EP2553153B1 - Antrieb und verfahren für den antrieb von greiferträgern - Google Patents

Antrieb und verfahren für den antrieb von greiferträgern Download PDF

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Publication number
EP2553153B1
EP2553153B1 EP11709704.8A EP11709704A EP2553153B1 EP 2553153 B1 EP2553153 B1 EP 2553153B1 EP 11709704 A EP11709704 A EP 11709704A EP 2553153 B1 EP2553153 B1 EP 2553153B1
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EP
European Patent Office
Prior art keywords
gripper
drive
respect
reversing point
taker
Prior art date
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Application number
EP11709704.8A
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English (en)
French (fr)
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EP2553153A2 (de
Inventor
Patrick Strubbe
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Picanol NV
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Picanol NV
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Publication of EP2553153A2 publication Critical patent/EP2553153A2/de
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Publication of EP2553153B1 publication Critical patent/EP2553153B1/de
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    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D47/00—Looms in which bulk supply of weft does not pass through shed, e.g. shuttleless looms, gripper shuttle looms, dummy shuttle looms
    • D03D47/12—Looms in which bulk supply of weft does not pass through shed, e.g. shuttleless looms, gripper shuttle looms, dummy shuttle looms wherein single picks of weft thread are inserted, i.e. with shedding between each pick
    • D03D47/18—Looms in which bulk supply of weft does not pass through shed, e.g. shuttleless looms, gripper shuttle looms, dummy shuttle looms wherein single picks of weft thread are inserted, i.e. with shedding between each pick two weft inserters meeting at or near the middle of the shed and transferring the weft from one to the other
    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D47/00—Looms in which bulk supply of weft does not pass through shed, e.g. shuttleless looms, gripper shuttle looms, dummy shuttle looms
    • D03D47/27—Drive or guide mechanisms for weft inserting
    • D03D47/275—Drive mechanisms
    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D47/00—Looms in which bulk supply of weft does not pass through shed, e.g. shuttleless looms, gripper shuttle looms, dummy shuttle looms
    • D03D47/27—Drive or guide mechanisms for weft inserting
    • D03D47/275—Drive mechanisms
    • D03D47/276—Details or arrangement of sprocket wheels

Definitions

  • the invention relates to a drive and a method for driving a gripper carrier for a bringer gripper and a gripper carrier for a taker gripper by means of a drive, which comprises a common drive motor for two drive mechanisms and two drive wheels each driven by an associated drive mechanism for a gripper carrier, wherein the gripper carriers are driven so that the bringer gripper and the taker gripper each reciprocate between an outer reversing point situated outside the shed and an inner reversing point situated inside the shed.
  • a drive mechanism for a gripper carrier is known.
  • a method for driving a gripper carrier and a drive for a gripper carrier according to the preamble of claim 1 and 6 are shown in JP 9-137338 A .
  • the drive wheel for the gripper carrier for the bringer gripper and the drive wheel for the gripper carrier for the taker gripper carry out a so-called "symmetrical" movement, in which the bringer gripper and the taker gripper move towards one another in the opposite direction, wherein the bringer gripper and the taker gripper meet one another approximately in the center of the shed and wherein the bringer gripper and the taker gripper subsequently move away from one another again in the opposite direction.
  • a gripper carrier may, for example, consist of a gripper band or of a gripper bar.
  • the object of the invention is to improve an abovementioned method in such a manner that an "asymmetrical" movement by a bringer gripper and a taker gripper is maintained without independent drive motors having to be provided for this purpose and wherein the bringer gripper and the taker gripper may insert a weft thread at a relatively low speed.
  • the invention not only has the advantage that a drive is provided with a common drive motor for the bringer gripper and the taker gripper, but also that the bringer gripper can enter the shed slower and that the taker gripper can leave the shed slower.
  • the movements of the bringer gripper and of the taker gripper are be dephased to such an extent that the outer reversing point of the bringer gripper is ahead of the outer reversing point of the taker gripper by several machine degrees.
  • the bringer gripper does not necessarily enter the shed sooner and the taker gripper does not necessarily leave the shed later.
  • the invention is particularly advantageous if the weaving machine is set to weave at maximum weaving width, more particularly if weaving takes place at virtually the maximum weaving width.
  • the method according to the invention allows, when the weaving machine weaves at a certain speed, to move the bringer gripper and the taker gripper at a relatively low speed at a certain weaving width when they insert a weft thread, which is particularly advantageous when weaving at relatively large weaving widths.
  • the object of the invention is achieved in that, at least at a setting for maximum weaving width, with respect to the weaving cycle, the outer reversing point of the bringer gripper is ahead of the outer reversing point of the taker gripper.
  • the gripper carrier for the bringer gripper and the gripper carrier for the taker gripper are driven at a variable speed by the common drive motor of the drive during their movements into the shed and out of the shed, wherein with respect to the weaving cycle, the bringer gripper is accelerated less after the outer reversing point than after the inner reversing point and wherein, with respect to the weaving cycle, the taker gripper is accelerated more after the outer reversing point than after the inner reversing point.
  • a movement into the shed is intended to mean that the bringer gripper and/or the taker gripper move towards the inner reversing point
  • the expression “a movement out of the shed” is intended to mean that the bringer gripper and/or the taker gripper move towards the outer reversing point.
  • This method is particularly advantageous since it allows to initially accelerate a bringer gripper less while picking up a weft thread which is held ready outside the shed in order to subsequently move at a higher speed in the shed. In this case, the bringer gripper moves relatively slowly during picking up of a weft thread and the taker gripper moves relatively slowly during the release of a weft thread.
  • the inner reversing point of the taker gripper is ahead of the inner reversing point of the bringer gripper.
  • the gripper carrier for the bringer gripper and the gripper carrier for the taker gripper are driven at variable speed by a common drive motor of the drive during their movements into the shed and out of the shed, wherein with respect to the weaving cycle, the bringer gripper before its inner reversing point and the taker gripper after its inner reversing point move in the same direction over a distance.
  • the variable speeds of the bringer gripper and the taker gripper it is ensured in this case that the bringer gripper and the taker gripper meet each other near the center of the shed and move in the same direction over a distance.
  • the outer reversing point of the bringer gripper is situated several machine degrees before the beat-up and the outer reversing point of the taker gripper is situated several machine degrees after the beat-up.
  • beat-up in this case is intended to mean the moment during the weaving cycle, more particularly, the angular position of the weaving machine wherein a weft thread is beaten-up by the weaving reed that is driven by the sley.
  • machine degrees is in this case intended to mean the degrees of the weaving machine which are determined by the drive motor and which, for one weaving cycle, vary successively between 0° and 360°.
  • the bringer gripper leaves the shed a number of machine degrees before beat-up and the bringer gripper enters the shed a number of, for example the same number of, machine degrees after beat-up, while the outer reversing point of the bringer gripper is situated several machine degrees before beat-up.
  • the taker gripper leaves the shed a number of machine degrees before beat-up and the taker gripper enters the shed within a number of, for example the same number of, machine degrees after beat-up, while the outer reversing point of the taker gripper is situated several machine degrees after beat-up.
  • the bringer gripper and the taker gripper can enter the shed as early as possible and can also leave the shed as late as possible, wherein a required average speed of the bringer gripper and/or of the taker gripper is relatively low for a given speed of the weaving machine, that is to say at a given number of insertions per unit time.
  • a drive for a gripper carrier for a bringer gripper and for a gripper carrier for a taker gripper which drive comprises a common drive motor for two drive mechanisms and two drive wheels for a gripper carrier which are each driven by an associated drive mechanism, wherein each drive mechanism comprises a crank which drives a fork element, wherein the fork element and a cross element are mounted rotatably with respect to one another via a shaft, wherein the cross element is connected to a toothed segment which drives a drive wheel for a gripper carrier and which, together with the cross element, is mounted rotatably with respect to a frame of the drive mechanism, wherein the cross element and the frame of the drive mechanism are mounted rotatably with respect to one another via a shaft which is arranged transversely to the shaft by means of which the fork element and the cross element are mounted rotatably with respect to one another, wherein each crank is driven in a rotationally fixed manner by the common drive motor at a certain angular position with respect to the
  • the adjusting according to the invention of the angles between each crank and associated fork element, of the angles between the two shafts assigned to each cross element and of the angular positions in which each crank is driven with respect to the common drive motor results in the advantage of an asymmetrical gripper movement being achieved with a common drive motor, wherein the bringer gripper and the taker gripper are still able to insert a weft thread in a shed at a relatively low speed and with relatively low accelerations. This is particularly advantageous when the weaving machine weaves at high speeds and with large weaving widths.
  • the two shafts assigned to the cross element are fitted on the cross element, more particularly are formed as a single part with the cross element.
  • a drive having a common drive motor for two drive wheels driven by an associated drive mechanism allows both drive wheels to be moved with respect to the weaving cycle as a function of the angular position of the drive motor and as a function of the properties of the drive mechanism according to the invention.
  • the expression "driven in a rotationally fixed manner" is intended to mean that the course of the angular position of the drive mechanism is determined by the course of the angular position of the drive motor.
  • the two shafts assigned to the cross element are arranged at an angle with respect to one another which deviates by a few angular degrees from 90°, i.e. the shaft by means of which the fork element and the cross element are mounted rotatably with respect to one another forms an angle which deviates from 90° with the shaft, by means of which the cross element and the frame for the drive mechanism are mounted rotatably with respect to one another, in such a manner that, with respect to the weaving cycle, the bringer gripper is accelerated less after the outer reversing point than after the inner reversing point and that the taker gripper is accelerated more after the outer reversing point than after the inner reversing point. With respect to the weaving cycle, this allows that the bringer gripper and the taker gripper may enter the shed as early as possible and also may leave the shed as late as possible.
  • the two shafts assigned to the cross element are arranged at an angle with respect to one another which deviates by a few angular degrees from 90° and/or the angular positions of the cranks of the drive mechanisms are set with respect to the angular position of the drive motor in such a manner that, with respect to the weaving cycle, the gripper carrier for the bringer gripper and the gripper carrier for the taker gripper are driven at variable speed by the drive during their movements into the shed and out of the shed, wherein with respect to the weaving cycle, the bringer gripper before its inner reversing point and the taker gripper after its inner reversing point move over a distance in the same direction.
  • the two shafts assigned to the cross element are arranged at an angle with respect to one another which deviates by a few angular degrees from 90° and/or the angular positions of the cranks of the drive mechanisms are set with respect to the angular position of the drive motor in such a manner that, with respect to the weaving cycle, the inner reversing point of the taker gripper is ahead of the inner reversing point of the bringer gripper.
  • the two shafts assigned to the cross element are arranged at an angle with respect to one another which deviates by a few angular degrees from 90° and/or the angular positions of the cranks of the drive mechanisms are set with respect to the angular position of the drive motor in such a manner that the outer reversing point of the bringer gripper is situated several machine degrees before beat-up and that the outer reversing point of the taker gripper is situated several machine degrees after beat-up.
  • the two shafts assigned to the cross element are arranged at an angle of approximately 4° displaced with respect to an angle of 90°.
  • the shaft by means of which the fork element and the associated crank are mounted rotatably with respect to one another, forms an angle which deviates by a few angular degrees from 45°, for example an angle of approximately 48°, with the shaft by means of which the cross element and the fork element are mounted rotatably with respect to one another. This allows the bringer gripper and the taker gripper to be moved, with respect to a weaving cycle, over a desired distance in the shed.
  • the shaft which connects the crank and the fork element and the two shafts assigned to the cross element preferably pass through a common point.
  • the cranks of the two drive mechanisms are driven in a rotationally fixed manner by a common drive shaft, wherein the crank of the drive mechanism for the bringer gripper is arranged, in the drive direction of the drive shaft, so that it is ahead of the crank of the drive mechanism for the taker gripper by a few machine degrees.
  • the drive mechanism for the bringer gripper and the drive mechanism for the taker gripper are of identical design. This makes an easy assembly of a drive for a weaving machine possible.
  • the object is furthermore achieved by a weaving machine which comprises a drive according to the invention.
  • Figure 1 shows a drive 1 for a gripper carrier 2 for a bringer gripper 3 and for a gripper carrier 4 for a taker gripper 5.
  • a drive 1 may be used in a weaving machine, in particular in a gripper weaving machine.
  • the drive 1 comprises a common drive motor 6 which drives two gear wheels 8 and 9 via a drive shaft 7.
  • the drive mechanism 10 which drives the drive wheel 14 for the gripper carrier 2 is driven by the drive motor 6 via the gear wheel 8, while the drive mechanism 11 which drives the drive wheel 15 for the gripper carrier 4 is driven by the drive motor 6 via the gear wheel 9.
  • Figures 1 , 2 , 3 , 5 and 6 show the drive mechanism 10 which comprises a gear wheel 12 which can be driven by the gear wheel 8, a crank 13 connected to the gear wheel 12, a fork element 16 assigned to the crank 13 and a cross element 17 assigned to the fork element 16.
  • the cross element 17 is connected to a toothed segment 22 which can drive the drive wheel 14 for the bringer gripper 3 via a gear wheel transmission 18.
  • Such a crank 13 and gear wheel transmission 18 are known, for example, from DE 10346227 A1 .
  • the crank 13 can be connected to the gear wheel 12 via a bearing half 19, illustrated in Figure 6 , in an adjustable position, in such a manner that the crank 13 is arranged rotatably to the gear wheel 12.
  • the crank 13 drives the fork element 16, wherein the crank 13 and the fork element 16 are mounted rotatably with respect to one another via the shaft 23.
  • the cross element 17 is driven by the fork element 16 via a shaft 20 with an axis 44, illustrated in Figures 3 and 5 , which is mounted in the fork element 16, wherein the fork element 16 and the cross element 17 are mounted rotatably with respect to one another via the shaft 20.
  • the cross element 17 is together with the toothed segment 22 mounted rotatably about a shaft 21 with an axis 45, illustrated in Figure 3 , which shaft 21 is arranged transversely with respect to the shaft 20.
  • the shaft 21 is mounted rotatably with respect to a frame 42, wherein the cross element 17 and the frame 42 are mounted rotatably with respect to one another via the shaft 21.
  • the frame 42 can be fixedly attached to the frame (not shown) of the drive mechanism 10 of the weaving machine.
  • the axes 43, 44 and 45 of the respective shafts 23, 20 and 21 pass through a common point 36, as is illustrated in Figures 3 and 5 .
  • the shaft 21 is formed by two axle stubs 56 and 57 which are fitted on the cross element 17 and which can be mounted with respect to the frame 42 via bearings 58, 59, which are illustrated in Figures 3 , 5 and 6 .
  • the shaft 20 is formed by two axle stubs 24 and 25 which are fitted on the cross element 17 and which can be mounted with respect to the fork element 16 via bearings.
  • the fork element 16 comprises two legs 60 and 61, in which an axle stub 24 or 25 can be mounted, respectively.
  • the shaft 23 with axis 43 by means of which the fork element 16 and the crank 13 are mounted rotatably with respect to one another forms an angle 53 which deviates by a few angular degrees from 45°, for example an angle of approximately 48°, with respect to the shaft 20 with axis 44 by means of which the cross element 17 and the fork element 16 are mounted rotatably with respect to one another.
  • Figure 4 shows a top view along arrow D from Figure 1 of the drive mechanism 11 which is of identical design to the drive mechanism 10, but is arranged angularly offset about 180° with respect to the drive mechanism 10.
  • the drive mechanisms 10 and 11 are arranged in such a manner that the axis 44 of the shaft 20 of the drive mechanism 10 and the axis 50 of the shaft 48 of the drive mechanism 11 are arranged virtually parallel to one another, in a top view.
  • the gear wheel 26 of the drive mechanism 11 is driven via the gear wheel 9 and the toothed segment 47 of the drive mechanism 11 drives the drive wheel 15 for the taker gripper 5 via a gear wheel transmission 27.
  • the axis 62 of the shaft 55 by means of which the fork element 54 and the crank 28 are mounted rotatably with respect to one another forms an angle 63 of approximately 48° with respect to the axis 50 of the shaft 48 by means of which the cross element 52 and the fork element 54 are mounted rotatably with respect to one another.
  • the shafts 20 and 21 with axes 44 and 45 and the shafts 48 and 49 with axes 50 and 51 of each cross element 17 and 52 for each drive mechanism 10 and 11 are arranged at an angle 37, 64 with respect to one another which deviates by a few angular degrees from 90°.
  • the perpendicular 82, 83 to the shafts 45 and 51 is illustrated in the Figures 3, 4 , 7 and 8 as a dot-dashed line.
  • the shafts 20 and 21 and the shafts 48 and 49 of each cross element 17, 52 are arranged at an angle 37 and 64, respectively, of approximately 4° displaced with respect to an angle of 90°.
  • the crank 13 can be driven by the drive motor 6 in a certain angular position with respect to the angular position of the drive motor 6.
  • the gear wheels 12 and 26 are driven by the drive motor 6 in the drive direction R.
  • the gear wheel 12 to which the crank 13 of the drive mechanism 10 is attached and the gear wheel 26 to which the crank 28 of the drive mechanism 11 is attached are set angularly displaced by angles 67 and 68 with respect to a reference position, for example a reference position determined by an angular position wherein the crank 13, 28 is attached to a gear wheel 12, 26 and thus set at a certain angular position with respect to the angular position of the drive motor 6, as is illustrated in Figure 1 , so that the cranks 13 and 28 of the two drive mechanisms 10 and 11 are driven in associated angular positions by the drive motor 6 via the drive shaft 7 in a rotationally fixed manner and dephased with respect to one another.
  • a reference position for example a reference position determined by an angular position wherein the crank 13, 28 is attached to a gear wheel 12, 26 and thus set at a certain angular position with respect to the angular position of the drive motor 6, as is illustrated in Figure 1 , so that the cranks 13 and 28 of the two drive mechanisms 10 and 11 are driven in associated
  • the gear wheel 8 can be fitted to this end to the drive shaft 7 via a clamping connection 65 and the gear wheel 9 via a clamping connection 66.
  • Each clamping connection 65, 66 allows the gear wheel 8, 9 to be fixedly attached in a certain angular position with respect to the drive shaft 7, so that both gear wheels 8, 9 can be attached in a certain mutual angular position with respect to the drive shaft 7.
  • one of the abovementioned gear wheels can be formed as a single part with the drive shaft 7, while the other gear wheel can be connected to the drive shaft 7 via an abovementioned clamping connection.
  • the angular positions of the cranks 13, 28 of the drive mechanisms 10, 11 can be set with respect to the angular position of the drive motor 6, so that the mutual angular position between the cranks 13, 28 can be set.
  • the drive shaft 7 can be formed by two shaft ends which are arranged in line with one another and which can be connected to one another by a clamping connection 84, as indicated schematically by a dashed line in Figure 10 , in different mutual angular positions, wherein each time one of the gear wheels 8, 9 is fitted on one of the shaft ends, so that the mutual angular position between the gear wheels 8, 9 and thus also between the cranks 13, 28 can be set.
  • a drive shaft 85 may be provided on which the gear wheels 12 and 26 are fitted.
  • the gear wheel 12 may, for example, be formed as a single part with the drive shaft 85, and the gear wheel 26 may be connected to the drive shaft 85 via a clamping connection.
  • the gear wheel 12 is in this case driven by the drive motor 6 via the gear wheel 8, while the gear wheel 26 is driven by the drive motor 6 via the gear wheel 8, the gear wheel 12 and the drive shaft 85.
  • the gear wheel 9, the clamping connection 66 and the part of the drive shaft 7 situated between the gear wheel 8 and the gear wheel 9 may be omitted.
  • the bringer gripper 3 and the taker gripper 5 are intended to move into and out of a shed 29.
  • a shed 29 is formed by planes of warp threads 30 and 31 which converge at the location of the beat-up line 32 of the fabric 33.
  • the drive mechanisms 10 and 11 allow the bringer gripper 3 and the taker gripper 4 each to reciprocate between an outer reversing point situated outside the shed 29 and an inner reversing point situated inside the shed 29.
  • the gripper carrier 2 for the bringer gripper 3 and the gripper carrier 4 for the taker gripper 5 move at a variable speed with respect to the weaving cycle when these are driven by the drive motor 6 of the drive 1 in the drive direction R.
  • the bringer gripper 3 and the taker gripper 5 move at a variable speed during their movements into the shed 29 and out of the shed 29.
  • FIG 11 a diagram of a movement path 38 of a bringer gripper 3 and a movement path 39 of a taker gripper 5 is shown.
  • Figure 12 the movement path 38 of the bringer gripper 3 and the movement path 39 of the taker gripper 4 are shown, in the vicinity of the outer reversing points I, III.
  • These movement paths 38 and 39 can be achieved with the drive mechanisms 10 and 11, as illustrated in Figures 1 to 10 .
  • the arrangement of the shafts 20 and 21, the shafts 48 and 49 and/or the setting of the mutual angular position between the gear wheels 12 and 26 with respect to the drive motor 6, allow to achieve a movement path 38 or 39 wherein with respect to the weaving cycle, i.e. according to the drive direction R of the drive motor 6, the outer reversing point I of the bringer gripper 3 is ahead of the outer reversing point III of the taker gripper 5.
  • the reversing point I is ahead of the reversing point III by an angular difference 40, wherein this angular difference is for example approximately 18°.
  • this angular difference 40 corresponds to a certain time difference.
  • the crank 13 of the drive mechanism, 10 for the bringer gripper 3, which is driven via the gear wheels 8 and 12 is fitted so that it is ahead with respect to the crank 28 of the drive mechanism 11 for the taker gripper 5 by some machine degrees, which is driven via the gear wheels 9 and 26.
  • the being ahead of the outer reversing point I of the bringer gripper 3 with respect to the outer reversing point III of the taker gripper 5 is also achieved by the drive mechanisms 10 and 11, more particularly by the angle 37 between both shafts 20 and 21 of the cross element 17 of the drive mechanism 10 and/or the angle 64 between both shafts 48 and 49 of the cross element 52 of the drive mechanism 11.
  • the outer reversing point I of the bringer gripper 3 is situated several machine degrees, for example 8°, before beat-up 34 and the outer reversing point III of the taker gripper 5 is situated several machine degrees, for example 10°, after beat-up 34.
  • the beat-up 34 corresponds to the angular position 0° or 360° of the weaving machine or the moment in the weaving cycle wherein a weft thread is beaten up.
  • the bringer gripper 3 is accelerated less after the outer reversing point I than after the inner reversing point II and the taker gripper 5 is accelerated more after the outer reversing point III than after the inner reversing point IV.
  • the bringer gripper 3 near the outer reversing point I and the taker gripper 5 near the inner reversing point IV are accelerated less, when they interact with the weft thread, which is advantageous for inserting a weft thread into a shed 29 by means of a bringer gripper 3 and a taker gripper 5.
  • Figure 11 also shows that, with respect to the weaving cycle, the inner reversing point IV of the taker gripper 5 is ahead of the inner reversing point II of the bringer gripper 3.
  • the reversing point IV is ahead of the reversing point II by an angular difference 41, wherein this angular difference is, for example, approximately 10°.
  • the bringer gripper 3 before its inner reversing point II and the taker gripper 5 after its inner reversing point IV move in the same direction over a distance 35, more particularly along the direction of insertion of the weft thread, which distance 35 is determined by the angular difference 41.
  • the hatched area 69 is determined by the angular positions in machine degrees in the weaving cycle and the longitudinal positions, i.e. positions with respect to the weaving width, in which a weaving reed 86 which is schematically illustrated in Figure 1 moves near the beat-up 34 up to a beat-up line 32 and beyond the movement path 87, indicated in Figure 1 by a dot-dashed line, of the bringer gripper 3 and/or of the taker gripper 4.
  • the weaving reed 85 moves between the beat-up line 32 and a rearmost position. In Figure 1 , the weaving reed 85 is illustrated in the rearmost position.
  • the bringer gripper 3 and the taker gripper 4 from the angular position 70 to the angular position 71, may not be situated between the longitudinal positions 76 and 77 in the shed 29, as these could otherwise come into contact with the weaving reed 86 or with the warp threads 30, 31.
  • the outer reversing point I of the bringer gripper 3 is several machine degrees ahead of the beat-up 34, in this embodiment, the bringer gripper 3 and the taker gripper 4 leave the area 69 at the angular position 70 and they enter the area 69 at the angular position 71, wherein the angular positions 70 and 71 are each situated, for example, an identical number of machine degrees away from the beat-up 34.
  • the number of machine degrees 72 and 73, and 74 and 75, respectively, are different, the number of machine degrees 78 and 79, and 80 and 81, respectively, are identical.
  • the available machine degrees are used in an optimum manner in order to achieve a relatively low average speed of the bringer gripper 3 and/or the taker gripper 4 for a certain number of insertions per unit time, while a weft thread can be inserted into a shed 29 by the bringer gripper 3 and the taker gripper 4 at a relatively low speed and acceleration.
  • the setting of the crank 13 with respect to the gear wheel 12 and/or the setting of the crank 28 with respect to the gear wheel 26 can be changed slightly.
  • the setting of the gear wheel 8 with respect to the drive shaft 7 and/or the setting of the gear wheel 9 with respect to the drive shaft 7 can also be changed.
  • Such a meshing position may, for example, be changed by displacing a gear wheel 8, 9 axially with respect to the drive shaft 7 until the teeth of the gear wheel 8, 9 no longer mesh with teeth of a gear wheel 12, 26, and by subsequently allowing the teeth of the gear wheel 8, 9 to mesh with other teeth of a gear wheel 12, 26.
  • Such adjustments can be carried out in such a manner that the features of the claims are met.
  • Figure 13 shows a variant for weaving at a more limited weaving width.
  • the position of the crank 28 with respect to the bearing half 19 is adjusted in such a way that, with respect to the movement course according to the setting of Figure 11 , the movement course 46 along which the taker gripper 5 is moved is reduced.
  • the angle by which the outer reversing point I of the bringer gripper 3 is ahead of the outer reversing point III of the taker gripper 5 can be increased again by suitably setting the angular positions of at least one of the cranks 13, 28 with respect to the angular position of the drive motor 6, for example by attaching the gear wheels 8 or 9 on the drive shaft 7 at a suitable angular position.
  • the invention is particularly suitable for use with relatively wide weaving machines and with weaving machines wherein the bringer gripper 3 and/or the taker gripper 4 are opened positively during gripping, changeover or release of the weft thread.
  • This positive opening can be carried out with devices which act on the clamp of a respective bringer gripper 3 or taker gripper 5.
  • Such devices are known, inter alia, from GB 2059455 and EP 0526390 A1 .
  • the drive 1 according to the invention has the particular advantage that the speed and the acceleration of the bringer gripper 3 are relatively limited during gripping of a weft thread.
  • the speed and the acceleration of the taker gripper 5 can be relatively limited during the release of the weft thread.
  • the drive 1 according to the invention allows the bringer gripper 3 and the taker gripper 5 to move in the same direction and at virtually the same speed for a certain period of time during the changeover, more particularly allows them to perform an overlapping movement, there is sufficient time available to changeover a weft thread in a satisfactory manner from the bringer gripper 3 to the taker gripper 5.
  • the bringer gripper 3 and the taker gripper 5 are more accelerated and/or slowed down when they do not cooperate with the weft thread than when they do cooperate with the weft thread, which allows to insert weft threads into a shed 29 at a reduced tension.
  • the taker gripper 5 can enter the shed 29, for example, sooner than the bringer gripper 3 and during opening of the shed 29. In this case, the taker gripper 5 can also leave the shed 29 later than the bringer gripper 3 and during the closing of the shed 29. If the taker gripper 5 has smaller dimensions than the bringer gripper 3, the taker gripper 5 can enter the shed 29, for example, sooner than the bringer gripper 3 and while the weaving reed is moving away from the beat-up line 32. In this case, the taker gripper 5 can also leave the shed 29 later than the bringer gripper 3 and while the weaving reed is moving towards the beat-up line 32.
  • a weaving machine allows that, at a certain speed of the weaving machine, the taker gripper 5 moves through the shed 29 over a larger movement course than the movement course with which the bringer gripper 3 moves through the shed 29, while both the bringer gripper 3 and the taker gripper 5, on average, move at a lower speed through the shed 29 when they are inserting a weft thread into the shed 29 than when they move through the shed 29 without a weft thread.

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  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Looms (AREA)
  • Braiding, Manufacturing Of Bobbin-Net Or Lace, And Manufacturing Of Nets By Knotting (AREA)

Claims (15)

  1. Ein Verfahren zum Antreiben eines Greiferträgers (2) für einen Gebergreifer (3) und eines Greiferträgers (4) für einen Nehmergreifer (5) mittels eines Antriebs (1), welcher Antrieb (1) einen gemeinsamen Antriebsmotor (6) für zwei Antriebsmechanismen (10, 11) und zwei Antriebsräder (14, 15) enthält, die jeweils durch einen zugehörigen Antriebsmechanismus (10, 11) für einen Greiferträger (2, 4) angetrieben werden, wobei die Greiferträger (2, 4) so angetrieben werden, dass der Gebergreifer (3) und der Nehmergreifer (5) sich jeweils zwischen einem äußeren Umkehrpunkt (I, III), der außerhalb des Webfachs (29) gelegen ist, und einem inneren Umkehrpunkt (II, IV), der innerhalb des Webfachs (29) gelegen ist, hin und her bewegen, dadurch gekennzeichnet, dass bezüglich eines Webzyklus der äußere Umkehrpunkt (I) des Gebergreifers (3) vor dem äußeren Umkehrpunkt (III) des Nehmergreifers (5) ist.
  2. Das Verfahren nach Anspruch 1, dadurch gekennzeichnet, dass der Greiferträger (2) für den Gebergreifer (3) und der Greiferträger (4) für den Nehmergreifer (5) bei ihren Bewegungen in das Webfach (29) und aus dem Webfach (29) durch den Antrieb (1) mit variabler Geschwindigkeit angetrieben werden, wobei bezüglich des Webzyklus der Gebergreifer (3) nach dem äußeren Umkehrpunkt (I) weniger beschleunigt wird als nach dem inneren Umkehrpunkt (II) und der Nehmergreifer (5) nach dem äußeren Umkehrpunkt (III) mehr beschleunigt wird als nach dem inneren Umkehrpunkt (IV).
  3. Das Verfahren nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass bezüglich des Webzyklus der innere Umkehrpunkt (IV) des Nehmergreifers (5) vor dem inneren Umkehrpunkt (II) des Gebergreifers (3) ist.
  4. Das Verfahren nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass der Greiferträger (2) für den Gebergreifer (3) und der Greiferträger (4) für den Nehmergreifer (5) bei ihren Bewegungen in das Webfach (29) und aus dem Webfach (29) durch den Antrieb (1) mit variabler Geschwindigkeit angetrieben werden, wobei bezüglich des Webzyklus der Gebergreifer (3) vor seinem inneren Umkehrpunkt (II) und der Nehmergreifer (5) nach seinem inneren Umkehrpunkt (IV) sich über eine Strecke in die gleiche Richtung bewegen.
  5. Das Verfahren nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass der äußere Umkehrpunkt (I) des Gebergreifers (3) mehrere Maschinengrad vor einem Anschlag (34) gelegen ist und dass der äußere Umkehrpunkt (III) des Nehmergreifers (5) mehrere Maschinengrad nach einem Anschlag (34) gelegen ist.
  6. Ein Antrieb für einen Greiferträger (2) für einen Gebergreifer (3) und für einen Greiferträger (4) für einen Nehmergreifer (5), welcher Antrieb einen gemeinsamen Antriebsmotor (6) für zwei Antriebsmechanismen (10, 11) und zwei Antriebsräder (14, 15) für einen Greiferträger (2, 4) enthält, die jeweils durch einen zugehörigen Antriebsmechanismus (10, 11) angetrieben werden, wobei jeder Antriebsmechanismus (10, 11) eine Kurbel (13, 28) enthält, die ein Gabelelement (16, 54) antreibt, wobei das Gabelelement (16, 54) und ein Querelement (17, 52) über eine Welle (20, 48) drehbar zueinander montiert sind, wobei das Querelement (17, 52) mit einem Zahnsegment (22, 47) verbunden ist, das ein Antriebsrad (14, 15) für einen Greiferträger (2, 4) antreibt, und das zusammen mit dem Querelement (17, 52) zu einem Rahmen (42) drehbar montiert ist, wobei das Querelement (17, 52) und der Rahmen (42) über eine Welle (21, 49) drehbar zueinander montiert sind, die quer zur Welle (20, 48) angeordnet ist, mittels derer das Gabelelement (16, 54) und das Querelement (17, 52) zueinander drehbar montiert sind, wobei jede Kurbel (13, 28) drehfest vom gemeinsamen Antriebsmotor (6) in einer gewissen Winkelposition zur Winkelposition des gemeinsamen Antriebsmotors (6) angetrieben wird, dadurch gekennzeichnet, dass für jeden Antriebsmechanismus (10, 11), dem ein Antriebsrad (14, 15) zugeordnet ist, die dem Querelement (17, 52) zugeordneten zwei Wellen (20, 21; 48, 49) in einem Winkel (37, 64) zueinander montiert sind, der um einige wenige Winkelgrad von 90° abweicht, und/oder dadurch, dass für jeden Antriebsmechanismus (10, 11), dem ein Antriebsrad (14, 15) zugeordnet ist, die Kurbel (13, 28) drehfest in einer gewissen Winkelposition zur Winkelposition des gemeinsamen Antriebsmotors (6) derart angetrieben wird, dass bezüglich des Webzyklus der äußere Umkehrpunkt (I) des Gebergreifers (3) vor dem äußeren Umkehrpunkt (III) des Nehmergreifers (5) ist.
  7. Der Antrieb nach Anspruch 6, dadurch gekennzeichnet, dass die dem Querelement (17, 52) zugeordneten zwei Wellen (20, 21; 48, 49) in einem Winkel (37, 64) zueinander angeordnet sind, der um einige wenige Winkelgrad von 90° derart abweicht, dass bezüglich des Webzyklus der Gebergreifer (3) nach dem äußeren Umkehrpunkt (I) weniger beschleunigt wird als nach dem inneren Umkehrpunkt (II) und dass der Nehmergreifer (5) nach dem äußeren Umkehrpunkt (III) mehr beschleunigt wird als nach dem inneren Umkehrpunkt (IV).
  8. Der Antrieb nach Anspruch 6 oder 7, dadurch gekennzeichnet, dass die dem Querelement (17, 52) zugeordneten zwei Wellen (20, 21; 48, 49) in einem Winkel (37, 64) zueinander angeordnet sind, der um einige wenige Winkelgrad von 90° abweicht, und/oder die Winkelpositionen der Kurbeln (13, 28) der Antriebsmechanismen (10, 11) zur Winkelposition des Antriebsmotors (6) derart eingestellt sind, dass bezüglich des Webzyklus der Greiferträger (2) des Gebergreifers (3) und der Greiferträger (4) des Nehmergreifers (5) bei ihren Bewegungen in ein Webfach (29) und aus dem Webfach (29) durch den Antrieb (1) mit variabler Geschwindigkeit angetrieben werden, wobei bezüglich des Webzyklus der Gebergreifer (3) vor seinem inneren Umkehrpunkt (II) und der Nehmergreifer (5) nach seinem inneren Umkehrpunkt (IV) sich über eine Strecke (35) in die gleiche Richtung bewegen.
  9. Der Antrieb nach einem der Ansprüche 6 bis 8, dadurch gekennzeichnet, dass die dem Querelement (17, 52) zugeordneten zwei Wellen (20, 21; 48, 49) in einem Winkel (37, 64) zueinander angeordnet sind, der um einige wenige Winkelgrad von 90° abweicht, und/oder die Winkelpositionen der Kurbeln (13, 28) der Antriebsmechanismen (10, 11) zur Winkelposition des Antriebsmotors (6) derart eingestellt sind, dass bezüglich des Webzyklus der innere Umkehrpunkt (IV) des Nehmergreifers (5) vor dem inneren Umkehrpunkt (II) des Gebergreifers (3) ist.
  10. Der Antrieb nach einem der Ansprüche 6 bis 9, dadurch gekennzeichnet, dass die dem Querelement (17, 52) zugeordneten zwei Wellen (20, 21; 48, 49) in einem Winkel zueinander angeordnet sind, der um einige wenige Winkelgrad von 90° abweicht, und/oder die Winkelpositionen der Kurbeln (13, 28) der Antriebsmechanismen (10, 11) zur Winkelposition des Antriebsmotors (6) derart eingestellt sind, dass der äußere Umkehrpunkt (I) des Gebergreifers (3) mehrere Maschinengrad vor einem Anschlag (34) gelegen ist und dass der äußere Umkehrpunkt (III) des Nehmergreifers (5) mehrere Maschinengrad nach einem Anschlag (34) gelegen ist.
  11. Der Antrieb nach einem der Ansprüche 6 bis 10, dadurch gekennzeichnet, dass die dem Querelement (17, 52) zugeordneten zwei Wellen (20, 21; 48, 49) in einem Winkel von ungefähr 4° versetzt zu einem Winkel von 90° angeordnet sind.
  12. Der Antrieb nach einem der Ansprüche 6 bis 11, dadurch gekennzeichnet, dass die Welle (23, 55), mittels derer das Gabelelement (16, 54) und die zugeordnete Kurbel (13, 28) zueinander drehbar verbunden sind, einen Winkel, der um einige wenige Winkelgrad von 45°, insbesondere einem Winkel von ungefähr 48° abweicht, mit der Welle (20, 48) bildet, mittels derer das Querelement (17, 52) und das Gabelelement (16, 54) zueinander drehbar verbunden sind.
  13. Der Antrieb nach einem der Ansprüche 6 bis 12, dadurch gekennzeichnet, dass die Kurbeln (13, 28) der zwei Antriebsmechanismen (10, 11) drehfest von einer gemeinsamen Antriebswelle (7) angetrieben werden, wobei bezüglich des Webzyklus die Kurbel (13) des Antriebsmechanismus (10) für den Gebergreifer (3) derart angebracht ist, dass sie um einige Maschinengrad vor der Kurbel (28) des Antriebsmechanismus (11) für den Nehmergreifer (5) ist.
  14. Der Antrieb nach einem der Ansprüche 6 bis 13, dadurch gekennzeichnet, dass der Antriebsmechanismus (10) für den Gebergreifer (3) und der Antriebsmechanismus (11) für den Nehmergreifer (5) identisch ausgebildet sind.
  15. Eine Webmaschine, dadurch gekennzeichnet, dass die Webmaschine einen Antrieb (1) nach einem der Ansprüche 6 bis 14 enthält.
EP11709704.8A 2010-04-02 2011-03-17 Antrieb und verfahren für den antrieb von greiferträgern Active EP2553153B1 (de)

Applications Claiming Priority (2)

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BE2010/0212A BE1019271A3 (nl) 2010-04-02 2010-04-02 Aandrijving en werkwijze voor het aandrijven van grijperdragers.
PCT/EP2011/054074 WO2011120820A2 (en) 2010-04-02 2011-03-17 Drive and method for driving gripper carriers

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EP2553153A2 EP2553153A2 (de) 2013-02-06
EP2553153B1 true EP2553153B1 (de) 2015-01-21

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EP4008817A1 (de) 2020-12-07 2022-06-08 Picanol Verfahren und vorrichtung zur bestimmung eines bewegungsparameters eines greifers
EP4008818A1 (de) 2020-12-07 2022-06-08 Picanol Verfahren und vorrichtung zum einstellen eines greiferbewegungshubes
WO2022122272A1 (en) 2020-12-07 2022-06-16 Picanol Method and device for adjusting a gripper movement stroke

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Publication number Priority date Publication date Assignee Title
NL7511122A (en) 1975-09-19 1977-03-22 Picanol Nv Feeding the weft in a rapier loom - by moving colour selector guide to impart acceleration to thread
GB2059455A (en) 1979-09-29 1981-04-23 Northrop Weaving Machinery Ltd Improvements in or relating to looms with stationary weft supply
DE3635545C1 (de) * 1986-10-18 1988-04-28 Dornier Gmbh Lindauer Getriebe fuer schuetzenlose Webmaschinen mit ins Webfach vorschiebbaren und wieder zurueckziehbaren Schusseintragorganen
EP0526390B1 (de) * 1991-07-24 1996-09-11 Sulzer RàœTi Ag Greiferwebmaschine mit auf Fadeneigenschaften einstellbarer Schusseintragsvorrichtung
JPH09137338A (ja) * 1995-11-13 1997-05-27 Toyota Autom Loom Works Ltd レピア織機における緯入れ方法
DE29808997U1 (de) * 1998-05-18 1998-07-30 Textilma Ag Greifer und eine Schusseintragvorrichtung für eine Greiferwebmaschine
DE10346227B4 (de) 2003-09-23 2012-09-13 Picanol N.V. Greiferbandantrieb für eine Greiferwebmaschine
BE1017477A3 (nl) * 2007-02-26 2008-10-07 Picanol Nv Een grijperweefmachine voorzien van een gevergrijper en een ombuiggeleiding.
US20090293983A1 (en) * 2008-05-28 2009-12-03 Itema (Switzerland) Ltd. Apparatus And Method For The Insertion Of A Weft Thread In A Rapier Weaving Machine
CN101525800B (zh) * 2009-04-20 2011-06-29 增城市柏迪创展有限公司 一种织机交接纬装置

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WO2011120820A2 (en) 2011-10-06
CN102947497A (zh) 2013-02-27
WO2011120820A3 (en) 2012-08-30
CN102947497B (zh) 2014-11-12
EP2553153A2 (de) 2013-02-06

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