US20060016504A1 - Warp let-off device for loom - Google Patents

Warp let-off device for loom Download PDF

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Publication number
US20060016504A1
US20060016504A1 US11/175,309 US17530905A US2006016504A1 US 20060016504 A1 US20060016504 A1 US 20060016504A1 US 17530905 A US17530905 A US 17530905A US 2006016504 A1 US2006016504 A1 US 2006016504A1
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United States
Prior art keywords
brake
warp
warp beam
braking force
gear
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.)
Abandoned
Application number
US11/175,309
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English (en)
Inventor
Yasuhiro Kura
Keiichi Myogi
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
Original Assignee
Tsudakoma Industrial Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Tsudakoma Industrial Co Ltd filed Critical Tsudakoma Industrial Co Ltd
Assigned to TSUDAKOMA KOGYO KABUSHIKI KAISHA reassignment TSUDAKOMA KOGYO KABUSHIKI KAISHA ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: Kura, Yasuhiro, MYOGI, KEIICHI
Publication of US20060016504A1 publication Critical patent/US20060016504A1/en
Abandoned legal-status Critical Current

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    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D49/00—Details or constructional features not specially adapted for looms of a particular type
    • D03D49/04—Control of the tension in warp or cloth
    • D03D49/06—Warp let-off mechanisms
    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D49/00—Details or constructional features not specially adapted for looms of a particular type
    • D03D49/04—Control of the tension in warp or cloth
    • D03D49/06—Warp let-off mechanisms
    • D03D49/10—Driving the warp beam to let the warp off
    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D49/00—Details or constructional features not specially adapted for looms of a particular type
    • D03D49/04—Control of the tension in warp or cloth
    • D03D49/06—Warp let-off mechanisms
    • D03D49/08—Warp beam brakes

Definitions

  • the present invention relates to a warp let-off device for a loom, and more specifically relates to a brake unit for a warp beam for feeding warp.
  • a predetermined tension is applied to a warp sheet, and a warp beam for feeding warp is rotated in an unwinding direction as the tension increases, so that the warp is fed.
  • Japanese Unexamined Patent Application Publication No. 2003-193355 discloses a warp let-off device which provides a braking force against the warp tension by a non-return function of a worm gear mechanism while rotating a worm included in the worm gear mechanism with a dedicated motor to drive a worm wheel. Accordingly, a warp beam rotates together with the worm wheel, and warp is fed at a predetermined tension.
  • the warp tension greatly varies because of shedding motion and beating motion, and vibration occurs in every pick (every cycle).
  • the tension variation is transmitted to the warp beam around which the warp is wound, and serves as a vibrating force which causes a so-called rotational vibration of the warp beam.
  • rotational vibration slight rotation of the warp beam in the unwinding direction and that in the winding direction (reverse rotation) are repeated because of torsional deformation of a shaft or backlash of a gear.
  • the warp length between a cloth fell and the warp beam varies due to the rotational vibration, and accordingly weaving bars (uneven density) occur.
  • weaving bars uneven density
  • the radius of the warp beam increases, the radius of the vibrating force applied to the warp beam increases, and therefore the rotational vibration of the warp beam easily occurs.
  • the weight of the warp beam increases, the energy of the rotational vibration increases, and therefore large weaving bars easily occur.
  • large tension vibration occurs due to looseness in the beating motion.
  • an object of the present invention is to reduce variation in warp tension in a warp let-off device for a loom, and to thereby prevent weaving bars.
  • Another object of the present invention is to reduce the required capacity of a drive source and a transmission for driving a rotating shaft of a warp beam, and to increase range of use conditions, such as allowable warp tension and pick density, so that versatility of the loom is increased.
  • a warp let-off device for a loom includes a drive unit which transmits rotation of a drive source to a warp beam with a transmission and rotates the warp beam in an unwinding direction while applying a braking force against a warp tension to the warp beam, and a brake unit which applies a braking force to the warp beam in addition to the braking force applied by the drive unit.
  • the brake unit may be provided with a braking-force reducing means for reducing the braking force applied by the brake unit when the warp beam rotates in the winding direction.
  • the braking-force reducing means may also include an actuator which reduces a contact pressure between a circular brake plate and brake discs, the circular brake plate being integrated with a brake shaft.
  • the contact pressure can be easily changed, and adequate contact pressure adjustment can be performed.
  • FIG. 1 is a side view of a warp let-off device for a loom
  • FIG. 3 is a sectional view of the main part of a warp let-off device for a loom according to a second embodiment
  • FIG. 4 is a schematic diagram showing the main part of a warp let-off device for a loom according to a third embodiment
  • FIG. 6 is a schematic diagram showing the main part of a warp let-off device for a loom according to a fifth embodiment
  • FIG. 7 is a diagram showing the main part of the warp let-off device shown in FIG. 6 viewed from the arrow A;
  • FIG. 8 is a schematic diagram showing the main part (circular brake plate) of a warp let-off device for a loom according to a sixth embodiment.
  • FIG. 1 shows the basic structure of a warp let-off device 1 for a loom according to embodiments of the present invention.
  • the warp let-off device 1 includes a drive unit 3 for driving a warp beam 2 .
  • the drive unit 3 includes a dedicated motor 32 which functions as a drive source 4 and a transmission 5 which transmits the rotation of the dedicated motor 32 to the warp beam 2 .
  • the gear 50 is a worm wheel, and the worm 34 and the gear 50 form a worm gear mechanism with a large reduction ratio which has a non-return function (self-lock function). Accordingly, although the rotation of the dedicated motor 32 is transmitted to the warp beam gear 35 after the rotational speed is reduced, reverse operation cannot be performed. More specifically, rotational force of the warp beam gear 35 cannot be transmitted to the worm 34 .
  • the drive unit 3 rotates the warp beam 2 while applying a braking force to the warp beam 2 against a warp tension T applied to warp 9 which is fed toward a cloth fell 8 from the warp beam 2 .
  • the braking force against the warp tension T is obtained by the non-return function (self-lock function) of the worm gear mechanism (the worm 34 and the gear (worm wheel) 50 meshing therewith).
  • the warp 9 is fed from the warp beam 2 in the form of a sheet, is guided by a guide roller 6 and a tension roller 7 , and is conveyed toward the cloth fell 8 .
  • the tension roller 7 is moveably supported by a tension supplying means (not shown) to apply a predetermined warp tension T to the warp 9 .
  • the warp let-off device 1 for the loom according to the present invention is characterized by including a brake unit 10 for applying a braking force to the warp beam 2 separately from the braking force applied by the drive unit 3 .
  • Examples of the brake unit 10 will be explained in the embodiments below.
  • a one-way rotation transmission 13 is used in embodiments other than a second embodiment, and an actuator 31 for reducing a contact pressure against a brake disc 25 is used in the second embodiment.
  • a brake unit 10 includes a one-way rotation transmission 13 disposed between a brake gear 11 and a brake shaft 14 as a braking-force reducing means 12 .
  • the brake unit 10 includes the brake gear 11 which meshes with the warp beam gear 35 , a circular brake plate 23 which functions as a braking means for applying a braking force to the brake gear 11 , a pair of brake discs 25 , and the one-way rotation transmission 13 which applies a braking force to the rotation of the warp beam 2 in an unwinding direction (hereafter called forward rotation) but applies no braking force to the rotation of in the winding direction (hereafter called reverse rotation).
  • the one-way rotation transmission 13 is, for example, a one-way clutch, and the warp beam gear 35 is concentrically attached to the rotating shaft 21 which supports the warp beam 2 .
  • the brake gear 11 and the pair of brake discs 25 are all supported by the brake shaft 14 .
  • the brake shaft 14 is supported by a ball bearing 15 and a bearing housing 16 in such a manner that the brake shaft 14 can rotate with respect to a frame 17 .
  • the brake gear 11 is attached to an end portion of the brake shaft 14 with a needle bearing 18 , the one-way rotation transmission (one-way clutch) 13 , a sleeve 19 , and a key 22 of the sleeve 19 interposed therebetween at a position such that the brake gear 11 meshes with the warp beam gear 35 .
  • the brake unit 10 includes a plurality of columns 20 attached to the bearing housing 16 , a circular brake plate 23 which is non-rotatably supported by the columns 20 , the pair of brake discs 25 which clamp the circular brake plate 23 , and a brake spring 27 .
  • Rotation of the pair of brake discs 25 with respect to the brake shaft 14 is locked by a spline or the like, and the brake discs 25 are supported such that they can move along the shaft.
  • Brake linings 24 provided at the periphery of the brake discs 25 come into frictional contact with the surfaces of the circular brake plate 23 , and accordingly the braking force is applied to the brake shaft 14 .
  • the brake spring 27 is shaped like a coil provided around the brake shaft 14 .
  • One end of the brake spring 27 is in contact with one of the brake discs 25 which is adjacent to the brake spring 27 , and the other end is in contact with a spring receiver 28 fitted around the brake shaft 14 .
  • the spring receiver 28 is in contact with an adjustment nut 26 engaged with an external screw 29 on the brake shaft 14 , and compresses the brake spring 27 to generate a frictional force corresponding to the required braking force between the circular brake plate 23 and the pair of brake linings 24 .
  • the brake disc 25 adjacent to the one-way rotation transmission (one-way clutch) 13 is pushed toward the ball bearing 15 with a receiving ring 30 disposed therebetween. Accordingly, the brake unit 10 generates the required braking force from the frictional force between the circular brake plate 23 and the pair of brake linings 24 .
  • the needle bearing 18 allows the rotation of the brake gear 11 with respect to the brake shaft 14 .
  • the brake gear 11 allows the rotation of the warp beam gear 35 in the winding direction (reverse rotation)
  • the brake gear 11 rotates together with the brake shaft 14 wile the warp beam gear 35 rotates in the unwinding direction (forward rotation), and thereby applies the braking force of the brake unit 10 against the warp tension T.
  • the one-way rotation transmission 13 is interposed between the rotating shaft 21 of the warp beam 2 and the braking-force reducing means 12 for applying the braking force of the brake unit 10 to the rotation of the warp beam 2 in the unwinding direction, but applies no braking force of the brake unit 10 to the rotation in the winding direction, that is, in the direction against the warp tension T.
  • a braking force is applied to the rotation of the warp beam 2 in the unwinding direction.
  • the braking force applied at this time is the sum of the braking force obtained by the non-return function (self-lock function) of the worm gear mechanism (the worm 34 and the warp beam gear (worm wheel) 35 meshing therewith) and the braking force of the brake unit 10 . Accordingly, the rotational vibration of the warp beam 2 can be prevented and the weaving bars do not occur.
  • the one-way rotation transmission (one-way clutch) 13 which functions as the braking-force reducing means 12 , allows the reverse rotation of the warp beam 2 (rotation in the winding direction). Accordingly, the braking force of the brake unit 10 is not applied to the reverse rotation of the warp beam 2 (rotation in the winding direction), and is reduced to substantially 0. Therefore, although the brake unit 10 is provided, the load of the drive unit 3 does not increase in the reverse rotation of the warp beam 2 , and is lower than the load in the rotation in the unwinding direction.
  • the one-way rotation transmission (one-way clutch) 13 which functions as the braking-force reducing means 12 , is interposed between the brake unit 10 and the rotating shaft 21 .
  • the one-way rotation transmission (one-way clutch) 13 may also be installed between the brake discs 25 and the brake shaft 14 .
  • the one-way rotation transmission 13 may also be an electromagnetic clutch instead of one-way clutch. In such a case, the electromagnetic clutch may be excited manually or in association with the control operation of the loom when the braking force is required, and the excitation may be cancelled to set a free state when the braking force is not necessary, such as when the reverse rotation is performed.
  • a braking-force reducing means 12 of a brake unit 10 includes an actuator 31 , for example, an air cylinder, for reducing a contact pressure between a circular brake plate 23 integrated with a brake shaft 14 and a pair of brake discs 25 .
  • the pair of brake discs 25 are brought into contact with or moved away from the circular brake plate 23 depending on whether the warp beam 2 is rotated in the forward or reverse rotation.
  • a brake gear 11 is directly fixed to the brake shaft 14 with a key 22 .
  • the actuator 31 is attached to an attachment plate 36 fixed to columns 20 at one end thereof.
  • the amount of projection (projecting force) of an actuator rod 37 of the actuator 31 is controlled with a pressure source 38 , a valve 39 , and a control unit 40 .
  • the actuator rod 37 extends through the attachment plate 36 , and applies a predetermined projecting force to an end portion of a brake spring 27 via a spring receiver 28 attached at the end of the actuator rod 37 . Accordingly, when the brake shaft 14 rotates, a predetermined frictional force (braking force) is applied between the circular brake plate 23 and the pair of brake discs 25 .
  • the control unit 40 controls the valve 39 to move the actuator rod 37 in the projecting direction, so that the pair of brake discs 25 receive a predetermined contact pressure and the braking force is applied to the warp beam 2 .
  • the control unit 40 controls the valve 39 to retract the actuator rod 37 so that the pair of brake discs 25 move away from the circular brake plate 23 by a distance small enough not to cause separation of the brake discs 25 from the circular brake plate 23 . Accordingly, the braking force between the circular brake plate 23 and the pair of brake discs 25 is reduced or substantially eliminated.
  • the actuator 31 may be a hydraulic air cylinder or an electromagnetic solenoid instead of an air cylinder.
  • the actuator 31 may be a unit obtained by combining an electric or hydraulic motor with a mechanism, such as a screw mechanism, for converting rotation to linear motion.
  • the brake unit 10 and a braking-force reducing means 12 are installed at a position where a rotating shaft 21 for supporting a warp beam 2 is disposed.
  • a one-way rotation transmission (one-way clutch) 13 which functions as the braking-force reducing means 12 , is fitted around the rotating shaft 21 .
  • the one-way rotation transmission 13 (one-way clutch) slips while the rotating shaft 21 rotates in the reverse direction.
  • a sliding bearing 41 which functions as brake unit 10 , is disposed between the one-way rotation transmission (one-way clutch) 13 and a loom frame 42 .
  • a braking force is generated by friction (sliding resistance) between an inner ring 43 and an outer ring 44 of the sliding bearing 41 . In this case, the frictional force increases, that is, the braking force increases as the diameter of the rotating shaft 21 increases.
  • the structure of the fourth embodiment is similar to that of the first embodiment ( FIG. 2 ) except a torsional coil spring 45 is provided as the one-way rotation transmission 13 instead of a one-way clutch.
  • the torsional coil spring 45 is disposed around a brake shaft 14 between a pair of brake discs 25 and a brake gear 11 .
  • the torsional coil spring 45 is wound around the peripheral surface of the brake shaft 14 , and is fixed to the brake shaft 14 at one end and to a boss portion of the brake gear 11 at the other end.
  • the brake gear 11 rotates in a direction to twist the torsional coil spring 45 . Accordingly, after the torsional coil spring 45 is twisted by a predetermined amount or to the limit, the rotation of the brake gear 11 is transmitted to the brake shaft 14 . As a result, when the warp beam 2 rotates in the unwinding direction, the braking force of the brake unit 10 is applied to the warp beam 2 .
  • the brake gear 11 rotates in a direction to untwist (release) the torsional coil spring 45 , and therefore the torsional coil spring 45 rotates while applying an urging force to the brake gear 11 .
  • the rotation of the brake gear 11 is not transmitted to the brake discs 25 , so that the braking force of the brake unit 10 is not applied to the warp beam 2 .
  • the amount of reverse rotation is limited to an amount such that the braking force is not exceeded (such that the brake discs 25 do not rotate during the reverse rotation).
  • the spring constant of the torsional coil spring 45 is set such that the braking force is not exceeded (such that the amount of twist is sufficient relative to the amount of reverse rotation).
  • the structure of the fifth embodiment is similar to that of the fourth embodiment ( FIG. 5 ) except a helical compression spring 46 , a brake connecting member 47 , and a gear connecting member 48 are used instead of the torsional coil spring 45 , as shown in FIGS. 6 and 7 .
  • the brake connecting member 47 is fixed to a brake shaft 14
  • the gear connecting member 48 is fixed to a brake gear 11 .
  • the brake connecting member 47 and the gear connecting member 48 are connected to each other with the helical compression spring 46 .
  • the brake gear 11 rotates in a direction to compress the helical compression spring 46 . Accordingly, after the helical compression spring 46 is compressed to the limit or a compressing force of the helical compression spring 46 reaches a value corresponding to a braking force of a brake unit 10 , the rotation of the brake gear 11 is transmitted to the brake discs 25 . Accordingly, the braking force of the brake unit 10 is applied to the warp beam 2 .
  • the brake gear 11 rotates in a direction to cancel the compressed state of the helical compression spring 46 . Accordingly, the brake gear 11 rotates while receiving an urging force from the helical compression spring 46 . At this time, the rotation of the brake gear 11 is not transmitted to the brake discs 25 , so that the braking force of the brake unit 10 is not applied to the brake gear 11 .
  • the amount of reverse rotation is limited to an amount such that the braking force is not exceeded (such that the brake discs 25 do not rotate during the reverse rotation).
  • the spring constant of the helical compression spring 46 is set such that the braking force is not exceeded (such that the amount of twist is sufficient relative to the amount of reverse rotation).
  • the structure of the sixth embodiment is similar to that of the first embodiment ( FIG. 2 ) except a circular brake plate 23 disposed between the pair of brake discs 25 is set to be rotatable within a predetermined range, as shown in FIG. 8 , instead of using the one-way clutch as the one-way rotation transmission 13 .
  • the circular brake plate 23 is fitted to columns 20 with long attachment holes 49 extending along the circumferential direction, and can rotate along with the pair of brake discs 25 within the range corresponding to the attachment holes 49 .
  • the pair of brake discs 25 and the circular brake plate 23 disposed between the brake discs 25 rotate together as the brake shaft 14 rotates.
  • the inner walls of the attachment holes (long holes) 49 formed in the circular brake plate 23 come into contact with the columns 20 at one end thereof, the circular brake plate 23 stops. Therefore, the pair of brake discs 25 rotate while exerting a frictional force, and the braking force of the brake unit 10 is applied to the warp beam 2 .
  • the pair of brake discs 25 and the circular brake plate 23 disposed between the brake discs 25 rotate together as the brake shaft 14 rotates. Then, when the inner walls of the attachment holes (long holes) 49 formed in the circular brake plate 23 come into contact with the columns 20 at the other end thereof, the circular brake plate 23 stops. Thus, the braking force of the brake unit 10 is not applied until the inner walls of the attachment holes (long holes) 49 in the circular brake plate 23 come into contact with the columns 20 .
  • the amount of reverse rotation of the warp beam 2 is limited such that the inner walls of the attachment holes 49 in the circular brake plate 23 do not come into contact with the columns 20 (such that the braking force is not applied in the reverse rotation).
  • the sixth embodiment is applied to a mechanical drive unit, for example, a drive unit including a transmission which changes the reduction ratio depending on the warp tension T.
  • a mechanical drive unit for example, a drive unit including a transmission which changes the reduction ratio depending on the warp tension T.
  • the drive unit 3 is electrical, reverse rotation is repeatedly performed by the dedicated motor 32 . Therefore, the amount of reverse rotation is limited by the drive unit 3 , or the size(range) of the attachment holes 49 is increased.
  • rotational driving of the warp beam 2 in the unwinding direction is regarded as braking/loosening driving for applying a braking force against the warp tension T, and the direction of load is the same as the rotating direction.
  • worm gear mechanisms are often used in the let-off device.
  • the worm gear mechanism (the worm 34 and the warp beam gear (worm wheel) 35 ) constantly applies a braking force to the warp beam 2 in order to prevent the warp beam 2 from slipping while the warp 9 is fed in the let-off motion.
  • a torque of the drive unit 3 required during the forward rotation of the warp beam 2 is determined depending on the braking force of the worm gear mechanism (the worm 34 and the warp beam gear (worm wheel) 35 ), that is, depending on the warp tension T.
  • the relationship between the motor torque TF against the warp tension T required of the dedicated motor 32 connected to the worm gear mechanism in the forward rotation and the motor torque TR required in the reverse rotation is expressed as TF ⁇ TR.
  • the ratio between the required motor torques TR/TF is about 3 or 4 (when the angle of lead is 10°). This means that the motor torque TR required in the reverse rotation is three or more times the motor torque TF required in the forward rotation even when the brake unit 10 is not provided. Therefore, there is a demand to reduce the motor torque TR required in the reverse rotation.
  • the reduction ratio of the dedicated motor 32 is increased to obtain a large motor torque TR in the reverse rotation.
  • the reduction ratio is increased, the maximum rotational speed of the warp beam 2 is reduced and low-density weaving cannot be performed. If settings are made such that low-density weaving can be performed, allowable warp tension T is reduced.
  • the torque required of the drive unit 3 of the warp beam 2 is increased.
  • the warp beam 2 when the warp beam 2 rotates in the reverse direction, opposite to the forward rotation, the warp beam 2 must be rotated with a torque high enough to overpower the sum of the warp tension T and the warp-beam braking force B. Therefore, the torque required in the reverse rotation of the warp beam 2 is calculated as (warp tension T)+(warp-beam braking force B). Accordingly, the capacity of the drive unit 3 is determined on the basis of the torque required in the reverse rotation of the warp beam 2 . Therefore, a motor with high capacity relative to the torque required in the forward rotation of the warp beam 2 must be used as the dedicated motor 32 .
  • the generated torque cannot be sufficiently exploited, and the range of use conditions, such as the allowable warp tension and the range of pick density, that is, the number of picks per inch (the rotational speed of the warp beam must be increased as the pick density is reduced), etc., is limited.
  • the drive unit 3 is not limited to electrical drive units, and mechanical drive units may also be used.
  • the braking force of the brake unit 10 may be applied over the entire period of the let-off motion.
  • the braking force of the brake unit 10 may be applied only under weaving conditions which tend to cause weaving bars or vibration of the warp beam 2 in a loom which changes the weaving conditions in the weaving process.
  • the transmission 5 may be controlled by the brake unit 10 .
  • the braking force of the brake unit 10 connected to the one-way clutch may be applied to the drive shaft 33 .
  • Such a structure is suitable for the case in which a dedicated motor having a braking function is used instead of the worm gear mechanism.

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  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Looms (AREA)
US11/175,309 2004-07-22 2005-07-07 Warp let-off device for loom Abandoned US20060016504A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2004-214796 2004-07-22
JP2004214796A JP4663266B2 (ja) 2004-07-22 2004-07-22 織機の経糸送り出し装置

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US (1) US20060016504A1 (zh)
JP (1) JP4663266B2 (zh)
KR (1) KR20060048337A (zh)
CN (1) CN1724735B (zh)

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US20100101679A1 (en) * 2008-10-24 2010-04-29 Groz-Beckert Kg Spreader with clamping and ventilating devices
CN106192169A (zh) * 2016-09-05 2016-12-07 江苏工程职业技术学院 一种交替产生不同立体泡绉效应的织机送经机构
RU2606221C2 (ru) * 2015-02-02 2017-01-10 федеральное государственное бюджетное образовательное учреждение высшего образования "Костромской государственный университет" (КГУ) Устройство для формирования трехмерной ткани
CN108221145A (zh) * 2018-01-30 2018-06-29 约科布·缪勒机械制造(中国)有限公司 Vtx单向传动控制装置
CN115029844A (zh) * 2022-06-27 2022-09-09 浙江泰坦股份有限公司 一种喷气织机自动上经轴装置

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CN102443947A (zh) * 2011-09-26 2012-05-09 江苏万工科技集团有限公司 一种双后梁转动联动装置
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CN105537900B (zh) * 2016-03-04 2017-12-12 郑州纺机工程技术有限公司 一种用于浆纱机自动上落经轴装置
CN108691075A (zh) * 2018-07-10 2018-10-23 山东日发纺织机械有限公司 主动送经装置
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Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2518158A (en) * 1948-05-18 1950-08-08 Kellogg M W Co Electrical let-off
US3677305A (en) * 1971-02-19 1972-07-18 Southern Machinery Co Loom having interconnected warp let-off and cloth take-up means at back of loom
US3704731A (en) * 1970-03-02 1972-12-05 Wernli Ag Verbandstaff Fabrik Warpbeam brake device
US3752378A (en) * 1970-12-21 1973-08-14 Scheffel W Device for supplying strip-like fabric by means of rollers
US3799210A (en) * 1971-06-19 1974-03-26 A Gardella Brake unit for the warp beam of weaving looms
US3802467A (en) * 1971-02-26 1974-04-09 Picanol Nv Warp unwinder for weaving looms
US4125131A (en) * 1976-09-21 1978-11-14 Adolph Saurer Fixed driving connection between a guide roller and delivery roller of a loom
US4407331A (en) * 1979-09-29 1983-10-04 Walter Rehling Speed regulator for the warp beam of a weaving machine
US4552186A (en) * 1982-12-02 1985-11-12 Nissan Motor Co., Ltd. Warp let-off mechanism of weaving machine

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3749136A (en) * 1971-10-13 1973-07-31 D Robinson Tension control device
US4485849A (en) * 1982-06-14 1984-12-04 Franks Bobby L Loom beam let off

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2518158A (en) * 1948-05-18 1950-08-08 Kellogg M W Co Electrical let-off
US3704731A (en) * 1970-03-02 1972-12-05 Wernli Ag Verbandstaff Fabrik Warpbeam brake device
US3752378A (en) * 1970-12-21 1973-08-14 Scheffel W Device for supplying strip-like fabric by means of rollers
US3677305A (en) * 1971-02-19 1972-07-18 Southern Machinery Co Loom having interconnected warp let-off and cloth take-up means at back of loom
US3802467A (en) * 1971-02-26 1974-04-09 Picanol Nv Warp unwinder for weaving looms
US3799210A (en) * 1971-06-19 1974-03-26 A Gardella Brake unit for the warp beam of weaving looms
US4125131A (en) * 1976-09-21 1978-11-14 Adolph Saurer Fixed driving connection between a guide roller and delivery roller of a loom
US4407331A (en) * 1979-09-29 1983-10-04 Walter Rehling Speed regulator for the warp beam of a weaving machine
US4552186A (en) * 1982-12-02 1985-11-12 Nissan Motor Co., Ltd. Warp let-off mechanism of weaving machine

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080135123A1 (en) * 2006-12-12 2008-06-12 Sultex Ag Cloth draw-off apparatus
US20100101679A1 (en) * 2008-10-24 2010-04-29 Groz-Beckert Kg Spreader with clamping and ventilating devices
US7798179B2 (en) * 2008-10-24 2010-09-21 Groz-Beckert Kg Spreader with clamping and ventilating devices
RU2606221C2 (ru) * 2015-02-02 2017-01-10 федеральное государственное бюджетное образовательное учреждение высшего образования "Костромской государственный университет" (КГУ) Устройство для формирования трехмерной ткани
CN106192169A (zh) * 2016-09-05 2016-12-07 江苏工程职业技术学院 一种交替产生不同立体泡绉效应的织机送经机构
CN108221145A (zh) * 2018-01-30 2018-06-29 约科布·缪勒机械制造(中国)有限公司 Vtx单向传动控制装置
CN115029844A (zh) * 2022-06-27 2022-09-09 浙江泰坦股份有限公司 一种喷气织机自动上经轴装置

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JP4663266B2 (ja) 2011-04-06
KR20060048337A (ko) 2006-05-18
CN1724735B (zh) 2012-03-28
JP2006037246A (ja) 2006-02-09

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