US3856055A - Shuttle control device for a loom - Google Patents

Shuttle control device for a loom Download PDF

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Publication number
US3856055A
US3856055A US00286700A US28670072A US3856055A US 3856055 A US3856055 A US 3856055A US 00286700 A US00286700 A US 00286700A US 28670072 A US28670072 A US 28670072A US 3856055 A US3856055 A US 3856055A
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shaft
control device
batten
shuttle control
power shaft
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US00286700A
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English (en)
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J Hirsch
E Mayeur
J Mayeur
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En Commandite Par Actions A &
Soc En Commandite Par Actions Dite A & A Caen fr
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En Commandite Par Actions A &
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    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D35/00—Smallware looms, i.e. looms for weaving ribbons or other narrow fabrics

Definitions

  • SHEET IBM 10 1 SHUTTLE CONTROL DEVICE FOR A LOOM This invention relates to shuttle control devices for looms and, more particularly, although not so restricted, to shuttle control devices for weaving looms, e.g., ribbon looms.
  • each driving rack comprises two pivotable stops capable of being placed in the path of a traction hook integral with each side of an endless chain, the chain performing a reciprocating movement.
  • the first of these known constructions necessitates brakes to immobilise the driving racks in clearly determined positions where a row of shuttles is positioned precisely between two adjacent sheds. Since the precision of positioning of the shuttles can only be obtained with complicated and expensive means, it is necessary to provide a relatively large distance between two adjacent sheds in order to leave sufficient play between the ends of the shuttles and the edges of the sheds. This has the effect that the stroke of the driving racks must be increased with a corresponding reduction in the number of strokes that they can perform per unit time.
  • the present invention seeks to eliminate the abovementioned disadvantages and to produce a shuttle control device which device enables the shuttles to be positively driven and braked, for the speed of the shuttles to be increased and for the positioning of the shuttles to be obtained with precision.
  • a shuttle control device for a loom comprising: a beam capable of executing a substantially horizontal reciprocating movement; a batten guided for vertical movement on one face of the beam and capable of occupying at least two different positions; a plurality of horizontally disposed driving racks mounted on the batten, each driving rack being arranged to act upon a group of shuttles so as to drive the group in a horizontally reciprocating movement along the batten; a plurality of control racks, each drive rack being integral at one end with a respective one of the control racks, each control rack being meshed with a toothed wheel keyed onto a sheath and an interior rod, the sheath being connected with the batten both for vertical displacement parallel to its axis and also for horizontal translation of the batten, the sliding interior rod having splines engaged in corresponding splines of the sheath; a self-locking reciprocating drive and selection mechanism having an output shaft,
  • a selected driving rack, and hence a corresponding row of shuttles are controlled and guided positively and can undergo considerable accelerations and decelerations, whereas the non-selected driving racks occupy a neutral position.
  • the clearances are reduced to a minimum, and the coupling of a driving rack to the power shaft and the uncoupling of the previously coupled driving rack are perfectly synchronised.
  • the said mechanism serves simultaneously for the braking and precise positioning of the shuttles. Due to the fact that the part of the shuttle control device which is integral with the batten comprises only a very small number of constituent elements, the beam/batten assembly is reduced in weight, which likewise favours an increase in the operating speed of the loom. Furthermore, only the selected driving rack and the corresponding toothed wheel are driven, whereas the other racks and toothed wheels remain stationary in the neutral position. The mass to be alternately accelerated and decelerated is therefore considerably reduced.
  • FIG. 1 is a side elevational view of a loom for weaving ribbons, the loom having a shuttle control device ac.- cording to the present invention
  • FIG. 2. is an end elevational view of the loom of FIG.
  • FIG. 3 is a plan view of part of the shuttle control device of FIG. 1 taken from the plane III-III of FIG. 2;
  • FIG. 4 is a sectional view of a self-locking reciprocating driving and selection mechanism taken along'the line IV-IV of FIG. 2;
  • FIG. 5 is a vertical elevational view of the self-locking reciprocating driving and selection mechanism taken on the line V-V of FIG. 4;
  • FIG. 6 is an elevational view of the upper part of the shuttle control device
  • FIG. 7 is a view in the direction of the arrow VII of FIG. 6;
  • FIG. 8 is an elevational view of control racks of the shuttle control device showing their connection to corresponding driving racks;
  • FIG. 9 to 11 are sections of the shuttle control device taken along the lines IX1X, XX and XI-XI respectively of FIG. 6;
  • FIG. 12 is a view taken along the line XIl-Xll of FIGS. 6 and 11;
  • FIG. 13 is a horizontal section through an intermediate transmission mechanism between a driving motor and a power shaft, the section being taken along the line XIIIXIII of FIG. 2.
  • FIG. 1 there is shown a loom for weaving ribbons having a shuttle control device according'to the present invention.
  • the loom comprises a frame 1 on which is mounted a motor 2 acting through a change speed gear 3 and a belt transmission 4, upon a flywheel 5, the axis 6 of rotation of which is within the frame 1.
  • On the flywheel there is mounted, eccentrically and radially adjustably, a rear end 7a of a connecting rod 7, the front end 7b of which is pivotally mounted on a T-piece 8.
  • the T-piece 8 is supported by two suspension or support levers 9, 10, the lower ends of which are pivoted at points 11, 12 to the frame 1 and the upper ends of which are pivoted at points 13, 14 to the T-piece 8 at the same horizontal level.
  • the four points 11, 12, 13 and 14 of the levers 9, define a deformable parallelogram.
  • a beam 15 is pivotally mounted at points 26, 27.
  • the beam 15 extends along the entire front face of the loom and is pivoted on the upper lateral side of the loom and, if required, also at the centre of the loom to another T-piece identical to the T-piece 8. Also, if required, on the other lateral side of the loom in the central part thereof, another control rod and another flywheel driven by another change speed gear may be provided.
  • the beam 15 acts as support for a batten 16 which extends across the total width of the front part of the loom and is vertically movable in guides 15a of the beam 15.
  • the batten 16 is equipped with two groups 17, 18 of superposed rows of shuttles.
  • a vertical control mechanism 19 of the batten 16 has not been shown in detail, but only schematically, in FIG. 1.
  • the output of the control mechanism 19, for vertically positioning the batten 16, acts, through the intermediary of a transmission, upon the lower end of the latter.
  • the control mechanism 19 and the transmission 20 are described in greater detail in the specification of British Patent Application No. 1 1345/72 corresponding to U.S. Pat. No. 3,752,196
  • Two sheds 21, 22, healds 23, a thread breaker 24 and a roller 25 are likewise indicated only schematically since, like the batten 16, its control mechanism 19 and the beam 15, they do not form part of the present invention,
  • the transmission 20 comprises a link rod pivoted at one end to the lower part of the batten 16 and at the other end to a horizontal arm 31a of a double return and lifting lever 31 which is keyed to a lifting shaft 32 extending horizontally across the total width of the front part of the loom.
  • the lifting shaft 32 may comprise a plurality of horizontal arms similar to the arm 31a, these arms being distributed across the lifting shaft 32 and each connected to the batten 16 through the intermediary of link rods 30 which, like the arms 31a, are arranged parallel to one another.
  • a second arm 31b of the lever 31 is perpendicular to the horizontal arm 31a, extends upwardly, and is pivoted, at its upper end, to a substantially horizontal connecting rod 33.
  • the rear end of the connecting rod 33 enters a housing 34 of the control mechanism 19 via an aperture 34a in the front face thereof.
  • the batten 16 carries two superposed groups 17, 18 of three similarly superposed rows of shuttles. Since the number of rows of shuttles per group, in the case of the illustrated embodiment, is equal to three, the batten 16 must be capable of occupying three different vertical positions, for each of which one row of shuttles of a group is located at the level of a work plane: that is to say, located at the level of the horizontal median plane of the respective shed 21 of 22. As illustrated in F IG. 1, the batten 16 occupies its median position for which each median row of shuttles 17a, 18a is located at the median plane of the corresponding shed.
  • the control mechanism 19 is associated with two selection units 107, 108 which are controlled from a Jacquard or similar type device (not shown) and which determines, in cooperation with the control detail. 19, the various vertical positions of the batten l6 and the groups of shuttles relative to the sheds 21, 22 and the beam. 15.
  • the control mechanism and selection units are also the subject of British Patent Application No. 11345/72 and will, therefore, not be described in de-' tail/ A rack box 40 of a shuttle control device 41 according to the present invention is integral with the lefthand end (FIG. 2) of the batten 16.
  • a control rack rigidly connected to the driving rack which extends across the total width of the batten 16 and is guided horizontally in a suitable manner.
  • the control racks are designated by reference numerals 42 to 47 which, in the case of the embodiment illustrated, are six in number.
  • Each control rack cooperates with a respective toothed wheel 48 to 53.
  • the wheels 48, 49 are keyed to a cylindrical sheath 54, the wheels 50, 51 to a cylindrical sheath 55, and the wheels 52, 53 to a cylindrical sheath 56, the sheaths being part of respective telescopic shafts 57, 58, 59 arranged vertically and parallel to one another in the rack box 40.
  • Each sheath 54, 55, 56 is housed in the rack box so as to be capable of rotating in either direction but each sheath is axially fixed and is integral with the batten 16.
  • Each telescopic shaft 57, 58, 59 also comprises a rod 60, 61, 62 which is axially movable, partly housed and guided in its respective sheath 54, 55, 56, and is provided with splines 60a, 61a, 62a which extend parallel to the axis of the rod and engage in internal splines of the respective sheath (see FIGS. 6 and 7).
  • each rod 60, 61, 62 passes through a projecting, hollow horizontal part b of the beam 15 and is connected to an upper cardan joint 63, 64, 65 of a double-cardan transmission shaft 66, 67, 68 which, through the intermediary of a lower cardan joint 69, 70, 71, is connected to an output shaft 72, 73, 74 of a self-locking reciprocating driving and selection mechanism 75.
  • the reciprocating driving and selection mechanism 75 possesses two inputs 76, 77, one input 76 constituting a power input and the second input 77 constituting a selection input.
  • the input 76 is powered by a drive motor for example, the motor 2 which rotates continuously.
  • An intermediate transmission mechanism 78 transforms the continuous rotary movement of the motor 2 into an intermittent rotary movement.
  • the input 77 is connected to a Jacquard or similar type device (not shown) for the loom. Since the movement of the connecting rod 33 and the lever 31 reproduce exactly the control commands or signals given by the Jacquard device, it is advantageous to make use of these movements to control the input 77.
  • the upper end of the second arm 31b is connected to the input 77 via a crank and a gear transmission 79 which transforms the reciprocating translation movement of the second arm 31b into a reciprocating rotary movement.
  • the transmission 79 comprises a crank 80 articulated, on the one hand, to the second arm 31b about a horizontal axis extending forwards and approximately parallel to the connecting rod 33, and on the other hand, to a rod 81 extendinglaterally and horizontally in a plane perpendicular to the second lever arm 31b and to the crank 80.
  • the rod 81 is fixed rigidly to a vertical shaft 82 supported by bearings 82a which are integral with the frame 1.
  • the vertical shaft 82 carries, at its lower end, a return pinion 83 which meshes with a second return pinion 84 keyed onto a horizontal shaft 85 housed in bearings 86, 87 of the self-locking reciprocating driving and selection mechanism 75.
  • the horizontal shaft 85 carries a return pinion 90 meshing with the return pinion 89 of the input 77.
  • the angular movement of the pinion 89 is notably small, but sufficient to control selectively a plurality of clutches, each of which is capable of being controlled by the vertical shaft 88 and of connecting the corresponding transmission shaft 66, 67, 68, and hence the respective control racks 42 to 47, to the input 76 constituted by a shaft, as will be explained hereinbelow.
  • the pinion 89 can occupy three different angular positions, each of which corresponds to one of the three vertical positions of the batten 16.
  • the vertical shaft 88 is positioned in bearings 92, 93.
  • a toothed segment 94 the radius of curvature of which is such that the transmission ratio between the pinion 89 and a partially toothed crown 94a of the segment 94 is sufficient to control consecutively and alternatively three clutches.
  • the segment 94 meshes by its toothed crown 940 with a rack 95 integral with a control fork 96 guided, for example, on two guide rods 97 fixed in the housing 91.
  • the control fork 96 moves in a direction parallel to the guide rods 97 and to an input power shaft 98 and a toothed wheel 99.
  • the toothed wheel 99 and the power shaft 98 constitute the input 76.
  • the power shaft 98 is housed in the housing 91 of the self-locking reciprocating driving and selection mechanism 75 and is axially immovably' mounted in three bearings 100, 101, 102. Upon the power shaft 98 there are mounted loosely, in ball bearings to 115, three cam wheels 116, 117, 118, each of which is associated with one of the outputs shafts 72, 73, 74.
  • the cam wheels 116, 117, 118 are axially immovable and each has, on its periphery, a continuous, active profile variable in the axial direction.
  • Each active profile may be constituted, for example, by an elliptical groove 119, 120,v 121 which is continuous and which determines an oblique plane relative to the axis of the power shaft 98.
  • Lateral flanks 122, 123 of each elliptical groove are perpendicular to a floor 124 thereof, the latter, when viewed parallel to the axis of the power shaft 98, is concentric therewith.
  • the external edge of the lateral flanks 122, 123, each constituting the active profile, is determined by an ellipse which constitutes the line of section between, on the one hand, a cylinder of circular cross-section concentric with the power shaft 98, and on the other hand, said oblique plane relative to the axis of the shaft 98 and containing only one straight line perpendicular to the axis of the power shaft and coincident with the minor axis of the ellipse.
  • a wheel 125, 126, 127 mounted loosely on a tenon 128, 129, 130.
  • Each tenon is perpendicular to the axis of the power shaft 98 and is integral with a carriage 131, 132, 133.
  • Each carriage 131, 132, 133 is guided, in similar manner, to the control fork 96, parallel to the power shaft 98 by means of two guide rods 134, 135 fixed to the housing 91.
  • the normal projection of the major axis of the ellipse of each groove 119, 120, 121 upon the axis of the power shaft 98 determines the maximum stroke of the respective carriage 131, 132, 133.
  • the respective carriage 131, 132, 133 comprises a straight rack 136, 137, 138 which is parallel to the axis of the power shaft 98 and which meshes with a toothed wheel 139, 140, 141 keyed onto the respective output shaft 72, 73, 74 of the self-locking reciprocating driving and selection mechanism 75.
  • Each carriage 131, 132, 133, its rack 136, 137, 138 and its toothed wheel 139, 140, 141 constitute a gear arrangement connecting the respective cam wheel 116, 117, 118 to the corresponding transmission shaft 66, 67, 68.
  • the control fork 96 comprises two lugs 142, 143, each of which is perpendicular to the power shaft 98, and each of which cooperates, at its free end, with the movable part of one of the three clutches capable of being controlled by the vertical shaft 88 and of separately connecting the transmission shafts 66, 67, 68 to the power shaft 98.
  • the movable part of each clutch is constituted by a clutch sleeve 144, 145, mounted for axial movement upon the power shaft 98, between two adjacent cam wheels 116, 117 and 117, 118, the clutch sleeve 145 being so designed as to constitute the movable part of the two clutches.
  • the lugs 142, 143 are arranged in the spaces between two adjacent cam wheels 116, 117 and 117, 118, Le, on each side of the central cam wheel 117.
  • Each clutch sleeve 144, 145 has, on its interior wall, axial ribs 144a, 145a which are engaged in respective axial splines 146, 147 provided on two sections 148, 149 of the power shaft 98, the two sections 148, 149 being situated on on each side of the central cam wheel 117.
  • the clutch sleeves 144, 145 rotate with the power shaft 98, and are axially movable relative to the latter.
  • each clutch sleeve 144, 145 On its exterior wall, each clutch sleeve 144, 145 has an annular groove 150, 151 in which the end of the respective lug 142, 143 of the control fork 96 is engaged. Each lug has, for example, a half-moon shape where it is in contact with the clutch sleeve. Furthermore, the clutch sleeve 144 has an external tooth system 152 and the sleeve 145 has two external tooth systems 153, 154 in the form of a toothed crown, each of these three tooth systems being capable of cooperating with an internal tooth system 155, 156, 157 formed in respective bosses 158, 159, 160 of the respective cam wheels 116, 117, 118.
  • the boss 159 of the central cam wheel 117 is prolonged towards the lug 143 and has, between its internal tooth system 156 and the ball bearing, 113, and internal annular groove 161 the diameter and width of which are greater than the diameter and the width of the external tooth system 153 of the clutch sleeve 145.
  • the clutch sleeve 145 has between, on the one hand, the external tooth system 153 intended to cooperate with the internal tooth system 156 of the central cam wheel 117,
  • the distances between the different internal tooth systems 155, 156, 157, on the one hand, and the external tooth systems 152, 153, 154 on the other hand, are determined in such a manner that only one cam wheel 116, 117, 118 can, at any time, be engaged with the power shaft 98, the other two cam wheels being automatically uncoupled.
  • the two cam wheels 117, 118 are uncoupled from the power shaft 98 when the cam wheel 116 is coupled thereto.
  • the external tooth system 153 of the clutch sleeve is positioned opposite the internal annular groove 161 of the boss 159 and the external tooth system 154 is positioned at a distance from the internal tooth system 157 of the boss by a distance slightly greater than the length of the cylindrical part 145b of the clutch sleeve 145.
  • the axial movement of the sleeves 144, 145 is always effected simultaneously by means of the lugs 142, 143 of the control fork 96, and these lugs bear on one or other flanks of the grooves 150, 151 of the sleeves 144, 145.
  • locking means are provided for the uncoupled cam wheels, so that the teeth of the external tooth systems 152, 154 of the clutch sleeves 144, 145 are aligned with the tooth gaps of the internal tooth systems.
  • the locking means are constituted by, on the one hand, lateral locking arms 162, 163, 164 which are integral with-the control fork 96 and which are located opposite the periphery of the respective bosses 158, 159, 160 of the cam wheels 116, 117, 118 and extend parallel to the axis of the power shaft 98.
  • the locking arms are capable of cooperating with respective locking teeth 165, 166, 167 arranged on the periphery of the bosses 158, 159, 160.
  • the locking teeth 165, 166, 167 are provided on the ends of the bosses adjacent to the clutch sleeves 144, 145 and are diametrically opposite to one another relative to the axis of the corresponding boss, so as to be position in a radial plane of the power shaft 98, the radial plane passing through the locking arms 162, 164 when the active profiles of the cam wheels 116, 117, 118 occupy one of their extreme positions corresponding to one of the two extreme positions of the carriages 131, 132, 133.
  • each locking arm 162, 163, 164 has a group of locking teeth or ribs 168, 169, 170, each of which is intended to cooperate with the corresponding external locking teeth 165, 166, 167 provided on the bosses 158, 159, 160 respectively, and to constitute the locking means of the cam wheels 116, 117,118 when they are stopped in one of their extreme positions.
  • Each of the groups of teeth or ribs 168, 169, 170 is interrupted for an axial length at least equal to the width of the corresponding external teeth 165, 166, 167 by a recess 171, 172, 173 extending perpendicularly to the power shaft 98 and permitting the rotation of the cam wheel 116, 117, 118 when (in FIG. 4, see for example the recess 171) it is positioned opposite to the corresponding external locking teeth 165, 166, 167 (see teeth 165, FIG. 4) of the cam wheel.
  • the positioning of the recesses 171, 172, 173 on the locking arms 162, 163, 164 is approximately at the same level as that of the external tooth systems 152, 153, 154 of the clutch sleeves 144, 145 so that during the temporary stoppage of the rotation of the power shaft 98, each boss 158, 159, 160 is always maintained in a definite angular position, either by the respective locking arm 162, 163, 164 or by the respective tooth system 152, 153, 154.
  • the clutch sleeves 144, 145 can be moved to couple one cam wheel and to uncouple the other two cam wheels when the power shaft 98 is not rotating.
  • the power shaft 98 rotates intermittently in the the output shaft 92 through the intermediary of its active profile, the wheel 125, the carriage 131 supporting the rack 136, and the toothed wheel 139 keyed upon output shaft 72.
  • the other two cam wheels 117, 118 are uncoupled from the power shaft 98 and remain locked by the locking arms 163, 164 in an angular position wherein their internal tooth systems 156, 157 are aligned with the tooth gaps of the external tooth systems 153, 154 of the clutch sleeve 145.
  • the periphery of the profiled pulley being likewise elliptical and determined by the intersection of a cylinder of circular cross-section coaxial with the power shaft 98 and an oblique plane relative to the axis of the power shaft, the straight line located in the oblique plane and perpendicular to the axis of the power shaft constituting the minor axis of the elliptical periphery.
  • the rack box 40 of the shuttle control device 41 is illustrated in detail in FIGS. 6 to 11.
  • the rack box 40 is provided on the left-hand end of the batten 16 and is constituted by a plurality of stringers 180, for example each of U-shaped profile and attached by its base to the base of a second stringer, the lateral arms of which are orientated downwardly. Two attached stringers then form a substantially I-shaped profile on one of the parallel wings fixed at a regular distance from a spacer or vertical bar 181.
  • a plurality of supports 182 each comprising, on its rear face, two superposed and vertically aligned bearings 183, 184 which serve as a housing for a guide rod 185.
  • the supports 182 are at least three in number and are uniformly distributed along the batten 16. Only the left-hand support 182, situated on the right-hand side of the rack box 40, is shown in the drawings.
  • the guide rod 185 is integral with the front end of the T- piece 8 which, in the case of the illustrated embodiment, is constituted by a plurality of pairs of vertically arranged triangular shaped pulleys 186, the pulleys of each pair being connected by spacer blocks 187 and bolts 188.
  • the spacer blocks 187 located on the side of the support 182 likewise serve as a housing for the rod 185 which is integral with them and is mounted slidingly in the bearings 183, 184.
  • the bearings 183, 184 include helical pitch ball bearings 189 and hence the batten 16 is guided along the rods 185 with substantially no friction.
  • a U-shaped channel bar 190 which has its arms oriented downwardly and is indented at the position of the transmission shaft 66.
  • bearings 191 are provided for guide sleeves 192, 193, 194 of the telescopic shafts 57, 58, 59.
  • the bearings 191 permits rotary movement of the telescopic shafts, but prohibit any axial movement of their sheaths 54, 55, 56.
  • each sheath 54, 55, 56 comprises two toothed wheels 48 to 53 which are keyed upon knurled sections 54, 55', 56 of the sheaths.
  • the toothed wheels 48, 49 are mounted on the knurled sections 54 of the sheath 54
  • the toothed wheels 50, 51 are mounted on the knurled sections 55' of the sheath 55
  • the toothed wheels 52, 53 are mounted upon the knurled sections 56"of the sheath 56.
  • FIG. 7 clearly shows, the axis of the telescopic shaft 57 is slightly withdrawn towards the rear with respect to the vertical plane defined by the axes of the other two telescopic shafts 58, 59.
  • the toothed wheel 48 and the toothed wheel 49 of the sheath 54 each cooperate with the control racks 42, 43, each of which is aligned and integral with a driving rack 42', 43' extending over the entire batten 16 and cooperating with toothed wheels 17', 18' associated with the groups 17, 18 of shuttles.
  • the control racks 42, 43 are guided by a plurality of guide wheels 195 mounted loosely on support tubes 196 fixed by assem bly lugs 197 upon the stringers 180, the guide wheels 195 being disposedon each side of the corresponding toothed wheel in such a way that the control rack always has two points of support while it is displaced by the toothed wheel situated on the other side of the control rack. Similar arrangements are provided for the other four control racks 44 to 47 which, by contrast,
  • the driving racks 44' to 47' are arranged parallel to the control racks 44 to 47 and are connected to the latter by respective angle irons 44" to 47".
  • the front vertical arms of the stringers have indentations 180' at the positions of the toothed wheels 48, 49, in the same way as the rear vertical arms of the said stringers have indentations at the positions of the guide wheels 195, so that the control racks 42, 43 do not rub against the arms of the stringers 180, but rest upon the wheels 195, ther peripheries of which slightly overhang the internal face of the rear arms of the stringers.
  • the shuttle control device has position adjusting means 200 for the shuttles.
  • the position adjusting means 200 comprises, for each transmission shaft 66, 67, 68, on the one hand, a pair of support arms 201 which are mutually aligned and which are mounted on the corresponding transmission shaft adjacent the upper cardan joint 63, 64, 65 and is equipped at the free ends of the arms with a guide wheel 202, and, on the other hand, guiding slideways 203 arranged at the level of the support arms 201 in front of the transmission shaft 66, 67, 68 and determining a guide plane extending parallel to the direction of movement of the batten 16.
  • the guiding slideways 203 are constituted by two L-shaped angle, irons, of which two arms 203a are arranged in two parallel vertical planes, and of which the other two arms occupy the same horizontal plane and are fixed to the lower face of a horizontal beam 204 which is integral with the frame 1 and parallel to the batten 16.
  • the slideways 203 are flared on the side of the transmission shafts to facilitate the entry of the wheels 202.
  • the transmission shafts 66, 67, 68 pivot through 180 about their axes in the direction of the double-headed arrow 205 when they pass from one extreme position to the other in the direction of the doubleheaded arrow 206, these extreme positions corresponding to the extreme positions of the shuttles. It follows that the support arms 201 with the wheels 202 of the adjusting means 200 associated with the transmission shaft which is selected and actuated for example, the transmission shaft 66 in order to cause the movement of the rows of shuttles controlled from the control racks 44, 45 (see FIG.
  • the transmission shafts 67, 68 which are not rotated execute only a translation movement in a position which is parallel to the respective slideways 203, so that the penetration of the wheels 202 into the slideways does not cause any pivoting of the transmission shafts 66, 68.
  • the wheels 202 will, in cooperation with the slideways 203, effect correction of the positioning of the shuttles so that they achieve their predetermined extreme positions.
  • FIG. 13 illustrates the intermediate transmission mechanism 78 provided between the power shaft 98 and the driving motor 2 of the loom and capable of transforming the continuous rotary movement into an intermittent rotary movement.
  • the intermediate transmission mechanism comprises two parallel horizontal shafts 220, 221 mounted in bearings 222, 223, 224, 225 integral with a housing 226 of the intermediate transmission mechanism 78.
  • the two shafts 220, 221 each comprise a chain wheel 227, 228.
  • the shaft 220 has keyed onto it at least one support arm 231 which, at its free end, is fitted with a wheel 232 capable of engaging more or less deeply and during a one quarter revolution of the shaft 220 into one of four radial grooves 233 of a Maltese Cross 234 keyed upon the shaft 221.
  • FIG. 1 A Maltese Cross 234 keyed upon the shaft 221.
  • FIG. 13 illustrates two support arms 231 mutually aligned so that during each first and third quarter revolution of the shaft 220, the shaft 221 is driven through one quarter of a revolution and the power shaft 98 through one half revolution, and that during each second and fourth quarter revolution of the shaft 220, the shaft 221 and the power shaft 98 are stationary during which the cam wheel corresponding to the row of shuttles having completed its work stroke can be uncoupled from the power shaft 98 and another cam wheel can be connected with the power shaft.
  • a shuttle control device for a loom comprising: a beam capable of executing a substantially horizontal reciprocating movement; a batten guided for vertical movement on one face of the beam and capable of occupying at least two different positions; a plurality of horizontally disposed driving racks mounted on the batten, each driving rack being arranged to act upon a group-of shuttles so as to drive the group in a horizontally reciprocating movement along the batten; a plurality of control racks, each drive rack being integral at one end with a respective one of the control racks, each control rack being meshed with a toothed wheel keyed onto a vertically disposed telescopic shaft, having an exterior sheath and an interior rod, the sheath being connected with the batten both for vertical displacement parallel to its axis and also for horizontal translation of the batten, the sliding interior rod having splines engaged in corresponding splines of the sheath; a selflocking reciprocating driving and selection mechanism having a plurality of output
  • a shuttle control device as claimed in claim 1 in which said mechanism comprises a clutch means for each output shaft, each clutch means being arranged to be controlled by the selection shaft and to connect the transmission shaft of the respective control rack to said power shaft.
  • each output shaft is permanently connected to one part of the respective clutch means by a cam wheel loosely mounted for rotation with the said part but axially-immovable with respect to the power shaft, the cam wheel having a continuous active profile variable in the axial direction and by gear means controlled by the said profile.
  • each clutch means comprises a clutch sleeve which is mounted for rotation with, but axially movable relative to the power shaft and which has at least one external tooth system, and a hollow boss integral with the respective cam wheel and having an internal tooth system cooperable with said an external tooth system of the clutch sleeve.
  • a shuttle control device as claimed in claim 4 in which the selection shaft is connected to each of the clutch sleeves via a control fork guided for movement in a direction parallel to the axis of the power shaft.
  • a shuttle control device as claimed in claim 5 in which each cam wheel has a locking means.
  • each locking means comprises first locking teeth provided on the periphery of the boss of the respective cam wheel and second locking teeth provided on the control fork and capable of engaging the locking teeth of the boss, the locking teeth of the control fork being provided with recesses extending in a direction parallel to the axis of the power shaft, the recesses being capable of being placed opposite the locking teeth of the boss when the respective clutch sleeve occupies a coupling position.
  • control fork comprises a rack meshing with a toothed segment keyed onto the selection shaft.
  • control fork includes a plurality of lugs, each of which is permanently engaged in an annular groove of one of the clutch sleeves.
  • each of the clutch sleeves has, at each end, an
  • a shuttle control device as claimed in claim 3 in which the gear means connecting each cam wheel to the transmission shaft comprises a carriage guided parallel to the axis of the power shaft and carrying a rack meshing with a toothed wheel keyed to said output shaft, said output shaft being connected by a cardan joint to the transmission shaft.
  • a shuttle control device as claimed in claim 11 in which the active profile of each cam wheel is constituted by an elliptical groove situated on a circular cylinder, the axis of which coincides with that of the power shaft, a wheel mounted for rotation on a tenon I integral with the respective carriage being engaged in the said groove and cooperable with one or other of the flanks of the said groove.
  • a shuttle control device as claimed in claim 11 in which the active profile of each cam wheel is constituted by the periphery of a pulley or an elliptical disc, the periphery being determined by the intersection between a circular cylinder the axis of which coincides with that of the power shaft and an oblique plane relative to the axis of said cylinder, the periphery being surmounted by two wheels each mounted on a tenon integral with the respective carriage and cooperable with one or other of the two flanks of the pulley or elliptical disc.
  • a shuttle control device as claimed in claim 1 in which the selection shaft is connected to the said mechanism to cause the vertical movement of the batten.
  • a shuttle control device as claimed in claim 1 in which the power shaft is connected to a principal driving driving shaft or to the drive motor via transmission means arranged to transform continuous rotary movement of the principal driving shaft or the drive motor into an intermittent rotary movement.
  • each control rack is arranged to be guided in a rack box by means of two guiding wheels arranged on each side of the said toothed wheel of the control rack.
  • a shuttle control device as claimed in claim 1 in which the batten is arranged to be guided by a plurality of rods integral with at least one T-piece of the loom and by a plurality of ball bearings, said ball bearings being arranged helically around each of said plurality of rods.
  • a shuttle control device as claimed in Claim 1 including adjusting means for adjusting the longitudinal position of the shuttles.
  • a shuttle control device as claimed in claim 18 in which the position adjusting means comprises a pair of support arms defining an angle therebetween equal to the maximum angle of rotation of the transmission shaft, each arm carrying a wheel at its free end, and a guiding slideway arranged at the level of the support arms and determining guiding planes extending parallel to the direction of movement of the batten, the slideway being arranged in such a manner that when one of the said wheels is engaged in the slideway, the shuttles occupy one of two extreme positions.

Landscapes

  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Looms (AREA)
  • Transmission Devices (AREA)
US00286700A 1971-09-06 1972-09-06 Shuttle control device for a loom Expired - Lifetime US3856055A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR7132161A FR2152353B1 (enrdf_load_stackoverflow) 1971-09-06 1971-09-06

Publications (1)

Publication Number Publication Date
US3856055A true US3856055A (en) 1974-12-24

Family

ID=9082566

Family Applications (1)

Application Number Title Priority Date Filing Date
US00286700A Expired - Lifetime US3856055A (en) 1971-09-06 1972-09-06 Shuttle control device for a loom

Country Status (6)

Country Link
US (1) US3856055A (enrdf_load_stackoverflow)
JP (1) JPS4835166A (enrdf_load_stackoverflow)
CH (1) CH562348A5 (enrdf_load_stackoverflow)
DE (1) DE2242897C3 (enrdf_load_stackoverflow)
FR (1) FR2152353B1 (enrdf_load_stackoverflow)
GB (1) GB1404856A (enrdf_load_stackoverflow)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3963060A (en) * 1975-01-21 1976-06-15 Crompton & Knowles Corporation Shuttle drive for a narrow ware loom
US20170121865A1 (en) * 2015-10-29 2017-05-04 Staubli Faverges Shedding mechanism comprising a level adjustment device and weaving machine including said mechanism
US10287712B2 (en) * 2016-07-22 2019-05-14 Staubli Faverges Shed forming machine and loom including such a machine
CN112962223A (zh) * 2021-01-29 2021-06-15 鹤山市新易高鞋业有限公司 一种新型鞋底缝纫装置
CN114964893A (zh) * 2022-07-27 2022-08-30 农业农村部南京农业机械化研究所 一种西甜瓜拱棚插架种植用的土壤检测取样装置

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US641605A (en) * 1898-05-09 1900-01-16 Edwin Oldfield Narrow-fabric loom.
US781967A (en) * 1904-06-18 1905-02-07 Crompton & Knowles Loom Works Narrow-ware loom.
US786237A (en) * 1903-10-05 1905-03-28 Otto W Schaum Narrow-ware loom.
US1278226A (en) * 1917-01-15 1918-09-10 Schaum & Uhlinger Inc Loom.
GB425494A (en) * 1933-11-08 1935-03-15 Hubert Haywood Improvements in and relating to multiple shuttle narrow fabric looms
FR978639A (fr) * 1949-01-03 1951-04-16 Louis Masson Fils De Dispositif de commande du va-et-vient des navettes dans les métiers à tisser les rubans
FR978640A (fr) * 1949-01-03 1951-04-16 Louis Masson Fils De Entraîneur de navettes dans les métiers à tisser les rubans

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US641605A (en) * 1898-05-09 1900-01-16 Edwin Oldfield Narrow-fabric loom.
US786237A (en) * 1903-10-05 1905-03-28 Otto W Schaum Narrow-ware loom.
US781967A (en) * 1904-06-18 1905-02-07 Crompton & Knowles Loom Works Narrow-ware loom.
US1278226A (en) * 1917-01-15 1918-09-10 Schaum & Uhlinger Inc Loom.
GB425494A (en) * 1933-11-08 1935-03-15 Hubert Haywood Improvements in and relating to multiple shuttle narrow fabric looms
FR978639A (fr) * 1949-01-03 1951-04-16 Louis Masson Fils De Dispositif de commande du va-et-vient des navettes dans les métiers à tisser les rubans
FR978640A (fr) * 1949-01-03 1951-04-16 Louis Masson Fils De Entraîneur de navettes dans les métiers à tisser les rubans

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3963060A (en) * 1975-01-21 1976-06-15 Crompton & Knowles Corporation Shuttle drive for a narrow ware loom
US20170121865A1 (en) * 2015-10-29 2017-05-04 Staubli Faverges Shedding mechanism comprising a level adjustment device and weaving machine including said mechanism
US9873961B2 (en) * 2015-10-29 2018-01-23 Staubli Faverges Shedding mechanism comprising a level adjustment device and weaving machine including said mechanism
US10287712B2 (en) * 2016-07-22 2019-05-14 Staubli Faverges Shed forming machine and loom including such a machine
CN112962223A (zh) * 2021-01-29 2021-06-15 鹤山市新易高鞋业有限公司 一种新型鞋底缝纫装置
CN114964893A (zh) * 2022-07-27 2022-08-30 农业农村部南京农业机械化研究所 一种西甜瓜拱棚插架种植用的土壤检测取样装置
CN114964893B (zh) * 2022-07-27 2022-09-30 农业农村部南京农业机械化研究所 一种西甜瓜拱棚插架种植用的土壤检测取样装置

Also Published As

Publication number Publication date
CH562348A5 (enrdf_load_stackoverflow) 1975-05-30
DE2242897A1 (de) 1973-04-12
FR2152353A1 (enrdf_load_stackoverflow) 1973-04-27
DE2242897B2 (de) 1978-03-23
JPS4835166A (enrdf_load_stackoverflow) 1973-05-23
DE2242897C3 (de) 1978-11-16
FR2152353B1 (enrdf_load_stackoverflow) 1974-08-19
GB1404856A (en) 1975-09-03

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