US2009922A - Thread-guide control for bobbinwinding machines - Google Patents

Description

July 30, 1935. w. HElNlTz 2,009,922

THREAD GUIDE CONTROL FOR BOBBIN WINDING MACHINES Filed March 17, 1932v 3 Sheets-Sheet 2 July 30, 1935. w. HElNlTz '21,009,922

THREAD GUIDE CONTROL FOR BOBBIN WINDING MACHINES Filed March 17,1932 5 Sheets-Sheet 3 Patented July 30, 1935 PATENT OFFICE THREAD-GUIDE CONTROL FOR BOBBIN- WINDING MACHINES Woldemar Heinitz, Chemnitr, Germany, assignor to Schubert Salzer Maschinenfabrik Aktiengesellschaft, Chemnitz, Germany Application March 17, 1932, Serial No. 599,504 In Germany April 30, 1931 2 Claims.

My invention relates to thread-guide controls for bobbin-winding machines.

It is an object of my invention to provide a control for the winding of conical or bottle bobbins in which the bobbin consists of individual layer sets, which is more adaptable than the usual control. To this end, in combination with mechanism for moving a thread guide along a peg, I provide means for temporarily reversing the direction in which the mechanism operates. By these means I obtain superimposed layer sets which are not uniform but partly cross-wound, without additional undulation.

In a preferred embodiment of my invention I equip the usual cam for reciprocating the threadguide plate with steps, so that the reciprocation of the thread-guide plate is-temporarily reversed by the steps.

In the drawings amxed to this specification and forming part thereof a control embodying my invention is illustrated diagrammatically by way of example.

In the drawings Fig. 1 is a sectional elevation of a control having a cam according to the invention,

Fig. 2 is a front end elevation of the control, viewed from the left in Fig. 1, and

Fig. 3 is a plan view of the control.

Fig. 4 is an elevation of a bottle bobbin,

Fig. 5 is an elevation of a conical bobbin, and

Fig. 6 is a diagram drawn to a larger scale and showing the winding ofthe bottle bobbin in Fig. 4.

Referring now to the drawings and rst to Figs. 1 to 3, A is the frame of the machine, 4 is its driving shaft, 3 is a vertical friction disk on'the driving shaft, and 2 is a horizontal friction disk of smaller diameter on the vertical shaft I of a conical peg or pirn B, which horizontal disk 2 bears on the vertical disk 3 by gravity.

9 is the control shaft to which rotation is imparted by reduction gearing 5, l, 6, 8, I0. The wheels of the reduction gearing are disposed in a plane which is in front of the plane on which Fig. 1 is sectioned and are therefore shown as circles in dot-and-dash lines. I I is a cam on the shaft 9, I 2 is a push rod with a roller at its lower end for cooperation with the cam and I3 is the threadguide plate at the upper end of the push rod 2. I4 is a threaded spindle on the thread-guide plate, I5 is a spur gear which is mounted on the spindle I4 with its internally threaded hub, and I6 is a thread-guide on the hub. The thread is indicated in dot-and-dish lines in Fig. l.

3| is an elongated pinion or serrated shaft which is mounted in a bearing on a bar extending longitudinally along the top of the frame A and extends in parallel to the threaded spindle I4. Rotation is imparted to the pinion 3| by bevel gearing 29, 30 and a shaft 21.

28 is a sprocket on the outer end of the shaft 5 21, 32 is a sprocket of equal diameter on the boss of a ratchet wheel 24 which is mounted to rotate on a pin 2|I and 26 is a chain on the two sprockets.

Il is an eccentric on the control shaft 9 and I8 is its rod. The rod I8 engages a pin in the slotted free end of a. lever I9 which is mountedl to rock about a pin 2|. 20 is a short arm extending from the lever I9, 23 is a ratchet pawl on the free end of arm 20 which engages in the ratchet wheel 24, and 22 is a threaded check for adjusting the pawl 23.

As the control shaft 9 rotates the lever I9 and the arm 20 are rocked about the pin 2| by the eccentric Il, imparting intermittent rotation to the ratchet wheel 24. The rotation is transmitted to the pinion 3| by the sprockets, chain and bevel gears described. Rotation of the pinion` 3| causes the spur gear I5 to rotate and to move along the thread of the spindle I4. The amount through which the spur gear and the thread guide I6 are displaced on the spindle 40 is regulated inv conformity with the thickness of the thread by adjusting the teeth 23 through the medium of the check 22 so that the ratchet wheel 24 is rotated through a. corresponding number of teeth per stroke of the arm 20.

As shown in Fig. l the cam II has a uniform rising curve extending through an angle b and a trailing curve extending through an angle c which is stepped at d, e, f, and g. The uniform rising curve is limited at one end by the longestv radius R and at the other end by the shortest radius r of the cam. The radii are determined in conformity with the length a of a layer on the o peg B, Fig. 6. rPhe radial distances of the steps d, e. f. y of the cam from the center of the shaft 9 progressively decrease from the highest point of the uniform rising curve to the lowest point of said curve. That is to say, the radius of 45 step d is greater than that of step e. the radius of step e is greater than that of step f, and the radius of step f is greater than that of step g.

In Fig. 4 the length a is shown on a bottle peg C, and in Fig. 5 it is shown on the conical peg B illustrated in Fig. 1.

The control shaft 9 and the cam I rotate anticlockwlse as indicated by the arrow in Fig. l, reciprocating the push rod I2 and the thread# guide plate I3. Fig. i shows the position of the cam II in which the shortest radius r is in line with the axis of the push rod I2. 'Ihe push rod is now raised gradually and uniformly by the rising curve corresponding to the angle b until the longest radius R is in line with the axis of the push rod I2; 'I'he movement of the thread guide I6 is the resultant from the movement imparted to it by the radius R-r and the movement it performs on the threaded spindle Il while being rotated by the pinion SI and its spur gear I5. Uniform movement of the thread guide through the distance a winds a layer on the peg which has parallel and uniform helical windings as shown for the bottle peg C in dotted lines in Fig. 6. This uniform layer is completed when the thread guide I6 has arrived at the upper end of its stroke a. The stepped trailing curve corresponding to the angle c nowcooperates with the roller at the lower end of the push rod I2 while the push rod descends by gravity. The cooperation of the stepped trailing curve with the push rod I2 effects a movement of the thread guide I6 to a certain amount in one direction and a smaller amount in the reverse direction, that is to say, a so-called pilgrim movement.

The effect of this pilgrim movement is that uni-` form windings are formed while the cam II rotates from the end of the longest radius R to the first step d by which the descent of the push rod I2 is temporarily reversed into an ascending movement, as indicated by the zig-zag line at d in Fig. 6. This results in cross-windings for the range of the step d. At the end of the step d the push rod continues its descent until it is reversed again by the second step e, and so on, until finally theshortest radius r is again in line with the axis of the push rod I2 and the cycle is completed. It will appear that at each step a small additional movement is superimposed on the uniform movement of the thread guide. In this manner the pilgrim movement of the thread guide I6 is obtained, that is to say, the movement of said thread guide I6 is temporarily reversed and cross windings are formed. Fig. 6 includes a diagram showing the small additional reversing movements imparted by the steps d, e, f, g and the cross windings resulting therefrom. The reversing movement is indicated by the zig-zag arrow.

l. In a thread guide control for bobbin-winding machines, a thread guide, a rotary peg forv a bobbin, a main shaft driving said peg, a cam shaft driven by said main shaft, a cam on said cam shaft having a uniformly shaped rising curve and a trailing curve, said rising curve during the rotation of said cam' imparting a uniform and complete upward stroke to said thread guide. a plurality of steps formed in said trailing curve the radial distances of which from the center of Said cam shaft progressively decrease from the highest towards the lowest point of said uniformly shaped curve whereby a descending stroke with a Pilgrim movement will be transmitted to said thread guide, each irregular traversing movement effected by said descending stroke being of an upward stroke less than that of the complete upward stroke of the thread guide effected by said uniformly rising curve of said-cam and a downward stroke less than that' of each upward stroke and means driven by said cam shaft for varying the position of said thread guide relative to its position caused by said cam.

2. In a winding machine for producing conical or bottle bobbinswith overlapped or interlocked layers of thread comprising in combination a rotary peg, a thread guide associated therewith, a driven shaft for rotating said peg, a cam carried by said shaft, means for operatively connecting said thread guide with said cam, said cam having a uniformly shaped rising curve and a trailing curve for imparting traversing strokes to said thread guide whereby upon each revolution of said cam said rising curve will impart a uniform and complete upward stroke to said thread guide and said trailing curve permitting descending strokes for producing layers of thread of different sizes, a plurality of steps formed in said trailing curve whereby during each descending stroke of said thread guide irregular traversing movements will be transmitted to said thread guide over each layer of threads so formed as to produce the overlapped or interlocked layers of thread in each layer, each irregular traversing movement o f the thread guide being of an upward stroke less than that of the complete upward stroke of the thread guide and that of each proceeding irregular traversing movement and the down stroke of each irregular traversing lmovement being greater than that of the proceeding traversing movement and less than that of the completed down stroke of the thread guide, and means operatively connecting said driven shaft with said thread guide to vary the position of the latter with respect toits positions caused by said cam.

WOLDEMAR EEINITZ.

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