US3316700A - Builder motion for roving frame - Google Patents

Builder motion for roving frame Download PDF

Info

Publication number
US3316700A
US3316700A US40966964A US3316700A US 3316700 A US3316700 A US 3316700A US 40966964 A US40966964 A US 40966964A US 3316700 A US3316700 A US 3316700A
Authority
US
United States
Prior art keywords
bobbin
traverse
feed mechanism
clutch
alternately
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
Other languages
English (en)
Inventor
Ronald C Mason
Jr William B Strzelewicz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Whitin Machine Works Inc
Original Assignee
Whitin Machine Works Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Whitin Machine Works Inc filed Critical Whitin Machine Works Inc
Priority to US40966964 priority Critical patent/US3316700A/en
Priority to US40989964 priority patent/US3317800A/en
Priority to US40991664 priority patent/US3316701A/en
Priority to DE19651535026 priority patent/DE1535026A1/de
Priority to CH1545065A priority patent/CH447754A/de
Priority to GB5566667A priority patent/GB1121042A/en
Priority to GB4755065A priority patent/GB1121041A/en
Application granted granted Critical
Publication of US3316700A publication Critical patent/US3316700A/en
Assigned to CONGRESS FINANCIAL CORPORATION reassignment CONGRESS FINANCIAL CORPORATION SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). AGAINST PATENTS & TRADEMARKS Assignors: LESCATH CORPORATION
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • D—TEXTILES; PAPER
    • D01—NATURAL OR MAN-MADE THREADS OR FIBRES; SPINNING
    • D01H—SPINNING OR TWISTING
    • D01H1/00—Spinning or twisting machines in which the product is wound-up continuously
    • D01H1/14—Details
    • D01H1/36—Package-shaping arrangements, e.g. building motions, e.g. control for the traversing stroke of ring rails; Stopping ring rails in a predetermined position
    • D01H1/365—Package-shaping arrangements, e.g. building motions, e.g. control for the traversing stroke of ring rails; Stopping ring rails in a predetermined position for flyer type

Definitions

  • a roving frame having bobbins and fliers, cone pulleys connected by a belt, a belt shipper for moving the belt axially of the pulleys, an air cylinder, ratchet, and rack for moving the shipper, and counterrotating electrically-operated clutch means for reciprocating the bobbins.
  • This invention relates to frames for paying off a filamentary material from a feed mechanism and winding the material onto a bobbin to form a package of the material on the bobbin.
  • the conventional design gives rise to a harsh, noisy action of the contact shaft, which must be suddenly geared into a high-speed rotating shaft (the top cone shaft) and suddenly stopped after only half a revolution with much noise and shock to the skip gear, contact dogs, builder nuts, and contact shaft.
  • the front roll speed of the conventional frame must be limited to about 300 rotations per minute, because the skip gear does not mesh properly with the top cone bevel gear at speeds greater than that.
  • An object of the present invention is to remedy the shortcomings of the conventional apparatus pointed out above.
  • an object of the present invention is to employ the cushioning effect of a compressible fluid in moving the cone-pulley-belt guide, in order to minimize noise and shock.
  • a further object of the invention is to provide for positive holding of the rail during rail reversal t0 eliminate the period of no drive during rail reversal.
  • Another object of the invention is to provide a builder mechanism which operates independently of frame speed, thereby permitting front roll speeds substantially in excess of 300 rotations per minute.
  • Another object of the invention is to provide a frame which can be stopped safely from an operational point of view in any position of rail travel.
  • control means for limiting at least one of (a) the rotational velocity, (b) the traverse velocity, and (c) the traverse length to values w, v, and l respectively.
  • the control means preferably comprises a pneumatic piston-cylinder assembly, means for actuating the piston-cylinder assembly at intervals to produce an output, and means coupling the output to the drive means to alter at least one value limited by the control means.
  • FIG. 1 is a fragmentary, sectioned view of one form of accordance with the invention
  • FIG. 2 is an enlarged perspective view of a portion of the apparatus of FIG. 1;
  • FIG. 3 is a schematic diagram of an electric circuit constituting .one of a number of possible means adapted to instrument the apparatus of the present invention.
  • FIG. 1 shows drive means 10 connected by suitable linkages H, 12 to a top cone pulley i4 and a flier 16, respectively, to rotate the top cone pulley 14 at constant speed and the flier at constant speed.
  • the top cone pulley M is connected to a bottom cone pulley 18 by a cone pulley belt 20 extending therebetween and tightly drawn thereabout so that the rotation of the top cone pulley 14 in the direction indicated by the arrow associated with the top cone pulley 14 is effective to rotate the bottom cone pulley 13 in the direction indicated by the arrow associated with the bottom cone pulley 18.
  • the top cone pulley 14 is tapered, either linearly as shown or non-linearly, so that its diameter perpendicular to its axis of rotation adjacent to its base 22 (the conefrustum base to the left as seen in the figure) is larger than the corresponding diameter adjacent to its base 24.
  • the bottom cone pulley 18 is tapered, either linearly as shown or non-linearly, and has a large base 26 and a small base 27. The bottom cone pulley is arranged, however, with its large base 26 to the right of its small base 27 as seen in the figure rather than to the left.
  • a cone-pulley-belt guide or shipper 28 envelops a por tion of the belt 20 to guide the belt 20 and move it longitudinally of the axes of the upper and lower cone pulleys 14, 18.
  • the cone pulleys 14, 13 and the belt 20 constitute a variable-mechanical-advantage means and that, for example, when the belt 20 is moved to the left as indicated in FIG. 1, the rotational speed of the lower cone pulley 18 increases and that, when the belt 20 is moved to the right as seen in FIG. 1, the rotational speed of the lower cone pulley 18 decreases.
  • the flier 16 is made to rotate, as noted partly-schematic, partlyapparatus constructed in above, by the drive means at a constant speed.
  • the bobbin 30, being connected to the lower cone pulley 18 by suitable linkages 32, 33, rotates in the same direction in which the flier 16 rotates but more rapidly than the flier 16.
  • the feed mechanism and bobbin thus rotate with respect to each other at a rotational velocity w.
  • the tangential speed of the package would become excessively great, except for the fact that the rotational speed of the bobbin 30 decreases with each successive traverse as the belt 20 moves to the right as seen in FIG. 1. Also, in order to provide the tapered bobbin shape indicated at t, the length of each successive traverse is preferably decreased.
  • the belt shipper 28 has formed thereon a rack 34 adapted to be driven by gearing 36 which is in turn actuated by a ratchet 38 under the control of a piston rod 40 of a piston-cylinder assembly 42.
  • the directions of rotation of the gears constituting the gearing mechanism 36 are shown by appropriate arrows in FIG. 2.
  • Movement of the piston 43 in the opposite directioni.e., to the left as seen in FIG. l has no effect on the location of the belt 20 longitudinally of the axes of the cone pulley 14, 18, inasmuch as the ratchet 38 is free wheeling in response to such movement of the piston 43.
  • the piston 43 of the piston-cylinder assembly 42 is actuated by an air supply line 44 and an air exhaust line 46 communicating with a shiftable valve 48 under the control of a solenoid 50 and spring 54.
  • the valve 48 moves to the position shown in response to energization of the solenoid 50.
  • the air supply line 44 communicates through a passage 45 in the valve 48 with a line 52 for moving the piston 43 of the piston-cylinder assembly 42 to the right as seen in FIG. 1 and performing an indexing function-Le, shifting the cone guide 28.
  • a line 58 communicating with a passage 47 in the valve 48 permits the exhaust of air from the right-hand end of the cylinder to the exhaust line 46.
  • the air supply line 44 is connected through a passage 56 in the valve 48 with the line 58 to the right-hand end of the pistoncylinder assembly 42 to drive the piston of the pistoncylinder assembly to the left as seen in FIG. 1.
  • the left-hand end of the piston-cylinder assembly 42 is connected to a passage 60 in the valve 48 to permit exhaust of air in the left-hand end of the piston-cylinder assembly 42 through the exhaust line 46.
  • Flow-control valves 61, 61' (FIG. 2) control the speed of the piston 43 and prevent shock loads.
  • An air pressure switch 63 stops the frame from operating if the air pressure in the mill falls below a safe builder operating pressure-usually about 40 pounds per square inch.
  • the solenoid 50 is shown also in FIG. 3. As that figure shows, the indexing solenoid 50 is energized when 1 contacts CR-1 are closed, inasmuch as the contacts CR-l and solenoid 50 are in series between lines 62, 64, across which a DC. control voltage is applied.
  • the contacts CR-l are in turn closed when a builder relay CR is energized. Provision may be made to energize the builder relay at either end of the relative traverse of the feed mechanism or flier 16 and bobbin 30 with respe'ct to each other, but provision is preferably made for energizing the builder relay CR at each end of the relative traverse of the feed mechanism 16 and the bobbin 30 with respect to each other. To this end, the builder relay CR is connected by a pair of normally-open contacts LR-3 to a line 66 and by a pair of normallyclosed contacts LR-4 to a line 68.
  • the lines 66 and 68 extend between the control-voltage leads 62 and 64 and therefore provide means for energizing the relay coil LR-R and reset coil LR-L, respectively, of a building latching relay 74.
  • the relay coil LR-R of the latching relay 74 is energized upon closing of a first section 76 of a builder switch 77, and the reset coil LR-L is energized upon closing of a second section 78 of the builder switch 77.
  • the first and second sections 76 and 78 of the builder switch 77 are in turn closed at opposite ends of the relative traverse of the flier 16 and bobbin 30 with respect to each other by contact of first and second contact dogs 80 and 82 with a third contact dog 84 (FIG. 1).
  • the contact dogs 80 and 82 are mounted on builder nuts 86 and 88, respectively, which are in turn threadedly engaged with a rotatable screw 90 having a lower portion 92 threaded oppositely to an upper portion 94 and a topmost portion 90 square in cross section so as to be rotatable by a gear train 130.
  • the nuts 86, 88, screw 90, and contact dogs 80, 82 are mounted on support means 96 rigidly retained on a bobbin rail 98 on which is also mounted the bobbin 30.
  • the bobbin rail 98 is made to reciprocate upwardly and downwardly, so that a relative traverse of length l and at velocity v of the feed mechanism or flier 16 and bobbin 30 with respect to each other is established.
  • the means for establishing the relative traverse includes a rail lifter 100 having thereon a rack 101 engaged with a train of gears 102 connected to a shaft 104.
  • the shaft 104 in turn is driven through -a reversible clutch mechanism 105 having clutches 106, 107 which are driven respectively by a pair of bevel gears 110, 114.
  • the gears 110 and 114 rotate in opposite directions with respect to each other, inasmuch as they are coaxial and are driven by a bevel gear 112 in constant engagement with the gears 110, 114 and having its axis normal to the axes of the gears 110, 114.
  • the gear train 32 is driven by the lower cone pulley 18 at a speed depending on the location of the belt 20. Inasmuch as the lower cone pulley 18 always turns in the same direction, the gear train 32 and the bevel gears 108, 112 also always turn in the same direction.
  • the shaft 104 turns in one direction or the other and, through the gear train 102 and the rack 101 and lifter element 100, reciprocates the bobbin rail 98 and the bobbin 30 upwardly and downwardly.
  • energization of the clutch 106 causes the bobbin rail 98 to move downwardly and energization of the clutch 107 causes the rail 98 to move upwardly.
  • a brake 116 is provided for immobilizing the shaft 104 and hence the bobbin 98 in the event of failure of both clutches, such as might occur during power failure.
  • the brake 116 is electrically held open; under power-off conditions, the brake is spring set.
  • the clutches 106 and 107 are preferably electrically operated by the circuit shown in FIG. 3.
  • the clutch 107 is energized to cause the bobbin rail 98 to move upwardly when normally-open contacts LR-l are closed between D.C. leads 118 and 120.
  • the rail-down clutch 106 is energized to move the rail 98 downwardly when the normally-closed contacts LR-2 are closed between the same two leads 118 and 120.
  • the currentdelay characteristics inherent in the electric reversing clutches insure adequate holding power during rail reversal. Thus, rail run overs are eliminated.
  • All of the contacts LR-l, LR-2, LR-3, and LR-4 are under the control of the builder latching relay 74.
  • the coils LR-R and LR-L of the latching relay 74 are adapted to be alternately energized, and the latching relay 74 is constructed in such a manner that, regardless of whether the relay coil LRR or the reset coil LRL is energized, all four of the contacts LR-l, LR2, LR3, and LR4 are reversed and remain in their new states until energization of the other of the coils LRR and LRL.
  • the contacts LR-1, LR-2, LR-3, and LR-4 are directly attracted by the electromagnet of the relay coil LR- R.
  • Energization of the coil LRR therefore magnetically moves the contacts LR-1, LR2, LR3, and LR4 to their magnetically-caused states, in which states they are mechanically held by mechanical holding means represented at 121, regardless of whether the relay coil LR-R remains energized.
  • the electromagnet of the reset coil LRL does not act directly on the contacts LR-l, LR2, LR3, and LR4 but acts, instead, on the mechanical holding means 121 to release the mechanical holding means 121 and permit the contacts LR-ll, LR2, LR3, and LR- 4 to return to their normal or mechanically-caused states shown in FIG. 3.
  • the holding means 121 provides a memory to prevent the rail 98 from going in the Wrong direction on start-up after the frame has been stopped for any reason.
  • Times t and t are of substantially equal duration and times t and L; are of duration substantially equal to each other and substantially exceeding the duration of times t and 2
  • the contacts LRI in their closed state facilitate the performance of a first function such as energizing the rail-up clutch 187 to cause the rail 98 to move upwardly
  • the contacts LR2 in their closed state facilitate the performance of a second function such as energizing the rail-down clutch 106 to cause the rail 98 to move downwardly
  • the contacts CR-l in their closed state facilitate the performance of a third function such as energization of the solenoid 50 to index the guide or shipper 28.
  • FIG. 3 illustrates the case where the reset coil LRL was the last to be energized, so that all contacts LR-l, LR2, LR3, and LR-4 are shown in their normal or mechanically-caused states.
  • the contacts LR2 are closed, energizing the rail-down clutch 106 and causing the bobbin 30 to move downwardly with respect to the flier 16.
  • the contact dogs 82 and 84 engage each other, closing the switch 76 shown in FIG. 3. This closing of the switch 76 energizes the relay coil LRR and reverses all of the contacts LR-l, LR Z, LR3, and LR 4.
  • the contacts LR-l are therefore closed, energizing the rail-up clutch, and contacts LR2 are open, de-energizing the rail-down clutch, so that the rail begins to move up.
  • the delay characteristic referred to above eliminates run over of the rail 98 during the reversal of traverse motion.
  • the contacts LR-3 close, completing a circuit through the switch 76, the contacts LR3, and the builder relay CR. This causes the contacts CR1 under the control of the builder relay to close, indexing the indexing solenoid 50.
  • the indexing of the solenoid 5t shifts the piston of the piston-cylinder assembly 42 in the manner noted above to move the cone guide belt shipper 28 to the right through the gear train 36, as shown in FIG. 1.
  • a gear train 130 is actuated by movement of the rack 34 to turn the rod 90 and bring the nuts 86 and 88 closer together to shorten the succeeding traverse.
  • the length l of a given traverse is of course a function of the distance x between the contact dogs 88 and 82.
  • the switch 76 When the rail-up clutch 106 has caused the rail 98 to move upwardly sufiiciently to disengage the contact dogs 82 and 84 from each other, the switch 76 is opened, so that the relay coil LRR is de-energized. Because the relay coil 74 is a latching relay the contacts LRL LR2, LR3, and LR4 remain in their magneticallycaused states even though the relay coil LRR is deenergized. The opening of the switch 76 breaks the circuit through the now-closed contacts LR3 and the builder relay CR, however, so that the relay CR is deenergized, the contacts CR-l open, and the indexing solenoid 50 returns to its normal position under the urging of the spring 54 (it is to be noted that FIG. 1 shows the valve 48 in its indexing rather than in its normal position). When the valve 4-8 returns to its normal position, the ratchet 38 free-wheels and does not move the guide or shipper 28 to the left; the shipper accordingly remains in its new position.
  • the contact dogs and 8d make contact with each other, closing the switch 78 and energizing the reset coil LRL of the building latching relay 74.
  • This causes reversal of all contacts LRI, LR2, LR3, and LR4 to their normal positions as shown in FIG. 3 and energizes the rail-down clutch 106 to cause the rail 98 to move downwardly, while again avoiding rail run over.
  • the closing of the switch 78 actuates the builder relay CR through the contacts LR4, closes the contacts LRI, and indexes the indexing solenoid 58 as noted above.
  • the switch 78 When the rail has moved downwardly sufliciently to separate the contact dogs 80 and 84, the switch 78 is opened, thereby de-energizing the reset coil LRL. Inasmuch, however, as the relay is a latching relay and all contacts are in their normal or mechanically-caused states, the contacts LR-l, LR2, LR3, and LR4 remain in their new states, even though the reset coil LRL is deenergized.
  • the opening of the switch 78 also breaks the circuit through the contacts LR-4 and the builder relay CR, so that the relay CR is de-energized, the contacts CR-ll open, and the indexing solenoid 50 returns to its normal position under the urging of the spring 54.
  • the ratchet 38 again free-wheels, so that the shipper 28 remains in its new position.
  • a wind-back motor 14a is connected through gearing 142, a clutch 144, and a shaft and pinion 146 forming a portion of the gear train 36 to the rack 34 to return the guide 28 and builder nuts 86, 88 to their starting positions at the end of the package-building operation.
  • the clutch 144 is keyed to a shaft 145 by a keyway 148 but movable axially along the shaft by clutch-control means 150. The clutch 144 is disengaged during the building operation and engaged at the end thereof to eliminate the need for manual rewinding.
  • the present invention relates only to the subject matter of FIGS. 1 and 2, combined as necessary with broadlyrecited means for instrumenting it. It does not relate to the details of FIG. 3, which is a separate invention by Frederick A. Willis, Jr., and which is disclosed in the present application merely as one means of instrumenting the apparatus of the present invention. Obviously, the apparatus of the present invention could be instrumented in other ways. Nor does the present invention relate to the details of the subject matter of FIGS. 1 and 2 in combination with the details of the subject matter of FIG. 3, which is a separate invention by Ronald C. Mason, William B. Strzelewicz, Jr., and Frederick A. Willis, Jr.
  • the use of a pneumatic pistoncylinder assembly eliminates the harsh, noisy action of the contact shaft and the shock to the skip gear, contact dogs, builder nuts, and contact shaft.
  • the reversing clutches eliminate rail run overs during reversal of rail movement by always maintaining positive holding of the rail.
  • the front roll speed may be varied independently of frame speed and may be substantially in excess of 300 rotations per minute, thereby facilitating greater manufacturing efficiency. Further, the machine may be stopped safely in any position of rail travel.
  • the improvement comprising drive means for establishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative traverse of the feed mechanism and bobbin with respect to each other longitudinally of the axis of rotation of the bobbin, the drive means including a pair of counterrotating clutch means and rotatable shaft means alternately engageable by the clutch means, and control means for (1) alternately energizing the clutch means to cause said relative traverse alternately to assume first and second directions opposite to each other and (2) limiting at least one of (a) the rotational velocity, (b) the traverse velocity, and (c) the traverse length to values w, v, and 1, respectively, the control means comprising a pneumatic piston-cylinder assembly, means for actuating the pistoncylinder assembly at intervals to produce an output, and means coupling the output to the drive means to alter at least one
  • the improvement comprising drive means for establishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative traverse of the feed mechanism and bobbin with respect to each other longitudinally of the axis of rotation of the bobbin, the drive means including a pair of counterrotating clutch means and rotatable shaft means alternately engageable by the clutch means, and control means for (1) alternately energizing the clutch means to cause said relative traverse alternately to assume first and second directions opposite to each other and (2) limiting the traverse length to a value I, the control means including (a) first and second contact means spaced apart from each other a distance x of which the value I is a function, (b) third contact means adapted to engage alternately the first and second contact means at opposite ends of the traverse, (c) first reversing means responsive to engagement of the first and third
  • the improvement comprising drive means for establishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative traverse of the feed mechanism and bobbin with respect to each other longitudinally of the axis of rotation of the bobbin, the drive means including (a) a pair of counterrotating clutch means and rotatable shaft means alternately engageable by the clutch means and (b) variablemechanical-advantage means, and control means for (l) alternately energizing the clutch means to cause said relative traverse alternately to assume first and second directions opposite to each other and (2) limiting the rotational velocity to a value w, the control means including (a) varying means for varying the mechanical advantage of the variable-mechanical-advantage means, (b) a pneumatic piston-cylinder assembly, (c) means for actuating the piston-cylinder assembly at intervals to produce an output
  • the improvement comprising drive means for establishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative traverse of the feed mechanism and bobbin with respect to each other longitudinally of the axis of rotation of the bobbin, the drive means including (a) a pair of counterrotating clutch means and rotatable shaft means alternately engageable by the clutch means and (b) variable-mechanical-advantage means, and control means for (1) alternately energizing the clutch means to cause said relative traverse alternately to assume first and second directions opposite to each other and (2) limiting the rotational velocity to a value w and the traverse length to a value I, the control means including (a) first and second contact means spaced apart from each other a distance x of which the value I is a function, (h) third contact means adapted to engage alternately the first and second
  • the improvement comprising drive means for establishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative traverse of the feed mechanism and bobbin with respect to each other longitudinally of the axis of rotation of the bobbin, the drive means including (a) a pair of counterrotating clutch means and rotatable shaft means alternately engagea-ble by the clutch means and (b) variable-mechanical-advantage means having at least one cone pulley and a belt, there being a driving relation therebetween, and control means for (1) alternately energizing the clutch means to cause said relative traverse alternately to assume first and second directions opposite to each other and (2) limiting the rotational velocity to a value w and the traverse length to a value I, the control means including (a) first and second contact means spaced apart from each other a distance x of which I is
  • the improvement comprising (a) drive means for establishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative traverse of the feed mechanism and bobbin with respect to each other longitudinally of the axis of rotation of the bobbin, the drive means including (i) a pair of counterrotating clutch means and rotatable shaft means alternately engageable by the clutch means and (ii) variablemechanical-advantage means having at least one cone pulley and a belt, there being a driving relation therebetween, and (b) control means for (1) alternately energizing the clutch means to cause said relative traverse alternately to assume first and second directions opposite to each other and (2) limiting the rotational velocity to a value w and the traverse length to a value I, the control means including (i) first and second contact dog means spaced apart from each other
  • the improvement comprising (a) drive means for establishing a relative rotation of the feed mechanism and bobbin With respect to each other and a relative traverse of the feed mechanism and bobbin with respect to each other having a component longitudinal of the axis of rotation of the bobbin, the drive means including (i) a pair of counterrotating clutch means and rotatable shaft means alternately engageable by the clutch means and (ii) variable-mechanical-advantage means, and (b) control means for (1) alternately energizing the clutch means to cause said relative traverse alternately to assume first and second directions opposite to each other and (2) limiting the rotational velocity to a value w, the traverse length to a value I, and the traverse velocity to a value v, the control means including (i) first and second contact means spaced apart from each other a distance x of which I is
  • a frame for paying ofi. a filamentary material from a feed mechanism and Winding the material onto a bobbin to form a package of the material on the bobbin
  • the improvement comprising drive means for establishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative traverse of the feed mechanism and bobbin With respect to each other longitudinally of the axis of rotation of the bobbin, control means adapted to modify its condition to limit at least one of (a) the rotational velocity, (b) the traverse velocity, and (c) the traverse length to values w, v and 1, respectively, motor means adapted to restore the control means to its original condition, and clutch means for selectively engaging the motor means to the control means to restore the control means to its original condition.
  • the improvement comprising drive means for establishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative tnaverse of the feed mechanism and bobbin with respect to each other longitudinally of the axis of rotation of the bobbin, the drive means including a pair of counterrotating clutch means and rotatable shaft means alternately engageable by the clutch means, and control means for alternately energizing the clutch means to cause said relative traverse alternately to assume first and second directions opposite to each other, the control means including a piston-cylinder assembly adapted to produce an output, and means coupling the output to the drive means to modify the action of the drive means.
  • the improvement comprising drive means for establishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative traverse of the feed mechanism and bobbin with respect to each other longitudinally of the axis of rotation of the bobbin, the drive means including a pair of counterrotating clutch means and rotatable shaft means alternately engageable by the clutch means, control means for (l) alternately energizing the clutch means to cause said relative traverse alternately to assume first and second directions opposite to each other and (2) limiting at least one rotational velocity, (b) the traverse velocity, and (c) the traverse length to values w, v and l, respectively, the control means comprising a pneumatic piston-cylinder assembly, means for actuating the piston-cylinder assembly at intervals to produce an output, means coupling the output to the drive means to alter at least one value limited by
  • a frame for paying off a filamentary material from a feed mechanism and winding the material onto a bobbin to form a package of the material on the bobbin comprising drive means for establishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative traverse of the feed mechanism and bobbin with respect to each other longitudinally of the axis of rotation of the bobbin, control means for limiting at least one of (a) the rotational velocity, (b) the traverse velocity, and (c) the traverse length to values w, v and I, respectively, the control means comprising a pneumatic piston-cylinder assembly, means for actuating the piston-cylinder assembly at intervals to produce an output, means coupling the output to the drive means to alter at least one value limited by the control means, and pressure-responsive means connected to the pneumatic piston-cylinder assembly for preventing operation of the frame in the of (a) the event that pneumatic pressure to the pneumatic pistoncylinder assembly falls below a prescribed value.
  • the improvement comprising drive means for est-ablishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative traverse of the feed mechanism and bobbin with respect to each other longitudinally of the axis of rotation of the bobbin, the drive means including a pair of counterrotating clutch means and rotatable shaft means alternately engageable by the clutch means, control means for alternately energizing the clutch means to cause said relative traverse alternately to assume first and second directions opposite to each other, and brake means for preventing rotation of the rotatable shaft means in the event of simultaneous failure of both counterrotating clutch means to engage the rotatable shaft means.

Landscapes

  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Textile Engineering (AREA)
  • Spinning Or Twisting Of Yarns (AREA)
  • Replacing, Conveying, And Pick-Finding For Filamentary Materials (AREA)
  • Operating, Guiding And Securing Of Roll- Type Closing Members (AREA)
  • Winding Filamentary Materials (AREA)
  • Relay Circuits (AREA)
US40966964 1964-11-09 1964-11-09 Builder motion for roving frame Expired - Lifetime US3316700A (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
US40966964 US3316700A (en) 1964-11-09 1964-11-09 Builder motion for roving frame
US40989964 US3317800A (en) 1964-11-09 1964-11-09 Electric control circuit
US40991664 US3316701A (en) 1964-11-09 1964-11-09 Winding apparatus with electric control circuit
DE19651535026 DE1535026A1 (de) 1964-11-09 1965-11-02 Wickelmaschine,insbesondere Vorspinnmaschine,Flyer od.dgl.
CH1545065A CH447754A (de) 1964-11-09 1965-11-09 Wickelmaschine
GB5566667A GB1121042A (en) 1964-11-09 1965-11-09 Improvements relating to winding frames
GB4755065A GB1121041A (en) 1964-11-09 1965-11-09 Improvements relating to winding frames

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US40966964 US3316700A (en) 1964-11-09 1964-11-09 Builder motion for roving frame
US40989964 US3317800A (en) 1964-11-09 1964-11-09 Electric control circuit
US40991664 US3316701A (en) 1964-11-09 1964-11-09 Winding apparatus with electric control circuit

Publications (1)

Publication Number Publication Date
US3316700A true US3316700A (en) 1967-05-02

Family

ID=27410814

Family Applications (3)

Application Number Title Priority Date Filing Date
US40966964 Expired - Lifetime US3316700A (en) 1964-11-09 1964-11-09 Builder motion for roving frame
US40991664 Expired - Lifetime US3316701A (en) 1964-11-09 1964-11-09 Winding apparatus with electric control circuit
US40989964 Expired - Lifetime US3317800A (en) 1964-11-09 1964-11-09 Electric control circuit

Family Applications After (2)

Application Number Title Priority Date Filing Date
US40991664 Expired - Lifetime US3316701A (en) 1964-11-09 1964-11-09 Winding apparatus with electric control circuit
US40989964 Expired - Lifetime US3317800A (en) 1964-11-09 1964-11-09 Electric control circuit

Country Status (4)

Country Link
US (3) US3316700A (de)
CH (1) CH447754A (de)
DE (1) DE1535026A1 (de)
GB (2) GB1121041A (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3397529A (en) * 1965-11-05 1968-08-20 Zinser Textilmaschinen Gmbh Rail speed control arrangement for textile machines
US5259179A (en) * 1991-03-11 1993-11-09 Howa Machinery, Ltd. Device for stopping bobbin rail of flyer frame at a desired position
US5560193A (en) * 1993-04-27 1996-10-01 Howa Machinery, Ltd. Method and device for winding a roving in a flyer frame

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3015203A (en) * 1959-12-11 1962-01-02 Whitin Machine Works Torque controlled strand tensioning system and method
US3203163A (en) * 1963-05-31 1965-08-31 Shuford Mills Inc Traverse and tension control for winding machines
US3287891A (en) * 1963-06-24 1966-11-29 Zinser Textilmaschinen Ges Apparatus for controlling winding operations in a spinning machine

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2981869A (en) * 1958-05-08 1961-04-25 Controls & Comm Company Relay control circuit

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3015203A (en) * 1959-12-11 1962-01-02 Whitin Machine Works Torque controlled strand tensioning system and method
US3203163A (en) * 1963-05-31 1965-08-31 Shuford Mills Inc Traverse and tension control for winding machines
US3287891A (en) * 1963-06-24 1966-11-29 Zinser Textilmaschinen Ges Apparatus for controlling winding operations in a spinning machine

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3397529A (en) * 1965-11-05 1968-08-20 Zinser Textilmaschinen Gmbh Rail speed control arrangement for textile machines
US5259179A (en) * 1991-03-11 1993-11-09 Howa Machinery, Ltd. Device for stopping bobbin rail of flyer frame at a desired position
US5560193A (en) * 1993-04-27 1996-10-01 Howa Machinery, Ltd. Method and device for winding a roving in a flyer frame

Also Published As

Publication number Publication date
US3316701A (en) 1967-05-02
DE1535026A1 (de) 1970-04-09
GB1121041A (en) 1968-07-24
CH447754A (de) 1967-11-30
US3317800A (en) 1967-05-02
GB1121042A (en) 1968-07-24

Similar Documents

Publication Publication Date Title
US2764363A (en) Traverse mechanism for spinning, twisting and like frames
US3130930A (en) Builder apparatus
US3245215A (en) Apparatus for controlling the ring rail movement of a ring twisting machine
US3316701A (en) Winding apparatus with electric control circuit
US2749055A (en) Portable cap spinning unit with hydraulic traverse
US3406918A (en) Control and switching device in mechanically or hydraulically operated traverse-motion systems in spinning, spooling and especially ring twist machines
US3075342A (en) Shifting and switching mechanism for a ring rail
US3397529A (en) Rail speed control arrangement for textile machines
US3124925A (en) Automatic control system for spinning frames
US2959372A (en) Winding machine
US3256683A (en) Spinning frame and automation means therefor
US3080701A (en) Ring rail lowering mechanism for textile spinning frames
US3080127A (en) Bead winding apparatus
US2720093A (en) Warp knitting machine
US3067961A (en) Traversing device
US3203163A (en) Traverse and tension control for winding machines
US3231209A (en) Twister frame
US3138339A (en) Builder motion rewinding and tip bunch applying means for spinning frames
US3134217A (en) Stop motion for fly frames
US1935524A (en) Apparatus for winding spools and cops
US3409237A (en) Reversible winding arrangement
US2719678A (en) Traversing guide for wire coiler
US3768244A (en) Ring rail lifting apparatus for spinning machinery
US3251562A (en) Apparatus for producing strand packages of uniform length
US3861130A (en) Auxiliary ring rail positioning means for textile twister or like machine

Legal Events

Date Code Title Description
AS Assignment

Owner name: CONGRESS FINANCIAL CORPORATION

Free format text: SECURITY INTEREST;ASSIGNOR:LESCATH CORPORATION;REEL/FRAME:004087/0502

Effective date: 19830103