EP1544338A2 - Dispositif de détection de tension de la chaíne pour métier à tisser - Google Patents

Dispositif de détection de tension de la chaíne pour métier à tisser Download PDF

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Publication number
EP1544338A2
EP1544338A2 EP03029492A EP03029492A EP1544338A2 EP 1544338 A2 EP1544338 A2 EP 1544338A2 EP 03029492 A EP03029492 A EP 03029492A EP 03029492 A EP03029492 A EP 03029492A EP 1544338 A2 EP1544338 A2 EP 1544338A2
Authority
EP
European Patent Office
Prior art keywords
warp
roller
tension
angle
detecting device
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.)
Withdrawn
Application number
EP03029492A
Other languages
German (de)
English (en)
Other versions
EP1544338A3 (fr
Inventor
Shinya Abe
Isao Makino
Yasutaka Murakami
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.)
Toyota Industries Corp
Original Assignee
Toyota Industries Corp
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 Toyota Industries Corp filed Critical Toyota Industries Corp
Publication of EP1544338A2 publication Critical patent/EP1544338A2/fr
Publication of EP1544338A3 publication Critical patent/EP1544338A3/fr
Withdrawn legal-status Critical Current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
    • 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
    • D03D49/12—Controlling warp tension by means other than let-off mechanisms
    • D03D49/14—Compensating for tension differences during shedding
    • 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
    • D03D49/18—Devices for indicating warp tension

Definitions

  • the present invention relates to a warp tension detecting device for a loom.
  • JP 02-269841 A discloses a loom in which the spring force of a tension spring is imparted to a tension lever rotatably supporting a tension roller guiding warp fed out from a warp beam, and fluctuations in the tension of the warp are absorbed by the spring force of this tension spring.
  • the tension of the warp is detected by a load cell through the tension roller.
  • An rpm of a feed-out motor for feeding out the warp by rotating a warp beam is controlled on the basis of warp tension detection information obtained by the load cell.
  • a swinging displacement of an easing lever swung in synchronism with the running of the loom is transmitted to a tension detecting roller for detecting warp tension while guiding the warp fed out from a warp beam.
  • the transmission of the swinging displacement of the easing lever absorbs fluctuations in warp tension.
  • the warp tension is detected by a load cell through the tension detecting roller.
  • the rpm of a feed-out motor for feeding out warp by rotating the warp beam is controlled on the basis of warp tension detection information obtained by the load cell.
  • a warp tension detecting device for a loom in which fluctuations in tension of warp fed out from a warp beam are absorbed by transmitting to the warp a swinging displacement of an easing lever swung in synchronism with a running of the loom, and the tension of the warp is detected through a first roller for guiding the warp, including:
  • the tension of the warp refers to the sum total of the tensions of a large number of warps wound around the warp beam.
  • a load detector detects through a first roller a load reflecting the tension of the warp. That is, the inertia of the easing motion of a second roller does not affect the load detection of the load detector, so that, even when the tension of the warp is low, it is possible to perform load detection (i.e., warp tension detection) with high accuracy.
  • the fluctuations in the warp tension are absorbed through positive easing of the second roller, so that, even when the tension of the warp is low and the loom is operating at high speed, the fluctuations in the warp tension can be absorbed in a satisfactory manner.
  • a warp beam 11 is driven by a feed-out motor 12.
  • Warp T fed out from the warp beam 11 is guided while being held in contact with a first roller 13 and a second roller 14.
  • the second roller 14 is on a downstream side of the first roller 13 with respect to the movement route for the warp T.
  • the solid-line circled indicates a maximum winding diameter of the warp beam 11
  • the broken-line circle C2 indicates a minimum winding diameter of the warp beam 11. In the state in which the winding diameter is minimum, all the warp on the warp beam 11 has been consumed.
  • the movement route S11 for the warp T shown in Fig. 3 corresponds to the case in which the winding diameter of the warp beam 11 is maximum.
  • the movement route S12 for the warp T shown in Fig. 3 corresponds to the case in which the winding diameter of the warp beam 11 is medium.
  • the movement route S13 for the warp T shown in Fig. 3 corresponds to the case in which the winding diameter of the warp beam 11 is minimum.
  • back brackets 15 and 16 are fixed to right and left side frames (not shown).
  • pivots 17 and 18 are supported by the back bracket 15 in a cantilever-like fashion.
  • pivots 19 and 20 are supported by the back bracket 16 in a cantilever-like fashion.
  • Support levers 21 and 22 are rotatably supported by the pivots 17 and 19, respectively.
  • Easing levers 23 and 24 are rotatably supported by and dangle from the pivots 18 and 20, respectively.
  • the first roller 13 is rotatably supported through the intermediation of a roller shaft 131 at the rear ends of the support levers 21 and 22 (In Fig.
  • a second roller 14 is supported through the intermediation of a roller shaft 141 at the intermediate portions of the easing levers 23 and 24.
  • the first roller 13 is rotatable around the roller shaft 131, and the second roller 14 is rotatable around the roller shaft 141.
  • Warp T fed out from the warp beam 11 moves along movement routes S2 and S3 indicated by a chain line in Fig. 1.
  • Load cells 25 and 26 serving as load detectors are connected to forward end portions of the support levers 21 and 22 through pin connection using shaft pins 27 and 28 and rods 29 and 30. Further, the load cells 25 and 26 are connected to the back brackets 15 and 16, respectively, through pin connection using shaft pins 31 and 32 and rods 33 and 34.
  • the load cell 25 and the rods 29 and 33 constitute a detection arm 35 including the load detector as a part thereof.
  • the load cell 26 and the rods 30 and 34 constitute a detection arm 36 including the load detector as a part thereof.
  • the support levers 21 and 22, the pivots 17 and 19, and the back brackets 15 and 16 constitute a support mechanism for supporting the first roller 13.
  • the positions of the axial centers 171 and 191 of the pivots 17 and 19 are fulcrum positions for the support levers 21 and 22 rotatably supporting the first roller 13.
  • the position of the axial center 132 of the roller shaft 131 is the connecting position of the support levers 21 and 22 and the roller shaft 131 of the first roller 13. This connecting position is the force application point for the support levers 21 and 22.
  • the first roller 13 is arranged below and behind the second roller 14.
  • the fulcrum positions for the support levers 21 and 22 (the positions of the axial centers 171 and 191 of the pivots 17 and 19) is set so as to be not lower than the height position of the axial center 132 of the first roller 13 and not higher than the height position of the axial center 142 of the second roller 14 and to be in front of the second roller 14.
  • the detection arms 35 and 36 including the load cells 25 and 26 as a part are connected to the support levers 21 and 22 so as to cross the line L (shown in Figs. 3 and 4) connecting the fulcrum point and the force application point as seen in the axial direction of the roller shaft 131 of the first roller 13.
  • the crossing angle of the support lever 21 and the detection arm 35 is the crossing angle ⁇ made by the line K1 (shown in Fig. 3) passing the centers of the shaft pins 27 and 31 and the line L as seen in the axial direction of the roller shaft 131.
  • the crossing angle of the support lever 22 and the detection arm 36 is the crossing angle ⁇ made by the line K2 (shown in Fig. 5) passing the centers of the shaft pins 28 and 32 and the line L as seen in the axial direction of the roller shaft 131.
  • the crossing angle ⁇ is a right angle.
  • the winding diameter of the warp beam 11 varies from the maximum diameter indicated by the solid-line circle C1 to the minimum diameter indicated by the broken-line circle C2, shown in Fig. 1.
  • a first angle ⁇ (shown in Fig. 4) made by the movement route for the warp T between the warp beam 11 and the first roller 13 and the line L is set to be larger than a second angle ⁇ (shown in Fig. 4) made by the movement route S2 for the warp T between the first roller 13 and the second roller 14 and the line L.
  • the load cells 25 and 26 are arranged on the side of the second angle ⁇ smaller than the first angle ⁇ as seen in the axial direction of the roller shaft 131 of the first roller 13. That is, the load cells 25 and 26 are arranged above the support levers 21 and 22.
  • the easing levers 23 and 24 are operationally connected to a crank mechanism 39 through the intermediation of easing rods 37 and 38.
  • the crank mechanism 39 rotates in synchronism with the running of the loom, with the easing levers 23 and 24 swinging around the pivots 18 and 20 in conformity with periodical fluctuations in tension during one rotation of the loom. That is, the easing levers 23 and 24 swing between the solid-line position of Fig. 3 and the solid-line position of Fig. 4 through the rotating operation of the crank mechanism 39 in synchronism with the running of the loom.
  • the second roller 14 moves forwards and backwards by periodical swinging of the easing levers 23 and 24 in synchronism with periodical fluctuations in warp tension during one rotation of the loom. The periodical fluctuations in warp tension during one rotation of the loom are thus absorbed by the swinging of the second roller 14.
  • the load applied to the first roller 13 by the tension of the warp T is divisionally received by the load cells 25 and 26 through the support levers 21 and 22.
  • the load cells 25 and 26 detect the load divisionally received by the support levers 21 and 22. That is, the load cells 25 and 26 detect a load reflecting the tension of the warp T.
  • Information on the load detected by the load cells 25 and 26 is transmitted to a control computer 10.
  • the control computer 10 compares a target load reflecting a pre-set target tension with the load detected by the load cells 25 and 26, and controls the rpm of the feed-out motor 12 in such a way that the detected load coincides with the target load. That is, the control computer 10 controls the rpm of the feed-out motor 12 so as to make the tension of the warp T corresponding to the load detected by the load cells 25 and 26 coincide with the target tension.
  • the first embodiment provides the following advantages.
  • arrows Ro, R1, R2, and R3 indicate tensions of the warp T.
  • the values of the tensions Ro, R1, R2, and R3 are equal to one another.
  • the tension R1 corresponds to the case in which the winding diameter of the warp beam 11 is maximum, that is, the case in which the movement route for the warp T is S11.
  • the tension R2 corresponds to the case in which the winding diameter of the warp beam 11 is medium, that is, the case in which the movement route for the warp T is S12.
  • the tension R3 corresponds to the case in which the winding diameter of the warp beam 11 is minimum, that is, the case in which the movement route for the warp T is S13.
  • the arrow Q1 indicates the resultant force of the tension Ro and the tension R1
  • the arrow Q2 indicates the resultant force of the tension Ro and the tension R2
  • the arrow Q3 indicates the resultant force of the tension Ro and the tension R3.
  • the resultant forces Q1, Q2, and Q3 act on the first roller 13 so as to pass through the axial center 132 of the roller shaft 131.
  • the lines of action of the resultant forces Q1, Q2, and Q3 are in lines deviated from the fulcrum positions for the support levers 21 and 22 (i.e., the axial centers 171 and 191 of the pivots 17 and 19).
  • the curve E represents changes in the product of the resultant forces Q1, Q2, and Q3 changing according to the change in the winding diameter of the warp beam 11 and the distances z1, z2, and z3 between the arrows indicating these resultant forces and the axial centers 171 and 191 of the pivots 17 and 19, that is, changes in moment.
  • the moment M2 is minimum when the winding diameter of the warp beam 11 is the medium winding diameter r2.
  • the moment M1 is maximum
  • the moment M3 when the winding diameter of the warp beam 11 is the maximum diameter r3 the moment is somewhat smaller than the maximum moment M1. That is, the moments M1, M2, andM3 are in the relationship: M1 > M3 > M2.
  • the way of moment change as indicated by the curve E of Fig. 6 results when the position of the roller shaft 131 of the first roller 13, the position of the roller shaft 141 of the second roller 14, and the positions of the pivots 17 and 19 for the support levers 21 and 22 are determined as in this embodiment. That is, by setting the positions of the roller shaft 131, the roller shaft 141, and the pivots 17 and 19 in such a way that the first angle ⁇ made by the movement route S11, S12, S13 for the warp T and the line L is larger than the second angle ⁇ made by the movement route S2 for the warp T and the line L, the moment tends to change as indicated by the curve E.
  • the moment tends to vary as indicated, for example, by the curve G2 of Fig. 6. That is, the winding diameter corresponding to the minimum value in the curve G1 is smaller than the winding diameter r2, and the winding diameter corresponding to the minimum value in the curve G2 is larger than the winding diameter r2. And, the moment changing amounts of the curves G1 and G2 corresponding to the changes in the winding diameters r1 through r3 are larger than that in the case of the curve E.
  • the moment changing amount during the change of the winding diameter of the warp beam 11 from the maximum diameter r3 to the minimum diameter r1 is very close to the minimum value. That is, the error in the detected tension of the warp is very close to the minimum value as in the case in which the warp tension is detected with the warp tension undergoing no change.
  • the rpm control for the feed-out motor 12 utilizing the detected tension is effected with high accuracy so as to provide a desired warp tension.
  • the rotation center 111 of the warp beam 11, the rotation center of the first roller 13 (the axial center 132 of the roller shaft 131), and the rotation center of the second roller 14 (the axial center 142 of the roller shaft 141) are determined first.
  • the axial center 132 of the roller shaft 131 and the axial center 142 of the roller shaft 141 are determined, the movement route for the warp T between the first roller 13 and the second roller 14 is determined.
  • the maximum diameter and the minimum diameter of the warp beam 11 are also determined beforehand, so that, when the rotation center 111 of the warp beam 11 and the axial center 132 of the roller shaft 131 are determined, the movement route for the warp T between the warp beam 11 and the first roller 13 is also determined.
  • the rotation centers of the support levers 21 and 22 are finally determined.
  • the positions of the roller shaft 131, the roller shaft 141, and the pivots 17 and 19 are determined so as to achieve the above-described moment change as indicated by the curve E, that is, in such a way that the above moment is minimum when the winding diameter of the warp beam 11 is the medium winding diameter.
  • a rod-shaped balance weight 40 extends across and is supported by the support levers 21 and 22 at the forward end portions thereof.
  • the balance weight 40 is arranged so as to be parallel to the roller shaft 131 of the first roller 13.
  • the balance weight 40, the support levers 21 and 22, and the roller shaft 131 form a rectangular frame.
  • the balance weight 40 serves to prevent torsion of the roller shaft 131 and the support levers 21 and 22 connected together. Further, the balance weight 40 is provided to maintain balance in weight between the balance weight 40 and the first roller 13 supported by the pivots 17 and 19, preventing the weight of the first roller 13 and the roller shaft 131 from being applied to the load cells 25 and 26. This balance in weight is effective in eliminating the influence of the inertial force of the first roller 13.

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  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Looms (AREA)
EP03029492A 2003-02-19 2003-12-19 Dispositif de détection de tension de la chaîne pour métier à tisser Withdrawn EP1544338A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2003041750A JP2004250817A (ja) 2003-02-19 2003-02-19 織機における経糸張力検出装置
JP2003041750 2003-12-19

Publications (2)

Publication Number Publication Date
EP1544338A2 true EP1544338A2 (fr) 2005-06-22
EP1544338A3 EP1544338A3 (fr) 2006-04-05

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP03029492A Withdrawn EP1544338A3 (fr) 2003-02-19 2003-12-19 Dispositif de détection de tension de la chaîne pour métier à tisser

Country Status (3)

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EP (1) EP1544338A3 (fr)
JP (1) JP2004250817A (fr)
CN (1) CN1306088C (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1878821A1 (fr) * 2006-07-11 2008-01-16 Tsudakoma Kogyo Kabushiki Kaisha Dispositif de soutien de cylindre d'un métier à tisser
EP2184390A1 (fr) * 2008-11-10 2010-05-12 Tsudakoma Kogyo Kabushiki Kaisha Dispositif de déroulage de fils de chaîne d'un métier à tisser utilisant un mécanisme positive de support pour le porte-fils
EP2937451A1 (fr) * 2014-04-24 2015-10-28 Tsudakoma Kogyo Kabushiki Kaisha Dispositif de rétraction de rouleau de relâchement pour métier à tisser
WO2018073386A1 (fr) * 2016-10-20 2018-04-26 Lindauer Dornier Gesellschaft Mit Beschränkter Haftung Dispositif de mesure de la tension de chaine dans une machine à tisser et machine a tisser équipé d'un tel dispositif
CN108584508A (zh) * 2018-05-18 2018-09-28 常州市新创智能科技有限公司 在线展纤用缓冲恒张力装置及其使用方法
CN115029841A (zh) * 2022-07-06 2022-09-09 天津工业大学 一种织造间隔织物特种织机送经系统的张力施加与检测装置

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5778544B2 (ja) * 2011-10-19 2015-09-16 津田駒工業株式会社 織機の張力検出装置
CN104153146A (zh) * 2013-05-14 2014-11-19 台嘉玻璃纤维有限公司 带有张力控制装置的玻璃纤维上浆机
CN103743516B (zh) * 2014-01-10 2015-12-09 宁波慈星股份有限公司 针织横机的主罗拉成套牵引力检测装置
CN104328583A (zh) * 2014-10-22 2015-02-04 杭州创兴织造设备科技有限公司 一种在经轴输出经线处的张力检测机构
EP3744878A4 (fr) * 2018-01-26 2021-10-13 Toray Industries, Inc. Faisceau de fibres ignifuges et procédé de fabrication de faisceau de fibres de carbone

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB918817A (en) * 1960-05-11 1963-02-20 Sulzer Ag Looms
EP0527705A1 (fr) * 1991-08-12 1993-02-17 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Procédé et dispositif pour détecter la tension des fils de chaîne dans un métier à tisser
EP0537111A1 (fr) * 1991-10-11 1993-04-14 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Dispositif pour détecter la tension des fils de chaîne dans un métier à tisser
EP0547003A1 (fr) * 1991-12-13 1993-06-16 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Système pour la détection de tension de fils de trame dans un métier à tisser
JPH0742046A (ja) * 1993-07-26 1995-02-10 Toyota Autom Loom Works Ltd 織機における経糸張力検出装置
JPH11125317A (ja) * 1997-10-23 1999-05-11 Tsudakoma Corp 偏心駆動装置と、それを使用する織機のイージング装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB918817A (en) * 1960-05-11 1963-02-20 Sulzer Ag Looms
EP0527705A1 (fr) * 1991-08-12 1993-02-17 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Procédé et dispositif pour détecter la tension des fils de chaîne dans un métier à tisser
EP0537111A1 (fr) * 1991-10-11 1993-04-14 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Dispositif pour détecter la tension des fils de chaîne dans un métier à tisser
EP0547003A1 (fr) * 1991-12-13 1993-06-16 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Système pour la détection de tension de fils de trame dans un métier à tisser
JPH0742046A (ja) * 1993-07-26 1995-02-10 Toyota Autom Loom Works Ltd 織機における経糸張力検出装置
JPH11125317A (ja) * 1997-10-23 1999-05-11 Tsudakoma Corp 偏心駆動装置と、それを使用する織機のイージング装置

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 1995, no. 05, 30 June 1995 (1995-06-30) & JP 07 042046 A (TOYOTA AUTOM LOOM WORKS LTD), 10 February 1995 (1995-02-10) *
PATENT ABSTRACTS OF JAPAN vol. 1999, no. 10, 31 August 1999 (1999-08-31) & JP 11 125317 A (TSUDAKOMA CORP), 11 May 1999 (1999-05-11) *

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1878821A1 (fr) * 2006-07-11 2008-01-16 Tsudakoma Kogyo Kabushiki Kaisha Dispositif de soutien de cylindre d'un métier à tisser
EP2184390A1 (fr) * 2008-11-10 2010-05-12 Tsudakoma Kogyo Kabushiki Kaisha Dispositif de déroulage de fils de chaîne d'un métier à tisser utilisant un mécanisme positive de support pour le porte-fils
EP2937451A1 (fr) * 2014-04-24 2015-10-28 Tsudakoma Kogyo Kabushiki Kaisha Dispositif de rétraction de rouleau de relâchement pour métier à tisser
WO2018073386A1 (fr) * 2016-10-20 2018-04-26 Lindauer Dornier Gesellschaft Mit Beschränkter Haftung Dispositif de mesure de la tension de chaine dans une machine à tisser et machine a tisser équipé d'un tel dispositif
CN108584508A (zh) * 2018-05-18 2018-09-28 常州市新创智能科技有限公司 在线展纤用缓冲恒张力装置及其使用方法
CN115029841A (zh) * 2022-07-06 2022-09-09 天津工业大学 一种织造间隔织物特种织机送经系统的张力施加与检测装置
CN115029841B (zh) * 2022-07-06 2024-02-20 天津工业大学 一种织造间隔织物特种织机送经系统的张力施加与检测装置

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Publication number Publication date
EP1544338A3 (fr) 2006-04-05
CN1306088C (zh) 2007-03-21
CN1523147A (zh) 2004-08-25
JP2004250817A (ja) 2004-09-09

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