US3794085A - Shuttle boxing method and apparatus - Google Patents

Shuttle boxing method and apparatus Download PDF

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Publication number
US3794085A
US3794085A US00229697A US3794085DA US3794085A US 3794085 A US3794085 A US 3794085A US 00229697 A US00229697 A US 00229697A US 3794085D A US3794085D A US 3794085DA US 3794085 A US3794085 A US 3794085A
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Prior art keywords
shuttle
target
inertial mass
boxing
linkage
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US00229697A
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English (en)
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W Stephens
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NOXXE Inc
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NOXXE Inc
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    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D49/00—Details or constructional features not specially adapted for looms of a particular type
    • D03D49/52—Shuttle boxes
    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D49/00—Details or constructional features not specially adapted for looms of a particular type
    • D03D49/24—Mechanisms for inserting shuttle in shed

Definitions

  • ABSTRACT There is disclosed a shuttle boxing method and appa- 52 us. 139/185, 139/142, 139/162 Paws whereby 100m Shuttles, upon Completion of their 511 Int. Cl.. 00341 49/54, D03d 49/24, 1303a 49/38 traverse of the lay beam, are rapidly and smoothly decelerated without deleterious rebound.
  • tion method and apparatus of the invention serve to employ the kinetic energy of the flying shuttle in over- 56] References Cited coming the inertia of a flywheel at rest.
  • the energy of the spinning flywheel is imparted to the boxed shuttle.
  • the present invention relates broadly to textile looms and operations thereof. More specifically, the method and apparatus disclosed and claimed herein relate to operations conventionally known in the art as shuttle boxing and picking.
  • shuttle rebound One of the major problems confronted in the textile loom art throughout its history, and particularly when high production rate loads are imposed upon a loom, resides in the phenomenon of shuttle rebound. It is quite common in present day loom operations to pick or fire the shuttle across the race board of the'loom at velocities substantially in excess of thirty miles per hour. At the end of each pick, however, it is allimportant that the shuttle be stopped without bounce or rebound from or within the shuttle box. Unfortunately, however, when a rapidly moving shuttle engages shuttle boxes of conventional designs of the prior art, rebound thereof often occurs.
  • the conventional shuttle box designs generally include friction means adapted to bear against the shuttle upon entry thereof into the box, thereby decelerating and halting the shuttle.
  • Such binder mechanisms thus depend upon the conversion of the kinetic energy of the shuttle into heat. Designs of this type are exemplified, for instance, in the disclosures of U.S. Pat. Nos. 2,874,727; 3,012,586 and 3,593,755.
  • Other known shuttle boxing protection devices include mechanical dogs, pawls or the like which are adapted to engage the shuttle upon entry thereof into the box and to release the shuttle prior to its subsequent pick.
  • Each of the shuttle box mechanisms described above have associated therewith certain serious deficiencies. Above all, the most serious of said deficiencies resides in the fact that none appear to have totally resolved the problem of shuttle rebound.
  • the mechanical pawls and friction inducing means of the prior art shuttle boxes further tend to wear rather rapidly, thus requiring a considerable amount of maintenance.
  • Another object of the invention is to provide a novel method for both boxing and picking loom shuttles.
  • the loom shuttle receiving and deceleration method of the invention comprises the transfer of the kinetic energy of a moving shuttle to a flywheel.
  • the apparatus by which said method is carried out includes a shuttle target which, through a suitable mechanical linkage, translates the linear displacement imparted thereto by the impacting shuttle to an angular displacement output.
  • the angular displacement output is transmitted to a resting flywheel by means of a suitable clutch device interposed between the linkage and the flywheel.
  • Firing or picking of the shuttle brought to rest by the method and apparatus described above is accomplished by transferring the energy and translating the rotational displacement of the spinning flywheel, again through suitable clutch means and said mechanical linkage to a linear output displacement of the shuttle target, thereby firing the shuttle in its reverse course across the race board of the loom. Accordingly, at least a portion of the energy imparted to the flywheel by the shuttle boxing cycle is stored and returned to the shuttle in the picking cycle.
  • the energy input to the flywheel is augmented by fixed attachment thereof to a prime mover adapted to rotate in either direction of rotation. The direction of rotation of said prime mover is dictated by the direction of initial movement of the flywheel in the previous shuttle boxing cycle.
  • FIG. 1 is a schematic, diagrammatic, partly sectional perspective view of a portion of a conventional flyshuttle loom equipped with the shuttle boxing and picking apparatus of the invention
  • FIG. 2 is a longitudinal section of clutch apparatus suitable for use in the apparatus of FIG. 1 and shown in the disengaged position;
  • FIG. 3 is a sectional plan view of the clutch mechanism of FIG. 2 in the engaged position, taken through section line 1-1' thereof;
  • FIG. 4 is a perspective, partly sectional view of the principal clutch engagement and disengagement actuating members of the clutch mechanism of FIGS. 2 and 3;
  • FIGS. 5 through 8 are schematic, diagrammatic side views of the mechanical linkage mechanism employed in FIG. 1 wherein the relative positions of the-various linkage elements thereof are shown at several stages of operations in the shuttle receiving and firing cycles of the apparatus of the invention.
  • lay beam 50 defines generally a race board 51 along which shuttle 55 traverses the warp shed (not shown) and shuttle box 52 wherein the shuttle is received, arrested, allowed to dwell for a time sufficient to provide suitable changeover of the harnesses (not shown) and fired in its return pick.
  • the shuttle boxing mechanism of the invention comprises shuttle target 11, mechanical linkage 20, clutch 20d) and flywheel 70.
  • Said mechanical linkage 20 is adapted to (A) provide for substantially linear and parallel displacement of target 11 with respect to the shuttle box bed 54, while (B) translating said linear displacement into an angular displacement output at a convenient point removed from the shuttle box 52.
  • linkage element 1 is pivotally affixed at its upper end to target 11 and is pivotally affixed at its midpoint to the lower end of linkage element 2.
  • the lower end of linkage element 1 comprises a common and mutually pivotal attach point for both the upper end of linkage element 3 and the right hand end of linkage element 5.
  • the upper end of linkage element 2 is pivotally affixed to a stationary base which may reside in slot 56 of lay beam 50.
  • linkage elements 6 and 7 are affixed in pivotal manner to a stationary base while the lower ends of said elements 6 and 7 are pivotally affixed to linkage element 5 at the midpoint and left hand end thereof, respectively.
  • linkage element 3 is pivotally attached to the upper end of terminal linkage element 4.
  • the lower end of said linkage element 4 is pivotally mounted in coaxial relationship with the center of flywheel 70.
  • Clutch 200 is adapted to transfer angular displacement of terminal linkage 4 to the flywheel.
  • One such suitable clutch will be discussed in more detail hereinbelow.
  • shuttle 55 strikes target 11, thereby linearly displacing said target 11 over the bed 54 of shuttle box 52 and towards the end 57 of lay beam 50.
  • Said substantially linear displacement actuates linkage mechanism 20 causing either a clockwise or counterclockwise angular displacement of terminal linkage element 4.
  • the initiation of the angular displacement of element 4 either causes or finds clutch 200 in engagement with resting flywheel 70, thereby overcoming the flywheels inertia and initiating and accelerating the rotation thereof while concomitantly transferring the kinetic energy of the shuttle 55 to the flywheel 70.
  • the end of the shuttle decelerating cycle (FIGS.
  • flywheel 70 The direction of rotation of flywheel 70 will be determined by the position of the knee formed between articulated linkage elements 3 and 4 at the beginning of the cycle. As is clearly shown in FIGS. 4 and 5, when said knee is positioned to the left at the beginning of the shuttle receiving cycle, the flywheel will spin in clockwise direction. However, referring now to FIGS. 7 and 8, when the knee formed between articulated elements 3 and 4 is positioned to the right upon initiation of the shuttle receiving cycle, the resulting rotation of the flywheel will be in a counterclockwise direction.
  • the resetting of the shuttle decelerating apparatus of the invention in preparation for the subsequent shuttle receiving cycle is accomplished merely by bringing the spinning flywheel 70 to rest and moving target 11 to its forward position.
  • the flywheel 70 may be brought to a halt by any suitable braking means (not shown) actuated in proper time sequence with respect to the weaving cycle of the loom. Such braking, for instance, may be actuated upon firing of the shuttle from the shuttle box.
  • the target 11 can be brought to its forward position by means of a separate picker stick (not shown) positioned therebehind.
  • the decelerating forces applied to the shuttle in carrying out the shuttle boxing method of the present invention are such as to insure the arresting of the shuttle with little or no danger of rebound. While there is no intent to be bound by this explanation, it is thought that the beneficially rebound-free nature of the present shuttle boxing method and apparatus is due to the inherent nature of the energy transfer involved in overcoming the inertia of a resting rotatable mass, i.e., the flywheel 70 inertia reflected to the shuttle 55 at the time of initial engagement with target 11 is essentially zero and, as the shuttle penetrates into the boxing apparatus, this reflected inertia increases due to the chaning mechanical advantages associated with the instantaneous position of the linkage 20 until, when the shuttle is deep into the boxing apparatus, this reflected inertia tends towards infinity.
  • the shuttle receiving apparatus of the invention is of the Sulzer type, in other words where the shuttle or dart is fired across the lay beam in one direction only, picked up and returned to the firing side of the warp shed, only one of the shuttle receiving and decelerating devices of the invention is required.
  • the shuttle boxes on both sides of the lay beam be equipped with the shuttle receiving and decelerating devices described and claimed herein.
  • said shuttle may be fired by conventional picker stick means.
  • a much preferred embodiment of the invention eliminates the need for such added picker stick means and serves further to converse and re-use a substantial portion of the energy originally imparted to the flywheel in the deceleration of the shuttle during the receiving cycle.
  • a prime mover 300 which is adapted for rotation of its shaft 301 in either direction upon mechanical initiation of rotation thereof.
  • a principal example of a prime mover possessed of this attribute is a single phase electric motor whose conventional electrical starting apparatus has been disabled.
  • Shaft 301 is fixed to flywheel 7t) and, indeed, desirably forms the common shaft for mounting of the flywheel and the freely rotatable spindle 605 of clutch Ztltl (FIGS. 2, 3 and 4).
  • target 11 is positioned at its rearmost position, clutch 200 is disengaged and flywheel 70 is freewheeling. Strictly speaking, however, when the shuttle firing embodiment of the invention is employed, said freewheeling does not occur. Rather, the initial motion of flywheel 70 in the shuttle receiving and decelerating cycle acts through shaft 301 to actuate prime mover 300.
  • flywheel 7tl Prior to initiation of the .shuttle firing cycle, flywheel 7tlwill generally attain the slip-speed of the prime mover 30ft.
  • the clutch engagement signal may be derived from sensing and responding to the position of lay sword 700.
  • clutch 200 engagement may be obtained through a motion reversing means whereby trigger 650 is actuated by the rearward motion of lay sword 700.
  • Other portions of the loom may be employed, however, such as the dobby head, harness cams, crankshaft or any other loom part from which the relative positions of the harnesses and lay beam can be accurately and repetitively determined.
  • the spinning flywheel upon engagement of clutch 200, the spinning flywheel imparts its energy to shuttle 55 through the linkage mechanism 20 and target 11.
  • Target ll propelled forwardly along shuttle box bed 52, thereby accelerates shuttle 55 to its pick speed.
  • the finish of the shuttle firing cycle finds target 11 in its forwardrnost position and the knee formed between linkage elements 3 and 4 fully reconstituted. Accordingly, initiation of the shuttle firing cycle from the position shown in FIG. 5, with clockwise spinning of flywheel 7t), will result in the finish linkage 20 position shown in FIG. 7. Conversely, where the shuttle firing sequence is initiated from the linkage 20 conformation shown in F lG. 8, wherein the flywheel 70 is spinning in counterclockwise rotation, the finish position will be that shown in FIG. 5. The attainment of the linkage 20 positions shown in FIGS. 5 and 7 brings linkage element 1 to its maximum angular displacement from the vertical.
  • this linkage geometry through transfer of forces through the linkage 2t) and clutch 20th smoothly and rapidly decelerates flywheel '70 and prime mover 300 to a complete halt.
  • the shuttle boxing and firing mechanism of the invention bears the conformation shown in FIGS. 5 and 7 and is prepared to receive the shuttle of the subsequent pick.
  • the linkage elements be constructed so as to withstand the operating stresses imposed thereupon.
  • the particular preferred em bodiment of the linkage 20 described in detail hereinabove can be generally described as two lsosceles type linkages connected back to back.
  • One of said linkages is defined by the combination of linkage elements 5, 6 and '7 while the other is defined by the combination of linkage elements 1 and 2.
  • the resulting overall linkage operates with marked freedom from torsional stresses, the bulk of the operating stresses being purely compressive or tensional in nature.
  • Another suitable linkage 20 design comprises a vertical race depending from the bottom of the lay beam.
  • a sliding member rides up and down on said vertical race and additionally comprises (1) a connecting linkage element attached in pivotal manner to the shuttle target, and (2) a two-element articulated toggle assembly, one of which toggle elements is affixed in pivotal manner to the sliding member and the other of which toggle elements is rotatably affixed to the flywheel shaft.
  • this last toggle element comprises the angular displacement member of the overall linkage.
  • Said type of linkage has the advantage of fewer moving parts than the linkage described in detail hereinbefore.
  • the sliding member thereof can impart substantial sliding friction into the overall system. With respect to such frictional considerations, moreover, it is obviously desirable that the linkage elements be provided with suitable bearings at their respective articulations so as to minimize frictional energy losses through the system.
  • the flywheel 70 size, weight and design is subject to considerable variation and is dependent upon the mass and velocity of the shuttle at the impact point thereof against target 11, frictional losses through the linkage 20, the energy required to drive the clutch mechanism 200 and the like. Accordingly, bearing the above in mind, the size, mass and specific design of the required flywheel or rotatable mass can be determined for any given loom situation.
  • the primary goal to be achieved, of course, is to provide a flywheel of sufficient inertial characteristics as to smoothly decelerate the shuttle to zero velocity.
  • the apparatus of the invention includes the shuttle firing embodiment, i.e., the prime mover 300
  • the contribution said prime mover may make upon start-up thereof to the acceleration of the flywheel prior to clutch disengagement and/or the contribution said prime mover may make to the overall flywheel function should also be taken into account in determining suitable flywheel mass and size.
  • FIGS. 2 through 5 A suitable clutch mechanism for use in the apparatus of the invention is depicted in detail in FIGS. 2 through 5 forming part hereof.
  • Shaft 301 which, as mentioned before, may desirably be the shaft of prime mover 300, traverses housing 204, bearing 610, flywheel 70, spin dle 605 and bearing 612.
  • Terminal linkage element 4 is rigidly affixed to spindle 605 which, in turn, is mounted rotatable and slideably upon said shaft 301.
  • Spindle 605 comprises a generally l-I-shaped member to which triangular toggle arms 606 and 607 are pivotally affixed, such as by pinning thereof.
  • Completing the toggle assembly are friction pad holders 610 and 611, each being pivotally affixed to the apex of triangular toggle arms 606 and 607 and to which pad holders there are attached friction pads 612 and 613.
  • said friction pads 612 and 613 ride close to but out of contact with the internal flange surface 72 of flywheel 70.
  • the engaged clutch mode FIG.
  • toggle members 606 and 607 rock in a slightly off-axis fashion and thus provide for the desirably greater available bearing force between pads 612 and 613 and the internal flywheel surface 72. Furthermore, said rocking motion tends to cause the clutch to self-energize, once initial actuation thereof has been achieved. Accordingly, the rocking motion of toggle members 606 and 607 is highly advantageous and contributes materially to the rapidity of clutch engagement and to the ultimate security of said engagement.
  • cam roller 614 and friction stud 615 depending from and integral with spindle 605 are cam roller 614 and friction stud 615, said stud 615 having affixed to the terminus thereof friction pad 616.
  • the clutch actuating mechanism comprises sliding block 617 having on the upper surface thereof disengage cam 618 and a double wedge vertical protuberance 619.
  • Lower surface 610 of recess 621 also defines a cam surface adapted to receive in operative combination therewith cam stud 651 of actuating trigger 650.
  • housing 204 there are afflxed ring-shaped members 206 and 207 whose internal circumferential surfaces define clutch lock-in cam surfaces 208 and 210. It should be noted that said semi-circular members 206 and 207 need only to subtend an are equal to or somewhat greater than the total are traversed by terminal link member 4 in its to and fro motion about the axis formed by shaft 301.
  • actuating trigger 650 Upon pick-off of the firing signal from a suitable source, actuating trigger 650 is mechanically and momentarily driven into slot 621 of blcok 617, cam 651 thereby lowering said block and moving cam 618 out of engagement with cam roller 614.
  • stud 653 of trigger 650 drives into cam roller 614. This last action serves to force cam roller 614 onto either one of the lock-in cam surfaces 208 or 210 depending on the direction of rotation of flywheel 70.
  • cam roller 614 is thus forced forwardly by cam surface 208 or 210 and carries with it spindle 605, thereby forcing toggle members 606 and 607 and their associated friction pads 612 and 613 against the interior flange surface 72 of flywheel 70, thus completing the engagement of the clutch and effectuating the firing of the shuttle.
  • the clutch remains engaged subsequent to the shuttle firing cycle and in preparation for the initiation of the next shuttle receiving cycle.
  • terminal link 4 In the shuttle receiving cycle the terminal link 4 will be at its furthest angular deflection from the vertical (FIGS. 5 or 7) and flywheel and prime mover 300 will be halted.
  • terminal link element 4 Upon impact of the shuttle against the shuttle target 11, terminal link element 4 is set into motion towards the vertical position, thereby initiating rotation of flywheel 70 and prime mover 300 by transfer of the motion thereof through the engaged clutch.
  • cam roller 614 As terminal link 4 approaches the vertical, cam roller 614 is forced outwardly by disengage cam 618, thus withdrawing spindle 615 from its forwardmost position and disengaging the clutch.
  • flywheel 70 continues spinning and is even further accelerated to the slip-speed of prime mover 300 while leaving shuttle target 11 in its rearmost position and terminal linkage element 4 at substantially the vertical position, thus providing the appropriate conditions for the subsequent firing cycle.
  • clutch mechanism discussed above has been described in detail, it will be obvious that many equivalents thereof can also be employed in the practice of the invention. Accordingly, it is only necessary that the clutch mechanism employed (1) be capable of engaging and disengaging immediately upon appropriate command thereof, (2) be sufficiently sturdy as to withstand the relatively high and instantaneously applied torque loads imposed thereupon during operations and (3) be bi-directional in operation.
  • clutches based on the well-known spring wrap principle wherein use is made of the capstan effect encountered when a coiled flat spring is wound or tightened about an arbor are also considered suitable for the practice of the invention. in this embodiment, two such devices in back-to-back relationship will achieve the necessary bi-directional function of the overall clutch mechanism.
  • the drive shaft of the prime mover when employed, need not be affixed directly to the hub of the flywheel.
  • said shaft can be equipped with pinion teeth adapted for geared engagement with the exterior periphery of the flywheel, thereby establishing.
  • the drive shaft of the prime mover will rotate in a direction opposite that of the flywheel.
  • the prime mover/flywheel drive interfacing can include roller chain and sprocket or other conventional means for the transfer of power between a prime mover and a rotatable body or mass.
  • a cyclic shuttle boxing method for textile loom operations wherein each boxing cycle comprises:
  • step (d) (ii) is achieved as said shuttle target attains said forward position.
  • Shuttle boxing apparatus for textile looms comprising:
  • rotational inertial mass means adapted for discontinuous operative communication with the angular displacement output of said linkage means, said operative communication occurring during the period of displacement of said shuttle target from said forward position to said rear position and ceasing upon attainment of said rear position;
  • the shuttle boxing apparatus of claim 6 additionally comprising:
  • prime mover means in driving relationship with said inertial mass means, said prime mover means being adapted to drive said rotatable inertial mass means only upon rotation thereof and in either direction of rotation in accord with and upon initiation of rotation of said mass by said angular displacement output of said linkage means;
  • F. clutch means providing said discontinuous operative communication of (C) between said linkage means and said inertial mass means and, in addition being further adapted to reestablish said operative communication timed to loom operations and subsequent to presentation of a new warp shed, said reestablished communication thereby causing rapid substantially linear displacement of said shuttle target from said rear position to said forward position, picking the shuttle previously boxed therein and bringing said rotating inertial mass to a halt.

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  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Looms (AREA)
US00229697A 1972-02-28 1972-02-28 Shuttle boxing method and apparatus Expired - Lifetime US3794085A (en)

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US22969772A 1972-02-28 1972-02-28

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US (1) US3794085A (en, 2012)
JP (1) JPS4898158A (en, 2012)
DE (1) DE2304083A1 (en, 2012)
FR (1) FR2174008B1 (en, 2012)
IT (1) IT977663B (en, 2012)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3964523A (en) * 1974-12-12 1976-06-22 Wayne H. Coloney Co., Inc. Shuttle drive linkage for looms
EP1777328A1 (de) * 2005-10-01 2007-04-25 Markus Farner Verfahren zum Eintragen eines Schussfadens

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1966704A (en) * 1930-12-05 1934-07-17 Bell Walter Picking mechanism for looms for weaving
US2517454A (en) * 1949-03-01 1950-08-01 F C Huyck & Sons Picking mechanism for looms
US2787290A (en) * 1954-06-24 1957-04-02 F C Huyck & Sons Picking mechanism for looms
US3124166A (en) * 1964-03-10 Shuttle receiving mechanism for gripper shuttle looms
US3487860A (en) * 1967-01-26 1970-01-06 Elitex Zavody Textilniho Shuttle braking arrangement
US3670775A (en) * 1969-08-28 1972-06-20 Saurer Ag Adolph Braking shuttles in loom shuttle box

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1710871A (en) * 1927-07-20 1929-04-30 L H Gilmer Co Of La Inc Loom
US2108375A (en) * 1937-02-16 1938-02-15 Cyclone Fence Company Shuttle bar actuating mechanism

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3124166A (en) * 1964-03-10 Shuttle receiving mechanism for gripper shuttle looms
US1966704A (en) * 1930-12-05 1934-07-17 Bell Walter Picking mechanism for looms for weaving
US2517454A (en) * 1949-03-01 1950-08-01 F C Huyck & Sons Picking mechanism for looms
US2787290A (en) * 1954-06-24 1957-04-02 F C Huyck & Sons Picking mechanism for looms
US3487860A (en) * 1967-01-26 1970-01-06 Elitex Zavody Textilniho Shuttle braking arrangement
US3670775A (en) * 1969-08-28 1972-06-20 Saurer Ag Adolph Braking shuttles in loom shuttle box

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3964523A (en) * 1974-12-12 1976-06-22 Wayne H. Coloney Co., Inc. Shuttle drive linkage for looms
EP1777328A1 (de) * 2005-10-01 2007-04-25 Markus Farner Verfahren zum Eintragen eines Schussfadens

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DE2304083A1 (de) 1973-09-06
FR2174008B1 (en, 2012) 1977-02-04
JPS4898158A (en, 2012) 1973-12-13
IT977663B (it) 1974-09-20
FR2174008A1 (en, 2012) 1973-10-12

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