse helical groove may also be used in the same cases as the above-described eccentric. The said winding cylinders overcome the main disadvantages of the winding eccentrics. In the present state of the art, these devices are most suitable as sources of linear reverse motion, and are also most frequently used. The dimensions of this device are advantageous as compared with those of the dimensions of the winding eccentric, and by means of the said device higher winding velocities and a higher frequency of strokes of the yarn guide can be achieved. However, on the other hand, this device also has certain disadvantages compared with the winding eccentric. These disadvantages arise from the fact that the cylinder is provided on its surface with a groove having a left and a right pitch, thus causing the presence of socalled crosses upon mutual intersection of the said grooves. For that reason, it is impossible to make the groove as a simple one, as in the case of the winding eccentric; thus the groove must be made doubled, i.e., e.g. two grooves above each other, the upper larger and the coaxial, lower groove narrower. In the lower groove there is guided a wing which entrains the slider through the groove crosspoints. It is, however, necessary to alter the configuration of the lower groove at the dead centers, so as to enable the wing to pass the small radius of the dead center; at the dead center the sliding element is guided in the upper wide groove by means of a roller. In the cylinders with grooves made as mentioned above, then the linearily vibrating mechanism which is driven by the wing, is made to oscillate at the crosspoints of the grooves and its operation is unsteady. Moreover, it is necessary to consider that at the dead center the wing passes through the altered groove, this making its movement uncontrollable and causing impacts and vibrations. These disadvantages reduce the accuracy of yarn distribution on the bobbin, and also reduce the operating life of the mechanisms; they cause noisy operation, and make further increase in the frequency of reciprocation of the yarn guide impossible. The wing, as well as the double groove, are also very intricate and expensive from the viewpoint of manufacture.

Another device with two winding cylinders with reversing helical grooves is known, in which the crosspoints of the grooves are mutually overset. That means, that the pitch of the grooves of the two cylinders is not the same, the pitch ratio of the two grooves being an irreducible fraction. This device overcomes the main disadvantage of the winding cylinder with a reversing groove. This device does have, however, an important disadvantage; it is not suitable for a higher frequency of strokes on the winding cylinders, as the mutual interception of the crosspoints would be in this case so imperceptible, that its original purpose would be lost. The most suitable ratio of the pitches of said grooves is, in that embodiment, l.5 2. A further substantial disadvantage, however, consists in that the device is not suitable for windings longer than 200 to 25 0 mms; in view of the number of groove pitches, it is necessary to choose cylinders of larger diameter in view of the pitch of said groove, this making it impossible to achieve in that device the necessary velocities and the necessary frequency of double strokes of the guide. A further substantial disadvantage consists in that the manufacture of grooves on the cylinders is difficult, particularly at the crosspoints, and rather expensive.

The present invention has for its object the overcoming of the disadvantages set out above, thus enabling the achievement of a higher operating speed of the device. In the illustrative embodiment of the device according to the present invention the two winding cylinders are interconnected by a driving transmission, and are provided each with one helical guiding groove. The opposite ends of each groove are situated in opposite directions axially past the respective dead centers. A driving pin in the sliding element alternately engages one of said grooves and then the other, depending upon the instan taneous direction of movement of the sliding element.

Further features of the device according to the present invention are described in the following specification and shown in the accompanying drawings in the form of several embodiments, of which FIG. 1 is a view in plan of a first illustrative embodiment of the device according to the present invention;

FIG. 2 is a view in cross section of the device as shown in FIG. 1, the section being taken along the line 2-2 of FIG. 1;

FIG. 3 is a view in cross section similar to that of FIG. 2, but with another, second embodiment of the grooves;

FIG. 4 is a view in cross section similar to that of FIG. 2, but with another, second embodiment of the sliding element;

FIG. 5 is a view in cross section similar to that of FIG. 4, but with the embodiment of grooves shown in FIG. 3 and with the embodiment of the sliding element shown in FIG. 4;

FIG. 6 is a view in plan of a further embodiment of the device according to the present invention, parts of the apparatus being shown in section;

FIG. 7 is a view in cross section of the device shown in FIG. 6, the section being taken along line 77 of FIG. 6;

FIG. 8 is a view in cross section of the device similar to that of FIG. 7 but with another embodiment of the drive;

FIG. 9 is a view in cross section of the device similar to that shown in FIG. 7 with another embodiment of the sliding element; and

FIG. 10 is a cross section of the device shown in FIG. 6, but with the embodiment of the drive shown in FIG. 8, and with v the embodiment of the sliding element shown in FIG. 9.

Turning first to FIGS. 1 and 2, the device according to the present invention has two parallel winding cylinders l and 2, each cylinder being mounted at each end in bearings as shown. One of the said winding cylinders is connected to a driving power source (not shown). The winding cylinders are provided with identical helical guiding grooves 3, 3' of the same pitch direction. The winding cylinders 1 and 2 are positively geared together to rotate in synchronism and in the same phase by gears 11 and 12. Between the two winding cylinders l and 2 parallel guiding rods 10 and 10' are mounted parallel to cylinders 1, 2. A sliding element 9 is mounted on rods 10, 10'. Element 9 has a transverse bore therein at substantially the center of sliding element 9. A driving pin 8 is slidably mounted in the transverse bore. Pin 8 alternately engages and is linearly driven by groove 3 of winding cylinder 1 and groove 3 of winding cylinder 2. The helical guiding grooves 3 and 3' are made such that their ends are located axially behind the dead centers, i.e. beyond

points

4 and 5 on the cylinder 1 and beyond

points

6 and 7 on the cylinder 2, the end portions of the grooves extending in the direction opposite to that of the main extent of grooves 3 and 3' without intersecting them. In the embodiment shown in FIGS. 1 and 2, the helical guiding grooves 3, 3' become progressively shallower as they approach both

dead centers

4 and 5 or 6 and 7,

respectively, until they reach substantially zero depth at the dead centers. Beyond the dead centers, the grooves progressively increase in depth to their ends, as shown, such end portions extending in opposite axial directions.

According to the variation as shown in FIG. 3, it is, however, also possible that the helical guiding groove 3 of the winding cylinder 1 is of substantially zero depth only at the dead center 4, whereas the helical groove 3' of the winding cylinder is of substantially zero depth at the dead center 7, i.e. a the opposite side. However, it is also possible tochoose the dead center 5 of winding cylinder 1 and the dead center 6 of winding cylinder 2 for the same purpose. In both cases, the reliability of the function performed by the device according to the present invention is maintained.

The device according to the present invention in the embodiment as shown in FIGS. 1 to 3 operates as follows:

The guide 9, provided with a driving pin 8 engaging the helical guiding groove 3 of the rotating winding cylinder 1 is displaced along the guiding rods 10 and 10' by rotation of the winding cylinder 1 in the direction of arrow 5,. As soon as the driving pin 8 reaches the dead center 4 of the helical guiding groove 3, which at this point is directed onto the surface of winding cylinder 1, said pin is transferred by the action of the continuous decrease of depth of groove 3 into the groove 3' of winding cylinder 2, which rotates, due to the direct engagement of gear 12 mounted thereon with gear 11 of winding cylinder 1, which rotates in the opposite direction from cylinder 1. Thereupon the guide 9 is displaced on the guiding rods 10 and 10' by motion of the driving pin 8 in the groove 3' of the winding cylinder 2 in the direction of arrow S Such motion continues as far as dead center 7 of groove 3', where said pin 8 is again transferred, upon continuous shallowing of the groove 3' on winding cylinder 2, to the guiding groove 3 of the winding cylinder 1 and the whole cycle is repeated.

In FIGS. 4 and 5, two variations of the device as shown in FIGS. 1 to 3 are shown; such variations have another embodiment of the guide, there designated 9. The guide 9' is, in both cases as shown in FIGS. 4 and 5, provided on both sides with recesses 18 and 18' of arcuate shape, such recesses receiving the winding cylinders 1 and 2 and replacing the function of guiding rods l0, 10, which thus need not be used. Guide 9' is provided approximately in its center with a transverse bore, in which a driving pin 8 is slidable; pin 8 alternately engages and is linearly driven by the helical guiding groove 3 of winding cylinder 1 and the helical groove 3' of winding cylinder 2.

In the variation of the embodiment as shown in FIGS. 4 and 5, the device operates in generally the same manner as the embodiments of FIGS. 1 to 3, the only difference being that guide 9 is displaced with its arcuate recesses 18 and 18' along the winding cylinders I and 2, the winding cylinders themselves coacting with recesses 18 and 18', serving accurately to guide the guide member 9' in its reciprocation.

The embodiment of the device according to the present invention shown in FIG. 6 is constituted by two winding cylinders I5, 16, mounted with their two ends in bearings and driven from a source of rotary driving power (not shown). The winding

cylinders

15 and 16 are provided with helical guiding grooves 17, 17', respectively, the said grooves having a mutually opposite direction of pitch, i.e. cylinder 15 being provided with a right and cylinder 16 with a left helix, or vice versa. The grooves 17 and 17' are of uniform radial depth in their main courses, as well as in their end portions behind or beyond their

dead centers

19 and 20, and 21 and 22. Such end portions of the grooves extend in a direction opposite to the course of grooves 17 and 17' without intersecting them. Between the winding

cylinders

15 and 16 there are mounted one above the other guiding rods 10 and 10' on which the guide 9 is mounted. The guide 9 is provided approximately at its center with a transverse bore in which a driving pin 8' is slidably mounted. Beside the guiding rods 10 and 10' at the points of

dead center

19 and 22, or 20 and 21, stop members 14 and 14', respectively, are mounted, the stop members being fastened in a housing (not shown) of the whole mechanism. The driving pin 8 is reciprocated between the left hand position thereof, shown at the top in FIG. 6, and a right hand position (not shown) when the guide 9 has reached its lowermost position. For this purpose, the guide 9' is provided with an opening centrally therethrough extending parallel to

cylinders

15, 16. The noses of stop members 14, 14', which are slanted in opposite directions, alternately engage opposite ends of the opening in guide member 9, thereby to reciprocate such member, as described.

The drive in that embodiment is derived from a rotary power source (not shown). Because the winding

cylinders

15, 16 must be driven, in contrast to the preceding embodiment, in the same direction, the drive is made in the manner shown in FIG. 7; a toothed or Timing belt 23 is used for transmitting the motion from the power source to winding

cylinders

15 and 16, said belt partially surrounding a toothed pulley 11" on the winding cylinder 15, as well as a toothed pulley 12" on winding cylinder 16.

In the embodiment shown in FIG. 8, a gear 13 is connected to the rotary driving source, said gear 13 meshing with a gear 11' affixed to winding cylinder 15 and with a gear 12' affixed to winding cylinder 16.

In the embodiment as shown in FIGS. 6 to 8, the device according to the present invention is as follows:

The guide 9 with the drive pin 8', which engages the helical guiding groove 17 of the rotating winding cylinder 15, is displaced on the guiding rods l0, 10' in the direction of arrow S As soon as the driving pin 8' reaches the proximity of the dead center of groove 17 of the winding cylinder 15, its groove 8a comes into contact with stop member 14 which, with its chamfered surface, transfers the driving pin 8' gradually to the opposite side as long as its is at the point of dead center of groove 17 of winding cylinder 15. The driving pin 8' is transferred into the helical guiding groove 17 of the winding cylinder 16, which drives pin 8' together with guide 9 on the guiding

rods

10, 10 in the direction of arrow 8,, as far as the proximity of dead center 21 of guiding groove 17' of the winding cylinder 16. Here the guiding pin 8 touches with its groove 8a the stop member 14 and the whole process is repeated. In that embodiment, the two winding

cylinders

15 and 16 must rotate in the same direction; however, their guiding grooves 17, 17' have opposite directions of pitch, as shown.

The embodiments as shown in FIGS. 9 and 10 are variations of the embodiments as shown in FIGS. 7 and 8. The guide 8', used in FIGS. 9 and 10, is shown in FIGS. 4 and 5. The guide 9 is provided with

recesses

18 and 18 of arcuate shape at its opposite ends. Said guide 9 is mounted on winding

cylinders

15 and 16, which thus replace the guiding rods 10 and 10'. Guide 9' is provided at approximately its center with a transverse bore in which the driving pin 8 is slidably mounted.

In the variations of the embodiment as shown in FIGS. 9 and 10, also, this device according to the present invention operates substantially in the same manner as previously described embodiments. The guide 9' slides with its

arcuate recesses

18 and 18 along the winding

cylinders

15 and 16, which rotate in the same direction (FIG. 9) or opposite (FIG. 10) directions. The driving pin 8 is alternately positioned in the guiding groove 17 of the winding cylinder 1, or in the guiding groove 17 of the winding cylinder 16.

The advantages of the device according to the present invention consist particularly in that the manufacture of cylinders with simple grooves is simpler, the device operates at a lower noise level, and a higher frequency of double strokes can be achieved therewith. This results in an increased lifetime of the whole mechanism. In view of the possibility of manufacturing cylinders of small diameter, it is also possible to use them simultaneously as guideways for the guide.

Although the present invention has been described in conjunction with preferred embodiments, it is to be understood that modifications and variations may be resorted to without departing from the spirit and scope of the invention, as those skilled in the art will readily understand. Such modifications and variations are considered to be within the purview and scope of the invention and appended claims.

What is claimed is:

l. A device for transforming a rotary motion to a reciprocatory linear motion, comprising two transversely spaced parallel rollers, means drivingly to connect the rollers to rotate in synchronism, a helical guiding groove in each roller, a guide member mounted between the rollers for reciprocation parallel thereto, a drive pin mounted on the guide member for reciprocation transversely of the rollers, means for shifting the drive pin at the ends of its strokes so that the pin drivingly engages the groove in one roller during the forward stroke of the guide member and drivingly engages the groove in the other roller during the reverse stroke of the guide member, and means at the longitudinally opposite ends of the device for stopping the guide member at the ends of its operative strokes, the means for shifting the drive pin so that it alternately engages the grooves in the opposite rollers comprising means on the driving pin engaged by the respective stop means at the ends of the operative strokes of the guide member.

2. A device according to claim 1, wherein the drive pin has a passage therethrough directed parallel to the rollers, and wherein the confronting axially inner ends of the stop members are bevelled in opposite directions, the peaks of the stop members being receivable within the passage in the pin whereby to thrust the pin in opposite directions at the ends of successive operative strokes of the guide member.

3. A device for transforming a rotary motion to a reciprocatory linear motion, comprising two transversely spaced parallel rollers, means drivingly to connect the rollers to rotate in synchronism, a helical guiding groove in each roller, a guide member mounted between the rollers for reciprocation parallel thereto, a drive pin mounted on the guide member for reciprocation transversely of the rollers, and means for shifting the drive pin at the ends of its strokes so that the pin drivingly engages the groove in one roller during the forward stroke of the guide member and drivingly engages the groove in the other roller during the reverse stroke of the guide member, the guide member having two oppositely disposed recesses, one at each of its transverse ends, said recesses accurately receiving the respective rollers whereby the rollers guide the guide member in its reciprocation.

4. A device according to claim 3 wherein the recesses have part-circular cylindrical guiding surfaces disposed with their axes parallel to the axes of the rollers, the rollers are of circular cylindrical configuration with the exception of the helical groove in each, and the circular cylindrical surface of each roller accurately engages the surface of the respective recess.

Claims

1. A device for transforming a rotary motion to a reciprocatory linear motion, comprising two transversely spaced parallel rollers, means drivingly to connect the rollers to rotate in synchronism, a helical guiding groove in each roller, a guide member mounted between the rollers for reciprocation parallel thereto, a drive pin mounted on the guide member for reciprocation transversely of the rollers, means for shifting the drive pin at the ends of its strokes so that the pin drivingly engages the groove in one roller during the forward stroke of the guide member and drivingly engages the groove in the other roller during the reverse stroke of the guide member, and means at the longitudinally opposite ends of the device for stopping the guide member at the ends of its operative strokes, the means for shifting the drive pin so that it alternately engages the grooves in the opposite rollers comprising means on the driving pin engaged by the respective stop means at the ends of the operative strokes of the guide member.