US1957394A

US1957394A - Bobbin-winding machine

Info

Publication number: US1957394A
Application number: US599505A
Authority: US
Inventors: Heinitz Woldemar
Original assignee: Schubert und Salzer Maschinenfabrik AG
Current assignee: Rieter Ingolstadt Spinnereimaschinenbau AG
Priority date: 1931-08-06
Filing date: 1932-03-17
Publication date: 1934-05-01
Anticipated expiration: 1951-05-01

Description

May 1, 1934. w. HEINITZ BOBBIN WINDING MACHINE Filed March 17, 1932 2 Sheets-Sheet [27 1 6 1110/": l 0/ae/7/ar #8121112 y 1934. w. HEINITZ 1,957,394

BOBBIN WINDING MACHINE Filed March 17, 1932 2 Sheets-$heet 2 Patented May 1, 1934 SAT ES BOBBIN-WINDING MACHINE Woldemar Heinitz, Chemnitz, Germany, assignor to Schubert & Salzer Maschinenfabrik Aktiengesellschaft, Chemnitz, Germany Application March 17, 1932, Serial No; 599,505

' in Germany August 6, 1931 2 Claims.

My invention relates to bobbin-winding machines and more particularly to a thread-guide control for such machines in which the thread guide is moved independently of the bobbin, i. e., without bearing on the bobbin or being operated by the thread to be wound.

It is an object of my invention to provide an improved thread guide control which is absolutely reliable, practically without wear, is readily accessible and adjustable while the machine is in operation, and suffices practically for all yarn thicknesses.

To this end, instead of the usual ratchet mechanisms for controlling the thread guide, I provide a control having transmitting members adapted to become active on the control in conformity with the thickness of the yarn being wound.

The usual ratchet mechanisms for periodically rotating a ratchet wheel while the thread-guide plate reciprocates so as to move the thread guide along a threaded spindle, must be adjusted in conformity with the yarn thickness. For thin yarn the ratchet wheel is moved for fewer teeth per cycle than for thick yarn. This involves the drawback that it is not always feasible to adjust the pawls during the operation of the machine with the rapidity, reliability and exactitude required, for it is diflicult to count the number of teeth to be operated per cycle of the threadguide plate, particularly as with thick yarns often two pawls are provided and each pawl requires individual adjusting. Providing two pawls in a ratchet control increases the diificulties of operation but still does not always enable the machine to handle all yarn thicknesses.

Another difficulty is that the pawls must be locked while in active position. This is often neglected by the operators so that the pawls are thrown out by the vibrations of the machine.

Still another difiiculty is the arrangement of the means for adjusting the pawls. If the means is readily accessible it interferes with the functions of the operator while if it is placed in a non-interfering position it is difficult to get at and the difficulty is increased by its partaking in the reciprocation of the thread-guide plate.

An inherent defect of all ratchet controls is the liability to overthrowing at high speeds.

According to my invention ratchet mechanisms are eliminated altogether and replaced by means such as a driving and a driven part in combination with transmitting means which are adapted to move into and out of active position with respect to the driven part. Such transmitting mem- Y bers may be the pins of a mangle gear which are shiftably mounted in a disk so that they may be moved into and out of active position with respect to the notches in a mating wheel.

Preferably locking means are provided for holding the parts insuch position that they are ready to be properly re-engaged by the transmitting members.

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

In the drawings Fig. 1 is a partly sectional elevation, and

Fig. 2 is a front-end elevationof the machine, viewed from the left in Fig. 1,

Fig. 3 is a plan view of its mangle gear,

Fig. 4 is an elevation showing a portion of the pin disk of the mangle gear, drawn to a larger scale,

Fig. 5 is a section on the line V-V in Fig. 4,

Figs. 6 and 8 show the locking means referred to in elevation and in two positions, and

Figs. 7 and 9 are plan views of Figs. 6 and 8, respectively.

Referring now to the drawings, a is the frame of the machine, 4 is its driving shaft, 5 is a vertical friction disk on the driving shaft, and 3 is a horizontal friction disk of smaller diameter on the vertical shaft 1 of a conical (or bottle) peg or pirn 2 whichhorizontal disk 3 bears on the vertical disk 5 by gravity.

10 is the control shaft to which rotation is imparted by reduction gearing 6, '7, 8, 9. 11 is a cam on the shaft 10. 12 is a push rod with a roller 13 at its lower end for cooperation with the

cam

11 and 14 is the thread-guide plate at the upper end of the push rod 12. 15 is a threaded spindle on the thread-guide plate which extends in parallel to the vertical shaft 1. 16 is a spur gear which is mounted on the spindle 15 with its internally threaded hub, and 17 is a thread guide on the hub. The thread is indicated in dot-anddash lines in Fig. 1. 1

18 is an elongated pinion or serrated shaft which is mounted in a bearing 19 on a bar 20 of the frame a and extends in parallel to the threaded spindle 15 and the vertical shaft 1. Rotation is imparted to the pinion 18 by bevel gearing 21, 22 and a control shaft 23.

34 is a sprocket on the outer end of the control 24 is a control disk on the outer end of the

cam shaft

10, and 25 are shiftable pins, for instance thirty, in the control disk which, together with the notched wheel 29 on the pin 31, constitute a mangle gear. Means are provided for holding the pins 25 in two final positions as shown in Figs. 4 and 5. The disk 24 has a peripheral groove 28 in which is inserted an annular coiled spring 27. Each pin has two grooves 26 and 26' which are adapted to be engaged by the spring 27 so as to retain the pins 25 in two positions with respect to the disk 24 and the wheel 29. Those pins which project from the outer face of the disk as shown for five pins in Fig. 3, will not operate the wheel 29, while those pins which project from the inner face of the disk 24, with the spring 2'7 engaging the groove 26, operate the notched wheel 29, as shown for four of them Fig. 3. Obviously, the coiled spring 27 might be replaced by a band of rubber or the like.

The locking mechanism illustrated in Figs. 6 to 9 has been omitted in Figs. 1 and 3 for the sake of clearness. In Figs. 6 and 8 those pins 25 which are inactive with respect to the notched wheel 29 are shown black and those which are in active position are shown white. In the example illustrated, 15 out of the 30 pins are inactive (black) while the other 15 are active (white). 35 is a ratchet wheel on the boss of the notched wheel 29, and 3'? is a pawl which is fulcrumed in the frame a at 36 and provided with a tooth for engaging between the teeth of the ratchet wheel 35 and with a'cam 39 adapted to be engaged by the inactive (black) pins 25. These pins hold the tooth 38 engaged with the ratchet Wheel 35 as shown in Fig. 8, while when the active (white) pins meet the cam 39 the pawl is released and forced out of the interstices between the teeth of the ratchet wheel 35 by the reaction of their sloping flanks. 40 is a circular check plate in a cavity or" the disk 24 which supports the back of cam 39 in the thrown-out position of the pawl, Fig. 6, and prevents overthrowing of the pawl.

In operation, if all pins 25 are in active position, i. e., project from the rear face of the disk 24, the notched wheel 29 performs a complete revolution per revolution of shaft 10 and disk 24 and consequently per cycle of the thread-guide plate 14. The rotation of the notched wheel 29 is transmitted to the elongated pinion 18 through the means described, feeding the thread guide 17 continuously on the spindle 15. This operation corresponds to the maximum velocity of the thread guide 17 required for the thickest yarns.

If a given number of pins 25 are inactive the wheel 29 partakes in the rotation of the disk 24 only while these pins engage its notches so that the thread guide 1'] moves only during portion of its reciprocation and is intermittently raised on the threaded spindle 15.

It will be understood that by the means described the movement of the thread guide is accelerated or retarded as desired. Tables may be calculate-cl for the number of pins 25 which must be in active position for a definite yarn. instance, when winding artificial silk, the first and the second pins 25 are moved into active position with respect to the wheel 29 if the silk has 30 deniers (a denier is the weight of a thread 10,000 metres long, expressed in grammes). If the silk has 40 deniers the first to fourth pins, if it has 50 deniers, the first to fifth pins, and if it has 120 deniers the first to twelfth pins 25 will be moved into active position, etc. Preferably the pins 25 are numbered so that they may be adjusted rapidly while the machine is in operation.

The great superiority of my control for winding comparatively thick yarns is that a complete revolution of the wheel 29 is available for the movement of the thread guide during a complete cycle of the thread-guide plate 14, which is not practicable in machines having ratchet mechanisms, and therefore the range of my novel control includes practically all yarn thicknesses.

The movement imparted to the thread guide 17 by my novel control is absolutely exact as the cam 39 while retained by the black pins 25 which are in inactive position, holds the ratchet wheel 35, and thereby the wheel 29, exactly in the position required for causing the next white pin 25 to properly enter the corresponding notch in the wheel 29. Conversely, if the last white pin 25 has moved out of engagement with the wheel 29 the first black pin engages the cam 39 of the pawl 37, throwing the tooth 38 into the ratchet wheel 35 and holding the wheel 29 exactly in the proper position for re-engagement by the next white pin.

' I claim:-

1. In a bobbin-winding machine, a thread guide, a rotary peg for a bobbin, mechanism for moving said thread guide along said peg, means for varying the relative position of said thread guide and said mechanism including a driving disk carrying longitudinally displaceable pins, means for retaining said pins in adjusted positions on the disk, 2. gear wheel driven by the pins of said disk and operatively connected to said position-varying means, a ratchet wheel connected to said driven gear and a pawl for intermittently locking said gear, said pawl having a cam adapted to cooperate with the pins of said disk and a locking head adapted to engage in.

the teeth of said ratchet wheel.

2. In a bobbin-Winding machine, a thread guide, a rotary peg for a bobbin, mechanism for moving said thread guide along said peg, means for varying the relative position of said thread guide and said mechanism including a driving disk carrying longitudinally displaceable pins, said displaceable pins having each a pair of spaced circumferential grooves and said driving disk having a peripheral groove accommodating an annular spring engaging one of said grooves of each of said pins for retaining said pins in the adjusted position, a gear wheel driven by the pins of said disk and operatively connected to said position-varying means, a ratchet wheel connected to said driven gear and a pawl for intermittently locking said gear, said pawl having a cam adapted to cooperate with the pins of said disk and a locking head adapted to engage in the teeth of said ratchet wheel.

WOLDEMAR HEINITZ.