EP1798320A2 - Système d'entraînement de lames pour métier à tisser - Google Patents

Système d'entraînement de lames pour métier à tisser Download PDF

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Publication number
EP1798320A2
EP1798320A2 EP06023500A EP06023500A EP1798320A2 EP 1798320 A2 EP1798320 A2 EP 1798320A2 EP 06023500 A EP06023500 A EP 06023500A EP 06023500 A EP06023500 A EP 06023500A EP 1798320 A2 EP1798320 A2 EP 1798320A2
Authority
EP
European Patent Office
Prior art keywords
shaft
drive according
shaft drive
rotation
eccentric
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
EP06023500A
Other languages
German (de)
English (en)
Other versions
EP1798320A3 (fr
EP1798320B1 (fr
Inventor
Gerhard Pohl
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.)
Groz Beckert KG
Original Assignee
Groz Beckert KG
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Publication date
Application filed by Groz Beckert KG filed Critical Groz Beckert KG
Publication of EP1798320A2 publication Critical patent/EP1798320A2/fr
Publication of EP1798320A3 publication Critical patent/EP1798320A3/fr
Application granted granted Critical
Publication of EP1798320B1 publication Critical patent/EP1798320B1/fr
Not-in-force legal-status Critical Current
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Classifications

    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03D—WOVEN FABRICS; METHODS OF WEAVING; LOOMS
    • D03D51/00—Driving, starting, or stopping arrangements; Automatic stop motions
    • D03D51/16—Driving, starting, or stopping arrangements; Automatic stop motions for varying speed cyclically
    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03C—SHEDDING MECHANISMS; PATTERN CARDS OR CHAINS; PUNCHING OF CARDS; DESIGNING PATTERNS
    • D03C1/00—Dobbies
    • D03C1/14—Features common to dobbies of different types
    • D03C1/146—Independent drive motor
    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03C—SHEDDING MECHANISMS; PATTERN CARDS OR CHAINS; PUNCHING OF CARDS; DESIGNING PATTERNS
    • D03C1/00—Dobbies
    • D03C1/14—Features common to dobbies of different types
    • D03C1/148—Eccentrics
    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03C—SHEDDING MECHANISMS; PATTERN CARDS OR CHAINS; PUNCHING OF CARDS; DESIGNING PATTERNS
    • D03C13/00—Shedding mechanisms not otherwise provided for

Definitions

  • the invention relates to a shaft drive for a loom with one or more heddles.
  • Weaving machines are usually provided with several WebMften, which are formed by rectangular, vertically standing frame.
  • the healds strands are held, with which by and large horizontally extending warp threads are guided and vertically moved for shedding.
  • the heald frames perform a swinging motion up and down, which is generated by a so-called shaft drive or a dobby.
  • the shaft drive is a transmission with the from a rotating drive movement, the reciprocating motion is derived from the shaft, which then essentially follows a sine function.
  • the DE 69702039 T2 a shaft drive having a coupling device to be able to trigger an upward or downward movement of the shaft if necessary.
  • a coupling device to be able to trigger an upward or downward movement of the shaft if necessary.
  • means which serve to reduce the otherwise resulting shock when engaging and disengaging the clutch.
  • the DE 103 43 377 B3 discloses a shaft drive which can be selectively activated and deactivated, wherein the heald performs vibration in one of its dead spots when the drive is deactivated. With this measure, the forces acting on the weaving shaft acceleration forces are minimized.
  • the DE 195 38 018 A1 a shaft drive with a modulation gear. This serves to delay the holding time of the heald frames in their extreme positions (dead spots). This is to be increased in particular for wide tissue related to the rotation of the drive shaft standstill angle for weft insertion. This should make the shed open longer.
  • Such a modulation gear is expensive. It also shows that the cams and the modulation gear take up a relatively large overall volume. On this basis, it is an object of the invention to provide an improved shaft drive.
  • the non-circular gear provides a simple and inexpensive solution to achieve a significantly different from the sinusoid Hedgehog movement, especially when the heald longer than an approximately inusterrorism in upper or lower extreme position (dead center) dwell and the transition between upper and lower dead center faster than at to rush through a sinusoidal movement.
  • the non-circular gear is able to transmit significant torque, the size and material usage is low. Thanks to modern production methods (CNC production), a non-circular gear unit in mass production is cost-effective.
  • CNC production modern production methods
  • a non-circular gear unit in mass production is cost-effective.
  • the torque increases before and after the extreme-lift positions can be minimized.
  • there is chosen as a law of motion for the shaft at least in a preferred embodiment, a polynomial of the seventh degree. The torque increase when entering and exiting the movement is gentle.
  • this shaft drive is suitable both for permanently operated heald frames (eccentric machines) and for heald frames which are to be switched on and off (dobby machines), for example in order to produce complicated weave bindings.
  • the transmission includes a coupling device which transmits the drive movement unhindered in an operating position and interrupts the transmission of motion in a second operating position.
  • the clutch assembly allows for the interruption of the drive movement to a pendulum motion of the output or generates such.
  • the pendulum motion can be used on the one hand to minimize the acceleration of the heald and on the other hand to create synchronization phases in which the clutch can soft on and disengage.
  • the coupling means is provided between the non-circular gear transmission and the output.
  • the non-circular gear can be formed both part of a conventional shaft drive and as an auxiliary gear. In the latter case is advantageous that existing shaft drives can continue to be used and that a single non-circular gear is sufficient to produce a modulated rotational movement for all outputs of the dobby.
  • the non-circular gear has preferably spur gears whose numbers of teeth are in an integer ratio.
  • the gears have a matching number of teeth. It thus results in total, i. on average, a transmission ratio of 1: 1, wherein this can be in relation to the respective rotational position of the gears to each other in each rotational angle above or below one.
  • the gears have elliptical shape. Such gears can be easily balanced and increase or reduce the transmission ratio in one revolution of the input shaft two times. A connected eccentric, which moves the output of the shaft drive, can thus be delayed in both extreme positions. With this measure, the standstill angle can be increased, i. Extend the time during which the tray is open for weft insertion.
  • FIG. 1 shows a weaving shank 1 is illustrated, which is associated with a dobby 2 and the latter via a linkage, which is designed as a lever mechanism 3, drives.
  • FIG. 2 further heald frames 1a, 1b, etc., which are likewise driven by the dobby 2, are provided parallel to the heald 1.
  • the arrangement is so far made in a conventional manner.
  • the heddle shafts which serve to move strands 4 up and down as indicated by an arrow 5 are moved up and down by the lever mechanism 3.
  • the swinging movement (arrow 7), which serves as the output rocker 6 of the dobby 2 is converted by the lever mechanism 3 into the vertically directed shaft movement, for which purpose a link 8, angle lever 9, 10 and a connecting rod 11 are used.
  • the dobby 2 has, as an output for driving the other heald frames 1a, 1b, wings 6a, 6b which are driven by a shaft 13 via coupling devices 12, 12a, 12b.
  • the shaft 13 is rotated from a non-circular gear 14 to a non-uniform rotation, i.e. offset a rotation with modulated angular velocity.
  • the non-circular gear 14 is preferably driven via a drive shaft 15 of a drive source 16 formed by an electric motor, which may be part of a weaving machine, preferably uniformly rotating.
  • the non-circular gear 14 forms, together with the coupling means 12, 12a, 12b, a gear 17 whose output is formed by the wings 6, 6a, 6b.
  • the drive train thus constructed is again schematically illustrated in FIG. 3 for a single output.
  • the coupling device 12 is optional. About them an eccentric shaft 18 is driven by an eccentric 19, the via a connecting rod 20, the not illustrated swing arm 6 drives.
  • the coupling device 12 has at least one input in the form of an input shaft 22.
  • the input shaft 22 performs a rotation with modulated speed, but not changing sense of direction.
  • the coupling device 12 can pass this rotational movement to the eccentric shaft 18 in a switching position.
  • the coupling device has a plurality of input shafts 22, 21.
  • all the input shafts can each be coupled to the non-circular gear 14 and each driven at the modulated speed (see Figure 3).
  • the input shaft 21 is directly controlled by the drive source 16 via the drive shaft 15.
  • the input shaft 22 preferably rotates non-uniformly, without reversing direction.
  • eccentric or curves / cam follower means this rotational movement is converted into a reciprocating motion.
  • the coupling device 12 is this rotary pendulum movement to the eccentric shaft 18 on.
  • the input shaft 22 and the input shaft 21 are driven via the non-circular gear 14.
  • the spur gears 23, 24 are illustrated in FIG. In the present embodiment, they are approximately elliptical, wherein they are formed so that they are in constant meshing engagement with each other. They show the same number of teeth and thus lay an average Gear ratio of 1: 1 fixed.
  • the uniform rotation of the spur gear 23 forces a continuously accelerated and decelerated rotation of the spur gear 24. Per revolution of the spur gear 24 it is accelerated twice and retarded twice, with the acceleration and deceleration in symmetric gear formation in both acceleration / deceleration phases identical.
  • the spur gears 23, 24 may also be more or less asymmetrical in order to produce two different motion modulations at a full rotation in the 180 ° distance.
  • this is preferably provided with a flywheel 25, so that load fluctuations largely kept away from the drive source 16 and the drive source 16 is uniformly loaded.
  • FIG. 5 illustrates one possible embodiment of the coupling device 12.
  • the clutch device 12 has a driven by the input shaft 21 cam 26 which forms a pendulum drive 28 with a cam follower 27.
  • the cam follower 27 is connected to a clutch plate 29 which performs a reciprocating motion.
  • a further, to the clutch plate 29 concentrically arranged clutch disc 30 performs a predetermined by the input shaft 22 rotational movement.
  • the clutch disc 30 is fixedly connected to the input shaft 22.
  • the eccentric shaft 18 is connected to a disc 31, which is the Output of the coupling device 12 forms.
  • the disc 31 carries a pawl 32 which is alternatively to be engaged with the clutch disc 29 or with the clutch disc 30.
  • Serve switching lever 33, 34 which are pivotally mounted and are moved by a selection finger 35 of an actuating lever 36. This is pivoted by electromagnets 37, 38 for activating either the shift lever 33 or the shift lever 34 back and forth. Springs 39, 40 bias the shift levers 33, 34 in the desired direction.
  • the coupling device 12 can be switched in the upper and in the lower reversing area to shuttle mode, to which the coupling device 12 is used.
  • This process is detailed in the DE 103 43 377 B3 described, which is hereby incorporated by reference.
  • the heald 1 can remain in pendulum mode as long as desired and can be reactivated without reducing the speed of the drive shaft 15, ie switched on.
  • the switching of the pawl 32 then takes place in a moment in which the clutch plates 29, 30 run largely synchronously for a short time.
  • the dobby 1 combines a conventional dobby 2 with a non-circular gear 14 for selectively extending the retention times of the heald 1 in the upper or lower reverse region and for reducing occurring accelerations. This allows an increase in the web speed or the web widths.
  • a coupling device 12 is additionally provided, which gives the heald 1 in rest periods, ie when no shedding is to be made, a pendulum movement with a stroke of a few millimeters to centimeters. By the swinging movement of the heald 1 in the upper or lower reverse region, the acceleration loads of the heald 1 can be further reduced.

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  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Looms (AREA)
  • Transmission Devices (AREA)
EP06023500A 2005-12-15 2006-11-11 Système d'entraînement de lames pour métier à tisser Not-in-force EP1798320B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005059911A DE102005059911B3 (de) 2005-12-15 2005-12-15 Schaftantrieb für eine Webmaschine

Publications (3)

Publication Number Publication Date
EP1798320A2 true EP1798320A2 (fr) 2007-06-20
EP1798320A3 EP1798320A3 (fr) 2008-07-30
EP1798320B1 EP1798320B1 (fr) 2011-04-06

Family

ID=37670261

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06023500A Not-in-force EP1798320B1 (fr) 2005-12-15 2006-11-11 Système d'entraînement de lames pour métier à tisser

Country Status (4)

Country Link
US (1) US20070137719A1 (fr)
EP (1) EP1798320B1 (fr)
JP (1) JP2007162205A (fr)
DE (2) DE102005059911B3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109402827A (zh) * 2017-08-15 2019-03-01 郑川田 可形成双织口的多臂机

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ATE335874T1 (de) * 2004-03-02 2006-09-15 Promatech Spa Webmaschine mit motorgetriebenen webschäften
EP2014805B1 (fr) * 2007-07-12 2011-12-14 Groz-Beckert KG Dispositif de commande pour un embrayage principal d'une ratière
EP2180092B1 (fr) * 2008-10-24 2012-11-21 Groz-Beckert KG Tendeur de largeur doté d'un dispositif de serrage et d'ouvrir
CN105568467A (zh) * 2015-12-15 2016-05-11 浙江理工大学 一种非圆齿轮空间球面4r开口机构
CN117248313B (zh) * 2023-10-16 2025-09-30 嵊州市三成纺织设备有限公司 一种提花机用于驱动摆动轴的传动装置

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US495453A (en) 1893-04-11 Pattern mechanism for looms
US770495A (en) 1904-09-20 Trading under the firm-name of crompton
US1651120A (en) 1927-03-21 1927-11-29 Crompton & Knowles Loom Works Clutch for loom pattern mechanisms
US1923048A (en) 1931-02-18 1933-08-15 John G Bentley Dobby drive
US2089069A (en) 1936-06-27 1937-08-03 William J Oothout Harness operating mechanism for looms
DE19538018A1 (de) 1995-01-16 1996-07-18 Staeubli Gmbh Modulationsgetriebe für eine Rotationsschaftmaschine in einer Webmaschine
DE69702039T2 (de) 1996-12-31 2000-09-14 Staubli Faverges, Faverges Rotationsschaftmaschine und Webmaschine mit einer solchen Schaftmaschine
DE10343377B3 (de) 2003-09-17 2005-04-28 Groz Beckert Kg Schaftantrieb für Webmaschinenschäfte

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US2282223A (en) * 1940-05-28 1942-05-05 Hamilton Wallace Loom
US2469200A (en) * 1946-09-11 1949-05-03 Matweeff Paul Harness motion for looms
CH392410A (de) * 1961-05-05 1965-05-15 Rueti Ag Maschf Schaftmaschine
US3168166A (en) * 1962-12-04 1965-02-02 American Brake Shoe Co Railroad car retarders
US3407678A (en) * 1966-12-19 1968-10-29 Ncr Co Mechanism for producing rotary output motion with harmonic displacement characteristics
BE792485A (fr) * 1971-12-10 1973-06-08 Sulzer Ag Barre de deviation des fils de chaine d'un metier a tisser
US3807460A (en) * 1972-10-12 1974-04-30 A Alexandr Heald motion for looms
US3865147A (en) * 1973-01-17 1975-02-11 Vyzk Vyvojovy Ustav Vseobe Mechanism for the return movement of heald shafts of a weaving loom
CH560262A5 (fr) * 1973-01-25 1975-03-27 Saurer Ag Adolph
CS179196B1 (en) * 1975-08-25 1977-10-31 Josef Resch Shedding mechanisms for weaving machines
US4151866A (en) * 1977-10-19 1979-05-01 Gloor Wilbur T Loom for the weaving of two and/or three thread fabrics
CH634613A5 (de) * 1979-02-15 1983-02-15 Textilma Ag Webmaschine mit schaeften und diesen zugeordneten hebeln.
FR2515702A1 (fr) * 1981-10-29 1983-05-06 Staubli Sa Ets Perfectionnements aux ratieres rotatives
FR2515703B1 (fr) * 1981-11-05 1983-12-09 Staubli Sa Ets
FR2540524B1 (fr) * 1983-02-07 1985-07-26 Staubli Sa Ets Ratiere rotative synchronisee pour metiers a tisser
CS239001B1 (en) * 1983-06-27 1985-12-16 Zdenek Rambousek Plain weave shed forming device
DE3414640A1 (de) * 1984-04-18 1985-10-24 W. Schlafhorst & Co, 4050 Mönchengladbach Rotations-schaftmaschine
FR2596425B1 (fr) * 1986-03-26 1988-05-20 Staubli Sa Ets Ratiere rotative pour machines a tisser
CH671782A5 (fr) * 1987-01-05 1989-09-29 Ernst Kleiner
US5069256A (en) * 1989-12-08 1991-12-03 Goodman Jr Robert M Loom harness system with spaced parallel rotating shafts
US5479963A (en) * 1994-11-30 1996-01-02 Cheng; Chuan-Tien Loom heald hook lifter
US5653268A (en) * 1995-01-16 1997-08-05 Staubli Gmbh Modulator mechanism for a rotary dobby in a loom
FR2757883B1 (fr) * 1996-12-31 1999-02-19 Staubli Sa Ets Ratiere rotative et metier a tisser equipe d'une telle ratiere
DE29713600U1 (de) * 1997-07-30 1997-09-18 Stäubli GmbH, 95448 Bayreuth Schaftantriebsvorrichtung
DE19915952A1 (de) * 1998-12-07 2000-10-12 Dornier Gmbh Lindauer Verbessertes Verfahren zur Kompensation der Längungs- oder Spannungsänderung in einer Webkette und Webmaschine zur Durchführung des Verfahrens
FR2835537B1 (fr) * 2002-02-07 2004-10-01 Staubli Lyon Dispositif de formation de la foule et metier a tisser jacquard incorporant un tel dispositif
FR2842538B1 (fr) * 2002-07-16 2004-10-29 Staubli Sa Ets Ratiere rotative pour metier a tisser, et metier a tisser equipe d'une telle ratiere
DE10341629B4 (de) * 2003-09-10 2007-04-12 Groz-Beckert Kg Vibrationsarmes Fachbildesystem

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US495453A (en) 1893-04-11 Pattern mechanism for looms
US770495A (en) 1904-09-20 Trading under the firm-name of crompton
US1651120A (en) 1927-03-21 1927-11-29 Crompton & Knowles Loom Works Clutch for loom pattern mechanisms
US1923048A (en) 1931-02-18 1933-08-15 John G Bentley Dobby drive
US2089069A (en) 1936-06-27 1937-08-03 William J Oothout Harness operating mechanism for looms
DE19538018A1 (de) 1995-01-16 1996-07-18 Staeubli Gmbh Modulationsgetriebe für eine Rotationsschaftmaschine in einer Webmaschine
DE69702039T2 (de) 1996-12-31 2000-09-14 Staubli Faverges, Faverges Rotationsschaftmaschine und Webmaschine mit einer solchen Schaftmaschine
DE10343377B3 (de) 2003-09-17 2005-04-28 Groz Beckert Kg Schaftantrieb für Webmaschinenschäfte

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109402827A (zh) * 2017-08-15 2019-03-01 郑川田 可形成双织口的多臂机

Also Published As

Publication number Publication date
EP1798320A3 (fr) 2008-07-30
JP2007162205A (ja) 2007-06-28
DE502006009243D1 (de) 2011-05-19
EP1798320B1 (fr) 2011-04-06
US20070137719A1 (en) 2007-06-21
DE102005059911B3 (de) 2007-02-08

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