EP1731640A2 - Dispositif de formation de lisière - Google Patents

Dispositif de formation de lisière Download PDF

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Publication number
EP1731640A2
EP1731640A2 EP06010384A EP06010384A EP1731640A2 EP 1731640 A2 EP1731640 A2 EP 1731640A2 EP 06010384 A EP06010384 A EP 06010384A EP 06010384 A EP06010384 A EP 06010384A EP 1731640 A2 EP1731640 A2 EP 1731640A2
Authority
EP
European Patent Office
Prior art keywords
gear
selvage
rotation
connecting section
pivotal connecting
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP06010384A
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German (de)
English (en)
Other versions
EP1731640B1 (fr
EP1731640A3 (fr
Inventor
Kazuto c/o TSUDAKOMA KOGYO K.K. Kakutani
Hisao Kasuga
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Tsudakoma Corp
Takano Co Ltd
Original Assignee
Takano Co Ltd
Tsudakoma Industrial Co Ltd
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Publication date
Application filed by Takano Co Ltd, Tsudakoma Industrial Co Ltd filed Critical Takano Co Ltd
Publication of EP1731640A2 publication Critical patent/EP1731640A2/fr
Publication of EP1731640A3 publication Critical patent/EP1731640A3/fr
Application granted granted Critical
Publication of EP1731640B1 publication Critical patent/EP1731640B1/fr
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Anticipated expiration legal-status Critical

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Classifications

    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03C—SHEDDING MECHANISMS; PATTERN CARDS OR CHAINS; PUNCHING OF CARDS; DESIGNING PATTERNS
    • D03C11/00—Selvedge shedding mechanisms not forming part of main shedding mechanism
    • 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
    • D03D47/40—Forming selvedges

Definitions

  • the present invention relates to a selvage device that forms a selvage on the basis of reciprocating motions of a first selvage heald frame and a second selvage heald frame in opposite directions from each other.
  • a selvage device includes a two-dimensional crank mechanism that is driven by an electric motor. By driving the two-dimensional crank mechanism, a pair of thread guide units is driven linearly in a reciprocating fashion.
  • the two-dimensional crank mechanism includes a lever attached to an output shaft of the electric motor, and a pair of links connected respectively to opposite ends of the lever.
  • the pair of links is respectively connected to the pair of thread guide units in a one-to-one fashion.
  • Fig. 6 in PCT Japanese Translation Patent Publication No. 10-503563 illustrates a structure in which an angular range of the links is adjustable
  • Fig. 7 therein illustrates a structure in which the radial length of cranks with respect to the links is adjustable.
  • a selvage device includes a first band supporting a first selvage heald frame and a second band supporting a second selvage heald frame.
  • the first and second bands are provided with power-receiving holes.
  • the power-receiving holes of the two bands are meshed with a gear that is rotated by an electric motor, thereby forming a so-called rack-pinion mechanism. Accordingly, in response to a rotation of the electric motor in forward and reverse directions, a selvage-shedding motion is implemented.
  • the settings for a standard height (i.e. frame height) and a warp-shedding amount of a warp shedding device may need to be changed depending on the type of cloth to be woven. In that case, the settings for a standard height and a shedding amount for the selvage-shedding motion may also need to be changed.
  • the settings for a standard height and a shedding amount for the selvage-shedding motion may also need to be changed.
  • PCT Japanese Translation Patent Publication No. 10-503563 applies the structure with the adjustable angular range of links or the structure with the adjustable radial length of cranks, the settings require high precision. Moreover, the work efficiency of the setting process is low.
  • Japanese Unexamined Patent Application Publication No. 2004-308064 has the rack-pinion mechanism, which means that in order to change the frame height and the shedding amount, the phase of the electric motor and the driving amount (i.e. the rotational amount of the electric motor) must be changed. Accordingly, the controlling of the electric motor is complicated, and an electric motor with a large output torque is necessary, thus leading to an increase in size of the entire device.
  • a selvage device includes two supporters whose movements are restricted to a selvage-shedding direction and having thread guides for guiding selvage threads; a driving motor that is independent of a main-shaft motor of the loom and is rotated in forward and reverse directions; and a motion-converting mechanism converting the rotation of the driving motor to reciprocating motions for the supporters.
  • the motion-converting mechanism includes a first gear attached to an output shaft of the driving motor; a second gear meshed with the first gear and having a first pivotal connecting section at a position distant from a center of rotation of the second gear in a radial direction thereof; a second pivotal connecting section provided in one of the first gear and a third gear directly meshed or indirectly linked with the first gear, the second pivotal connecting section being positioned distant from a center of rotation of the one of the first gear and the third gear in a radial direction thereof; and linking rods respectively provided for the supporters, the linking rods having first ends respectively connected to the first pivotal connecting section and the second pivotal connecting section and second ends connected to the corresponding supporters.
  • the first pivotal connecting section and the second pivotal connecting section driven in response to the rotation of the output shaft of the driving motor function as crank pins; the first supporter and the second supporter whose movements are restricted to the selvage-shedding direction function as pistons; and the linking rods for respectively linking the first pivotal connecting section and the second pivotal connecting section to the first supporter and the second supporter function as crank rods. Consequently, the crank pins, the pistons, and the crank rods constitute a so-called piston-crank mechanism.
  • the rotation of the output shaft of the driving motor is transmitted to the first pivotal connecting section and the second pivotal connecting section via the first gear and the driven gears included in the motion-converting mechanism.
  • the rotation is transmitted via the plurality of meshed gears included in the motion-converting mechanism
  • at least one of the first gear and the second gear included in the motion-converting mechanism may be replaced with an alternative gear having an appropriate number of gear teeth.
  • a selvage-shedding motion can be implemented properly without having to increase the driving torque of the motor.
  • an adjustment of the standard height for a selvage-shedding motion which is one of the selvage-shedding conditions, can be achieved by displacing the meshing position (phase) between the first gear of the driving side and the second gear of the driven side having a pivotal connecting section.
  • the shedding amount of selvage threads which is another one of the selvage-shedding conditions, can be set differently between the two driving systems. Accordingly, the operating conditions for the selvage device can be set properly to desired conditions.
  • standard height for a selvage-shedding motion refers to a relative distance between a position of the thread guides in a state where the selvage shed is closed and a position of a reference surface such as an upper surface of a loom frame.
  • the term "shedding amount of selvage threads” refers to a relative distance between two sets of the thread guides in a state where the selvage shed is opened.
  • the second pivotal connecting section may be provided in the first gear.
  • the first pivotal connecting section of the second gear and the second pivotal connecting section of the first gear are preferably disposed on the same side with respect to two corresponding imaginary lines extending respectively through the center of rotation of the second gear and the center of rotation of the first gear and extending parallel to each other in the selvage-shedding direction. Accordingly, the second gear is rotated in the reverse direction with respect to the rotational direction of the first gear.
  • the first pivotal connecting section and the second pivotal connecting section move in opposite directions from each other, allowing the two supporters to reciprocate in opposite directions from each other.
  • the driving load of the driving motor is reduced accordingly, thereby contributing to lower power consumption.
  • the second pivotal connecting section may be provided in the third gear.
  • the first pivotal connecting section of the second gear and the second pivotal connecting section of the third gear are preferably disposed on opposite sides from each other with respect to two corresponding imaginary lines extending respectively through the center of rotation of the second gear and the center of rotation of the third gear and extending parallel to each other in the selvage-shedding direction.
  • the second gear and the third gear may be disposed in a manner such that the center of rotation of the second gear and the center of rotation of the third gear are positioned within a range defined by two tangent lines tangent to an outer periphery of the first gear and extending parallel to each other in the selvage-shedding direction.
  • the second gear and the third gear may be disposed in a manner such that the center of rotation of the second gear and the center of rotation of the third gear are positioned within a range defined by two imaginary lines each extending through the center of rotation of the first gear and forming a crossing angle of ⁇ 45° with respect to an imaginary line extending through the center of rotation of the first gear in the selvage-shedding direction.
  • the second gear and the third gear may be arranged in a manner such that an imaginary line extending through the centers of rotation of the two respective gears extends crosswise with respect to the selvage-shedding direction.
  • the first pivotal connecting section and the second pivotal connecting section are preferably positioned within a range defined by two imaginary lines extending respectively through the centers of rotation of the two gears and extending parallel to each other in the selvage-shedding direction.
  • the first pivotal connecting section and the second pivotal connecting section can be relatively disposed closer to each other. Accordingly, by positioning the gears or the pivotal connecting sections so that the first pivotal connecting section and the second pivotal connecting section are relatively disposed close to each other indirectly or directly, the degree of change in the angle of the linking rods in response to the driving of the corresponding gears is reduced, thereby achieving an efficient conversion of the rotation of the driving motor (i.e. the rotation of the gears) to reciprocating motions for the supporters.
  • the second and third gears defining the driven gears may be disposed in a manner such that the imaginary line connecting the centers of rotation of the second and third gears extends crosswise to an imaginary line extending in the selvage-shedding direction, or that the centers of rotation of the two gears having the pivotal connecting sections are collinear to the imaginary line extending in the selvage-shedding direction.
  • the third gear may be meshed with a fourth gear attached to the output shaft of the driving motor.
  • the supporter linked to the first pivotal connecting section will be defined as the first supporter
  • the supporter linked to the second pivotal connecting section will be defined as the second supporter.
  • the position of the center of rotation of at least one of the first gear, the second gear, and the third gear may be relatively adjustable with respect to the center of rotation of the remaining one or more gears meshed with the at least one of the first gear, the second gear, and the third gear. Accordingly, this allows for a wider variety of gears (in other words, more types of gears having different number of gear teeth and different outer diameters) to be installable in the selvage device so that the selvage-shedding conditions can be set with higher precision, thereby further enhancing the selvage quality.
  • FIG. 1 to 4 illustrate one of a pair of selvage devices 1 that perform a shedding operation of selvage threads 3, 3.
  • the pair of selvage devices 1 is respectively disposed adjacent to opposite edges of a woven cloth 4.
  • the one of selvage devices 1 shown in the drawings is disposed on the right side of the loom, as viewed from the front of the loom.
  • the other selvage device 1 on the left side is disposed symmetrical to the selvage device 1 on the right side.
  • the selvage threads 3, 3 extend through selvage bobbins, tensers, and guides, which are disposed in the loom but are not shown in the drawings, and pass through thread guides 32, 32 included in the selvage device 1. After passing through a reed 5, the selvage threads 3, 3 reach a cloth fell so as to be interwoven into the woven cloth 4.
  • the selvage device 1 mainly includes a first supporter 20 and a second supporter 21 respectively having the thread guides 32, 32 through which the selvage threads 3, 3 extend; a pulse motor 33 serving as a driving motor; and a motion-converting mechanism that converts a rotary motion of the pulse motor 33 to a reciprocating motion. These components of the selvage device 1 are substantially mounted on a base plate 10 functioning as a mounting base of the selvage device 1.
  • the base plate 10 is formed of a plate material and extends in a selvage-shedding direction and in a width direction of the woven cloth 4.
  • a front face of the base plate 10 as viewed from a side of the cloth fell is provided with holder blocks 12, 13 functioning as attachment members attached to loom frames, and the pulse motor 33 functioning as the driving motor.
  • a rear face of the base plate 10 is provided with a holder bracket 30 functioning as a supporting member for supporting the first supporter 20 and the second supporter 21, and a plurality of gears 35, 36, 37 included in the motion-converting mechanism.
  • the first supporter 20 mainly includes a plurality of healds 22, ..., 22 respectively having the thread guides 32, ..., 32 for the selvage threads 3, ..., 3; a pair of upper and lower carrier rods 23, 24 respectively disposed at upper and lower positions of the healds 22 to support the healds 22; and a slide guide 28A extending in the selvage-shedding direction.
  • the second supporter 21 mainly includes a plurality of healds 22, ..., 22 respectively having the thread guides 32, ..., 32 for the selvage threads 3, ..., 3; a pair of upper and lower carrier rods 25, 26 respectively disposed at upper and lower positions of the healds 22 to support the healds 22; and a slide guide 28b extending in the selvage-shedding direction.
  • Opposite longitudinal ends of the slide guide 28A are respectively connected to the pair of upper and lower carrier rods 23, 24, and similarly, opposite longitudinal ends of the slide guide 28b are respectively connected to the pair of upper and lower carrier rods 25, 26.
  • the pair of carrier rods 23, 24 and the pair of carrier rods 25, 26 have attachment segments that are screwed to the corresponding slide guides 28A and 28B. Moreover, each of the carrier rods 23, 24, 25, 26 has an elongate segment extending in the width direction of the woven cloth 4. Upper and lower ends of each heald 22 are provided with holes. The upper and lower holes of one set of the healds 22 are respectively engaged to the elongate segments of the upper and lower carrier rods 23, 24, thereby forming a first heald frame that supports the set of healds 22.
  • the upper and lower holes of the other set of the healds 22 are respectively engaged to the elongate segments of the carrier rods 25, 26, thereby forming a second heald frame that supports the other set of healds 22.
  • the upper carrier rod 23 and the upper carrier rod 25 are provided with connecting sections having pivotal connection holes for connecting a linking rod 51A and a linking rod 51B to the upper carrier rod 23 and the upper carrier rod 25, respectively.
  • slide rods 29A, 29B, 29C extending in the selvage-shedding direction are disposed adjacent to side surfaces of the slide guides 28A and 28B.
  • slide rods 29A, 29B, 29C are formed of, for example, round bars extending longitudinally in the selvage-shedding direction, and are separated from each other by a predetermined distance in the width direction of the woven cloth 4.
  • Each of the slide guides 28A and 28B has sliding portions that are semi-circularly depressed in cross section and extend in the longitudinal direction of the slide rods 29A, 29B, 29C, such that the sliding portions correspond to the adjacent slide rods.
  • the sliding portions of the slide guide 28A are slidably disposed between the adjacent slide rods 29A and 29B so that a moving direction of the first supporter 20 is restricted to the longitudinal direction of the slide guide 28A, that is, the selvage-shedding direction.
  • the sliding portions of the slide guide 28b are slidably disposed between the adjacent slide rods 29B and 29C so that a moving direction of the second supporter 21 is restricted to the longitudinal direction of the slide guide 28B, that is, the selvage-shedding direction.
  • Upper and lower ends of each of the slide rods 29A, 29B, 29C are respectively housed in the holder bracket 30 attached to the base plate 10 and a holder bracket 31. Similar to a damper stay 9, which will be described below, a stay (not shown) for supporting the holder bracket 31 is bridged between the loom frames, so that the holder bracket 31 is stabilized with respect to the loom frames.
  • the pulse motor 33 is attached to the base plate 10 with bolts 15 engaged to threaded holes 17 provided in the base plate 10.
  • An output shaft 34 of the pulse motor 33 extends from the front face towards the rear face of the base plate 10 so as to protrude outward from the rear face.
  • the protruding portion of the output shaft 34 has an outer periphery provided with a predetermined number of gear teeth, and is engaged with the gear 35 corresponding to a first gear according to the present invention.
  • the gear 35 has a hexagon socket head bolt 19 disposed in a base shaft portion thereof.
  • the gear 35 is secured to the output shaft 34 in a relatively immovable fashion with the hexagon socket head bolt 19.
  • two supporting shafts 40A, 40B are disposed distant from the output shaft 34 by predetermined center distances.
  • each of the supporting shafts 40A, 40B is provided with a predetermined number of gear teeth.
  • the gear 36 corresponding to a second gear according to the present invention is attached to the outer periphery of the supporting shaft 40A and is meshed with the gear 35, and similarly, the gear 37 corresponding to a third gear according to the present invention is attached to the outer periphery of the supporting shaft 40B and is meshed with the gear 35.
  • Each of the supporting shafts 40A, 40B includes a base portion 40, a reduced-diameter portion 42 defining a first axial half of the supporting shaft 40A or 40B and having a smaller diameter than the base 40, and a threaded portion 41 defining a second axial half of the supporting shaft 40A or 40B and having a smaller diameter than the base 40.
  • the rear face of the base plate 10 is provided with threaded holes 18A, 18B that are distant from the output shaft 34 by predetermined center distances.
  • the supporting shafts 40A, 40B are integrated with the base plate 10 by screwing the threaded portions 41, 41 into the corresponding threaded holes 18A, 18B.
  • Each of the gears 36, 37 is provided with a through hole that extends through the center of rotation thereof.
  • Each through hole has a step so that the through hole is given a section with a larger inner diameter than the remaining section.
  • a bearing 46 is fitted in the large-diameter section such that the bearing 46 abuts on the large-diameter section and the step.
  • a stopper ring 47 is fitted to an annular groove provided along the inner periphery of the gear 36 or 37. The stopper ring 47 prevents the bearing 46 from falling off the gear 36 or 37.
  • an inner ring portion of the bearing 46 is fitted to the reduced-diameter portion 42 of the corresponding supporting shaft 40A or 40B so that the gear 36 or 37 is rotatable around the supporting shaft 40A or 40B.
  • the supporting shafts 40A, 40B are respectively provided with annular stopper grooves 43. Stopper rings 44 are fitted to these annular stopper grooves 43 so as to prevent the gear 36 and the gear 37 from falling off the respective supporting shafts 40A, 40B.
  • One axial end of the gear 36 has an arm 48A attached thereto.
  • one axial end of the gear 37 has an arm 48B attached thereto.
  • Each of the arms 48A, 48B has a circular hole that provides a working space for attachment and detachment of the corresponding stopper ring 44, and an arm segment extending outward from the center of the arm 48A or 48B in the radial direction.
  • the arm segments of the arms 48A, 48B are provided with pivotal connection holes for connecting with the respective linking rods 51A, 51B.
  • the arms 48A, 48B are respectively mounted to the gears 36, 37 with a plurality of bolts 49, 49 in a manner such that the centers of the arms 48A, 48B are respectively aligned with the centers of rotation of the gears 36, 37 and that first and second pivotal connecting sections 53A, 53B respectively provided in the arms 48A, 48B are positioned on opposite sides from each other with respect to two corresponding imaginary lines L1, L0 extending through an outer periphery of the gear 35 and extending parallel to each other in the selvage-shedding direction.
  • the gear 36 is integrally provided with the first pivotal connecting section 53A at a position distant from the center of the gear 36 in the radial direction thereof.
  • the gear 37 is integrally provided with the second pivotal connecting section 53B at a position distant from the center of the gear 37 in the radial direction thereof.
  • the arm 48A and the upper carrier rod 23 are linked with each other with the linking rod 51A having pivotal connection holes at its opposite ends.
  • a linking pin 52A functioning as a pivot shaft extends through the pivotal connection hole at a first end of the linking rod 51A and through the pivotal connection hole of the arm 48A so as to form the pivotal connecting section 53A of the arm 48A.
  • the arm 48B and the upper carrier rod 25 are linked with each other with the linking rod 51B having pivotal connection holes at its opposite ends.
  • a linking pin 52B functioning as a pivot shaft extends through the pivotal connection hole at a first end of the linking rod 51B and through the pivotal connection hole provided in the arm 48B so as to form the pivotal connecting section 53B of the arm 48B.
  • linking rods 51A, 51B are respectively linked to the pivotal connection holes of the upper carrier rods 23, 25.
  • a linking pin 39A functioning as a pivot shaft extends through the pivotal connection hole at the second end of the linking rod 51A and through the pivotal connection hole of the upper carrier rod 23 so as to form a pivotal connecting section 27A of the first supporter 20.
  • a linking pin 39B functioning as a pivot shaft extends through the pivotal connection hole at the second end of the linking rod 51B and through the pivotal connection hole of the upper carrier rod 25 so as to form a pivotal connecting section 27B of the second supporter 21.
  • the two supporters that have the thread guides 32, 32 guiding the selvage threads 3, 3 and whose movements are restricted to the selvage-shedding direction are defined by the first supporter 20 including the healds 22, the carrier rods 23, 24, and the slide guide 28A, and by the second supporter 21 including the healds 22, the carrier rods 25, 26, and the slide guide 28b.
  • the driving motor that is provided independent of a main-shaft motor of the loom and is driven in forward and reverse directions is defined by the pulse motor 33.
  • the motion-converting mechanism that converts a rotary motion of the driving motor to reciprocating motions for the supporters 20, 21 includes the gear 35 serving as the first gear; the gear 36 serving as the second gear and having the first pivotal connecting section 53A at a position distant from the center of rotation of the gear 36 in the radial direction thereof; the second pivotal connecting section 53B provided in the third gear that is directly meshed with the first gear and disposed at a position distant from the center of rotation of the third gear in the radial direction thereof; and the linking rods 51A, 51B provided respectively for the two supporters 20, 21 such that the first ends of the linking rods 51A, 51B are respectively connected to the first pivotal connecting section 53A and the second pivotal connecting section 53B and the second ends are connected to the corresponding supporters 20, 21.
  • the pulse motor 33 rotates its output shaft 34 alternately in the forward and reverse directions by a predetermined amount every time the main shaft (crank shaft) of the loom makes a predetermined number of rotations.
  • the motion-converting mechanism transmits the forward and reverse rotation of the output shaft 34 to the second gear 36 and the third gear 37 through the first gear 35, which is attached to the output shaft 34 and is meshed with the gears 36, 37.
  • the first pivotal connecting section 53A and the second pivotal connecting section 53B of the respective gears 36, 37 are rocked.
  • the rocking motions of the pivotal connecting sections 53A, 53B are then transmitted respectively to the first supporter 20 and the second supporter 21 as reciprocating motions via the linking rod 51A and the linking rod 51B.
  • the pulse motor 33 may be, for example, a stepping motor having a step angle of several degrees or a typical rotation-controllable motor.
  • the pulse motor 33 is connected to, for example, a control circuit, not shown, which counts the number of timing signals generated when the main shaft of the loom passes a predetermined angle and which alternately generates rotation command pulses for driving the pulse motor 33 in the forward and reverse directions on the basis of the counted number.
  • the pulse motor 33 is driven in response to a command from the control circuit.
  • a moving range of the first pivotal connecting section 53A and a moving range of the second pivotal connecting section 53B in response to the forward and reverse rotation of the output shaft 34 are respectively indicated by reference characters P1 to P3 and reference characters Q1 to Q3.
  • an angle ⁇ 1 of the moving range of the first pivotal connecting section 53A in response to the driving of the pulse motor 33 is substantially 90°.
  • reference characters S1, S2, and S3 each indicate a position of the corresponding thread guides 32 when the first pivotal connecting section 53A is moved to one of the positions P1, P2, P3, respectively.
  • the position S1 of the thread guides 32 corresponds to an intermediate position in a selvage-shedding process and defines a standard height for the selvage-shedding motion.
  • the distance between the position S2 and the position S3 of the thread guides 32 corresponds to a shedding amount of selvage threads.
  • the selvage-shedding mode is reversed for every predetermined number of rotations of the loom.
  • weft threads are each inserted into a weft-traveling path formed in response to a warp-shedding motion, and a beating operation is subsequently performed. Accordingly, this forms the woven cloth 4 having selvage edges formed of the selvage threads 3, 3 and the inserted weft threads.
  • the selvage device 1 may be disposed at a position so as not to interfere with the weft insertion process.
  • the selvage device 1 is positioned in front of a first warp heald frame 7 of the frontmost row as viewed from the front of the loom in order to reduce the shedding amount of selvage threads to the minimum.
  • the selvage device 1 may be positioned to the back of a warp heald frame of the rearmost row.
  • the selvage device 1 is positionally adjustable in the width direction of the woven cloth 4 depending on the cloth specification.
  • the base plate 10 included in the selvage device 1 is attached to the damper stay 9 with the holder blocks 12, 13.
  • the damper stay 9 is bridged between the pair of left and right loom frames, not shown.
  • the holder blocks 12, 13 sandwich the damper stay 9 in the vertical direction.
  • the holder blocks 12, 13 are fixed to the front face of the base plate 10 with the bolts 15.
  • the holder block 12 is provided with a threaded hole extending towards the damper stay 9.
  • a bolt 14 is screwed into this threaded hole so that the holder block 12 can be secured to the damper stay 9.
  • an operator may loosen the bolt 14 and shift the base plate 10, i.e. the selvage device 1, along the damper stay 9 to a position corresponding to the width of the woven cloth 4. Accordingly, the selvage device 1 is positionally adjustable in the width direction of the woven cloth 4.
  • the driven gears having the first pivotal connecting section 53A and the second pivotal connecting section 53B function as crank pins; the first supporter 20 and the second supporter 21 whose movements are restricted to the selvage-shedding direction function as pistons; and the linking rod 51A and the linking rod 51B respectively linking the first pivotal connecting section 53A and the second pivotal connecting section 53B to the first supporter 20 and the second supporter 21 function as crank rods. Consequently, the crank pins, the pistons, and the crank rods constitute a so-called piston-crank mechanism.
  • the rotation of the driving motor is transmitted to the gears 36, 37 defining the driven gears via the first gear 35, and is converted to reciprocating motions for the first supporter 20 and the second supporter 21.
  • the first selvage heald frame and the second selvage heald frame are reciprocated in opposite directions from each other, thereby implementing the selvage-shedding motion.
  • the meshing position (phase) between the first gear 35 of the driving side and the second gear 36 of the driven side having the pivotal connecting section 53A may be displaced so as to change the standard height for the selvage-shedding motion.
  • the hexagon socket head bolt 19 securing the gear 35 in position and then shifting the gear 35 towards the axial end of the output shaft 34, the two gears can be disengaged from each other.
  • the meshing phase can be displaced.
  • At least one of the first gear of the driving side and the second gear of the driven side may be replaced with another gear so as to change the gear ratio between the two gears
  • at least one of the first gear and the third gear may be replaced with another gear so as to change the gear ratio between the two gears.
  • the gear 35 may be detached from the output shaft 34 by means of the above-mentioned method.
  • the corresponding stopper rings 44 may be removed so that the gears 36, 37 can be detached from the supporting shafts 40A, 40B while the corresponding bearings 46 remain attached to the gears 36, 37.
  • the gears may be replaced with alternative gears having an appropriate number of gear teeth using the above-mentioned method so as to increase the gear ratio between the gear 35 and the gear 36 and between the gear 35 and the gear 37 in correspondence to an increase in the selvage tension. Accordingly, the operating condition of the selvage device 1 can be set properly to a desired condition.
  • a first gear for transmitting the rotation of the output shaft 34 to the gear 36 and the gear 37 respectively functioning as the second gear and the third gear includes a single gear 35.
  • a plurality of driving gears that transmits the rotation individually to the driven gears may be provided.
  • the gear 37 functioning as the third gear is axially supported by the gear 36 functioning as the second gear in a rotatable fashion such that the two gears share the same center of rotation.
  • a gear 55 functioning as a fourth gear is coaxially disposed on the output shaft 34, which protrudes outward from the gear 35 in the axial direction thereof, and is meshed with the gear 37.
  • the first pivotal connecting section 53A and the second pivotal connecting section 53B are positioned on opposite sides from each other with respect to the two corresponding imaginary lines L1, L0 respectively extending through the centers of rotation 36a, 37a of the gears 36, 37 and extending parallel to each other in the selvage-shedding direction.
  • the gear 36 and the gear 37 are disposed in a manner such that the centers of rotation 36a, 37a of the gears 36, 37 are positioned within a range defined by two tangent lines L5, L6 tangent to the outer periphery of the gear 35 and extending parallel to each other in the selvage-shedding direction. (More specifically, the centers of rotation 36a, 37a of the gears 36, 37 are collinear to an imaginary line extending through the center of rotation 35a of the gear 35 in the selvage-shedding direction.)
  • each pair of gears may include a combination of gears having different outer diameters with a different number of gear teeth. In that case, the shedding amount of selvage threads of the first supporter 20 can be set at a value different from that of the second supporter 21.
  • the center distance between the output shaft 34 of the pulse motor 33 and the center of rotation of at least one of the gears 36, 37 serving as the second and third gears is preferably adjustable.
  • Fig. 14 illustrates a typical example of such an adjustable feature provided in the first embodiment.
  • the base plate 10 is given a structure such that the attachment position of the pulse motor 33 and the positions of the supporting shafts 40A and 40B are adjustable in a direction for changing the center distance therebetween.
  • the base plate 10 is provided with a cutout 62 in a range in which the base plate 10 does not interfere with the positional adjustment of the output shaft 34 of the pulse motor 33, and slots 60 extending in the positional adjustment direction in place of threaded holes 17 shown in Fig.
  • the pulse motor 33 is mounted to the base plate 10 by inserting bolts 63 through the slots 60 and then fastening the bolts 63 to nuts, not shown.
  • the base plate 10 is provided with positional-adjustment slots 61A, 61B in place of the threaded holes 18A, 18B provided respectively for the attachment of the supporting shaft 40A and the supporting shaft 40B to the base plate 10.
  • the slots 61A, 61B extend longitudinally along lines extending through the centers of the respective gears 36, 37.
  • each of the supporting shafts 40A, 40B is provided with the threaded portion 41 that extends through and protrudes from the base plate 10.
  • the supporting shafts 40A, 40B are respectively inserted through the slots 61A, 61B.
  • the threaded portions 41 of the supporting shafts 40A, 40B are then fastened to corresponding nuts 64 so that the base plate 10 is tightly pressed from opposite directions. Accordingly, the supporting shafts 40A, 40B are secured to the base plate 10.
  • the base plate 10 may be given a structure such that the positional adjustment feature is given only to the pulse motor 33 or to the supporting shafts 40A, 40B.
  • the gear 35 in order to rotate the gear 37 having the second pivotal connecting section 53b, the gear 35 transmits the rotation of the output shaft 34 to the gear 37.
  • the gear 37 to which the rotation is transmitted does not necessarily have to be provided.
  • the gear 35 functioning as the first gear and the gear 36 functioning as the second gear may have substantially the same diameter (with substantially the same number or similar number of gear teeth).
  • the gear 35 may be provided with the second pivotal connecting section 53B at a position distant from the center of rotation of the gear 35, and the linking rod 51B may be connected to the pivotal connecting section 53B.
  • the driving torque of the pulse motor 33 can be reduced, thereby contributing to lower power consumption.
  • the first pivotal connecting section 53A and the second pivotal connecting section 53B are positioned on the same side with respect to the two imaginary lines L1, L0 respectively extending through the centers of rotation 36a, 35a of the gears 36, 35 and extending parallel to each other in the selvage-shedding direction (in other words, the two pivotal connecting sections 53A, 53B are both positioned on the right side in Fig. 6 with respect to the imaginary lines L1, L0 as a boundary line).
  • the gear 36 is positioned within a range defined by two tangent lines L5, L6 tangent to the outer periphery of the gear 35 and extending parallel to each other in the selvage-shedding direction. (More specifically, the center of rotation 36a of the gear 36 is collinear to the imaginary line L0 extending through the center of rotation 35a of the gear 35 in the selvage-shedding direction.)
  • the centers of rotation 36a, 37a of the gears 36, 37 and the center of rotation of the pulse motor 33 are arranged in a manner such that the centers of rotation are positioned at apexes of a triangle.
  • the pulse motor 33, the gear 36, and the gear 37 may be disposed in a collinear fashion such that the center of rotation of the pulse motor 33, the center of rotation 36a of the gear 36, and the center of rotation 37a of the gear 37 are arranged in a single line.
  • Fig. 7 shows an example in which the gear 36, the gear 37, and the gear 35 are arranged in a meshing fashion along an imaginary line extending vertically in the selvage-shedding direction with respect to the gear 35.
  • the first and second pivotal connecting sections 53A, 53B are positioned on opposite sides from each other with respect to the two corresponding imaginary lines L1, L0 extending respectively through the centers of rotation 36a, 37a of the gears 36, 37 and extending parallel to each other in the selvage-shedding direction.
  • the gear 36 and the gear 37 are disposed in a manner such that the centers of rotation 36a, 37a of the gears 36, 37 are positioned within a range defined by two tangent lines L5, L6 tangent to the outer periphery of the gear 35 and extending parallel to each other in the selvage-shedding direction.
  • first pivotal connecting section 53A and the second pivotal connecting section 53B are disposed relatively closer to each other.
  • Fig. 8 illustrates an example in which the gear 36 and the gear 37 are meshed with the outer periphery of the gear 35 and are disposed at an angle with respect to the center of rotation 35a of the gear 35.
  • the gear 36 and the gear 37 are respectively positioned at an angle ⁇ 1 and an angle ⁇ 2 in the counterclockwise direction with respect to the center of rotation 35a of the gear 35.
  • the gear 36 and the gear 37 are disposed in a manner such that the centers of rotation 36a, 37a of the gears 36, 37 are positioned within a range defined by two imaginary lines L8, L9 each extending through the center of rotation 35a of the gear 35 and forming a crossing angle ⁇ 3 with respect to an imaginary line L7 that extends through the center of rotation 35a of the gear 35 in the selvage-shedding direction.
  • the imaginary line L7 and an imaginary line L21 extending through the center of rotation 35a and the center of rotation 36a of the gear 36 form a crossing angle ⁇ 1 therebetween
  • the imaginary line L7 and an imaginary line L22 extending through the center of rotation 35a and the center of rotation 37a of the gear 37 form a crossing angle ⁇ 2 therebetween.
  • the gears 36, 37 are disposed at positions where the crossing angles ⁇ 1 and ⁇ 2 are smaller than the angle ⁇ 3.
  • the angle ⁇ 3 is preferably set at 45°.
  • first pivotal connecting section 53A and the second pivotal connecting section 53B are positioned on opposite sides from each other with respect to the two corresponding imaginary lines L1, L0 extending respectively through the centers of rotation 36a, 37a of the gears 36, 37 and extending parallel to each other in the selvage-shedding direction.
  • the center of rotation 37a of the gear 37 and the pivotal connecting section 53B are disposed on opposite sides of the imaginary line L7. Accordingly, this reduces the degree of change in the angle of the linking rod 51B when the gear 37 is driven, thereby achieving an efficient conversion to a reciprocating motion.
  • Fig. 9 illustrates another example in which the gear 36 and the gear 37 are disposed in a manner such that an imaginary line L10 extending through the centers of rotation 36a, 37a of the gears 36, 37 extends crosswise with respect to the selvage-shedding direction.
  • the first pivotal connecting section 53A and the second pivotal connecting section 53B are positioned within a range defined by two imaginary lines L11, L12 extending respectively through the centers of rotation 36a, 37a of the gears 36, 37 and extending parallel to each other in the selvage-shedding direction.
  • first pivotal connecting section 53A and the second pivotal connecting section 53B are positioned on opposite sides from each other and at inner sides of the imaginary lines L11, L12, which extend respectively through the centers of rotation 36a, 37a and parallel to each other in the selvage-shedding direction. Accordingly, this reduces the degree of change in the angle of the linking rods 51A, 51B when the gears 36, 37 are rotated, thereby achieving an efficient conversion to reciprocating motions.
  • Fig. 10 illustrates another example in which the gear 36 and the gear 37 are arranged in a rotary-axis direction thereof with a predetermined distance therebetween so as to share a common center of rotation.
  • the tooth surface of the gear 35 functioning as the first gear extends in an axial direction thereof so that the gear 35 is meshed with both the gear 36 and the gear 37.
  • the first pivotal connecting section 53A and the second pivotal connecting section 53B are positioned on opposite sides from each other with respect to the two corresponding imaginary lines L1, L0 extending respectively through the centers of rotation 36a, 37a of the respective gears 36, 37 and extending parallel to each other in the selvage-shedding direction.
  • the gear 36 and the gear 37 are disposed in a manner such that the centers of rotation 36a, 37a of the gears 36, 37 are positioned within a range defined by two tangent lines L5, L6 tangent to the outer periphery of the gear 35 and extending parallel to each other in the selvage-shedding direction.
  • Fig. 11 shows an example in which the output shaft 34 of the pulse motor 33 is oriented in the selvage-shedding direction, and the output shaft 34 is provided with a bevel gear 35, which is three-dimensional.
  • the bevel gear 35 is disposed such that its tooth surface faces downward.
  • the gear 36 and the gear 37 are defined by the same bevel gears as the gear 35, and have their rotary axes aligned with each other so that the gear 36 and the gear 37 share a common center of rotation.
  • the gear 37 functioning as the third gear is driven by the gear 35 functioning as the first gear, which is used in common between the gear 37 and the gear 36 functioning as the second gear.
  • a gear 56 serving as a fourth gear may be provided.
  • the gear 56 is meshed with the gear 37 and is attached to a rotary shaft 59, which is rotated together with the gear 36. Consequently, when the gear 56 is rotated in response to the rotation of the output shaft 34, the gear 37 is driven.
  • another indirect transmission gear 57 may be provided in addition to such an indirect transmission gear 56. In this case, the rotation of the output shaft 34 is transmitted to the gear 37 integrated with the gear 57.
  • the linking pins 52A, 52B, the connection holes, and the like are used for the pivotal connecting sections 53A and 53B and the pivotal connecting sections 27A and 27B that link together the linking rods 51A, 51B, the arms 48A, 48B, and the upper carrier rods 23, 25, respectively.
  • other known pivotal connecting structures are also permissible.
  • one set of components that are to be linked to the other set of components may be provided with pivot shafts so that the one set can be linked to the other set.
  • the present invention is not limited to fluid-jet looms, such as air-jet looms, and is widely applicable to other shuttleless looms, such as rapier looms and projectile looms.

Landscapes

  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Looms (AREA)
  • Sewing Machines And Sewing (AREA)
EP06010384A 2005-06-06 2006-05-19 Dispositif de formation de lisière Not-in-force EP1731640B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2005164908A JP4718248B2 (ja) 2005-06-06 2005-06-06 耳織成装置

Publications (3)

Publication Number Publication Date
EP1731640A2 true EP1731640A2 (fr) 2006-12-13
EP1731640A3 EP1731640A3 (fr) 2010-02-03
EP1731640B1 EP1731640B1 (fr) 2011-08-10

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EP (1) EP1731640B1 (fr)
JP (1) JP4718248B2 (fr)
KR (1) KR20060127739A (fr)
CN (1) CN1876915B (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE1017768A3 (fr) * 2007-09-26 2009-06-02 Toyota Jidoshokki Kk Dispositif de formation de la foule en utilisant des fils de lisiere dans un metier a tisser.
WO2018130933A1 (fr) * 2017-01-13 2018-07-19 Nv Michel Van De Wiele Dispositif de lisière

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014015699A (ja) * 2012-06-12 2014-01-30 Tsudakoma Corp 織機の耳形成装置
JP5884792B2 (ja) * 2013-08-27 2016-03-15 株式会社豊田自動織機 織機における捨耳用開口装置
CN103924354B (zh) * 2014-03-27 2015-05-27 经纬纺织机械股份有限公司 一种联动式边组织开口机构
CN109137227A (zh) * 2018-11-15 2019-01-04 青岛东佳机械制造有限公司 一种喷气织机的机械折入边装置
JP7518035B2 (ja) 2021-05-10 2024-07-17 津田駒工業株式会社 織機の耳糸開口装置
KR102585133B1 (ko) * 2021-08-05 2023-10-04 도준석 레노종광 직기의 개구운동 왕복안내장치

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10503563A (ja) * 1995-05-29 1998-03-31 ピカノール エヌ．ヴィ． 織機の耳織成装置
JP2004308064A (ja) * 2003-04-08 2004-11-04 Toyota Industries Corp 織機における耳形成装置

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5848383Y2 (ja) * 1978-04-10 1983-11-04 ワイケイケイ株式会社 織機の開口装置
JPH09268450A (ja) * 1996-01-29 1997-10-14 Toyota Autom Loom Works Ltd 織機における捨耳形成方法及び装置
BE1010014A3 (nl) * 1996-02-09 1997-11-04 Picanol Nv Kanteninrichting voor een weefmachine.
IT1293618B1 (it) * 1997-07-17 1999-03-08 Vamatex Nuova Spa Dispositivo di comando per la legatura a giro inglese in telai di tessitura
JP2004300637A (ja) * 2003-03-31 2004-10-28 Toyota Industries Corp 織機における開口装置

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10503563A (ja) * 1995-05-29 1998-03-31 ピカノール エヌ．ヴィ． 織機の耳織成装置
JP2004308064A (ja) * 2003-04-08 2004-11-04 Toyota Industries Corp 織機における耳形成装置

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE1017768A3 (fr) * 2007-09-26 2009-06-02 Toyota Jidoshokki Kk Dispositif de formation de la foule en utilisant des fils de lisiere dans un metier a tisser.
WO2018130933A1 (fr) * 2017-01-13 2018-07-19 Nv Michel Van De Wiele Dispositif de lisière
BE1024912B1 (nl) * 2017-01-13 2018-08-16 VAN DE WIELE Michel NV Zelfkantinrichting
US10988867B2 (en) 2017-01-13 2021-04-27 Nv Michel Van De Wiele Selvedge device

Also Published As

Publication number Publication date
EP1731640B1 (fr) 2011-08-10
KR20060127739A (ko) 2006-12-13
CN1876915B (zh) 2010-09-08
EP1731640A3 (fr) 2010-02-03
CN1876915A (zh) 2006-12-13
JP4718248B2 (ja) 2011-07-06
JP2006336171A (ja) 2006-12-14

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