US20070137719A1 - Shaft drive for a power loom - Google Patents

Shaft drive for a power loom Download PDF

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Publication number
US20070137719A1
US20070137719A1 US11/639,199 US63919906A US2007137719A1 US 20070137719 A1 US20070137719 A1 US 20070137719A1 US 63919906 A US63919906 A US 63919906A US 2007137719 A1 US2007137719 A1 US 2007137719A1
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US
United States
Prior art keywords
shaft
drive according
shaft drive
movement
heddle
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
US11/639,199
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English (en)
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
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Groz Beckert KG
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 Groz Beckert KG filed Critical Groz Beckert KG
Assigned to GROZ-BECKERT KG reassignment GROZ-BECKERT KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: POHL, GERHARD
Publication of US20070137719A1 publication Critical patent/US20070137719A1/en
Abandoned 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 power loom, provided with one or several heddle shafts.
  • Power looms are generally provided with several heddle shafts in the form of rectangular, vertically positioned frames. These heddle shafts accommodate heddles for guiding the on the whole horizontally extending warp threads, so as to move them vertically up and down for the shed forming.
  • the heddle shafts normally execute an up and down swinging movement, generated by a so-called shaft drive and/or a heddle machine.
  • the shaft drive is a gear for converting the rotational driving movement to a back and forth movement, wherein the shaft essentially follows a sinusoidal function.
  • document DE 69702039 T2 discloses a shaft drive provided with a coupling device for triggering an up and down movement of the shaft as needed, wherein means are provided for reducing the otherwise occurring jolt during the engagement and disengagement of the coupling device.
  • Document DE 103 43 377 B3 discloses a shaft drive which can be optionally activated or deactivated, wherein the heddle shaft executes a swinging movement while the drive is deactivated, in one of its dead center positions. With this measure, the acceleration forces acting upon the heddle shaft are minimized.
  • Document DE 195 38 018 A1 furthermore discloses a shaft drive with modulation gear, which functions to delay the dwell time for the heddle shafts in the extreme stroke positions (dead center positions). In particular for wide textile width, this is designed to increase the shed standstill angle for the weft yarn intake, relative to the drive shaft rotation, thereby keeping the shed open for a longer period of time.
  • a modulation gear of this type is expensive.
  • the shaft drive according to the invention is provided with a drive assembly, consisting of drive shaft, a power take-off, and a gear mechanism that is arranged in-between.
  • the gear mechanism comprises an eccentric toothed gearing with a non-constant transmission ratio. The transmission ratio depends on the angular position of the drive shaft.
  • the eccentric toothed gearing preferably contains at least two toothed gears with non-constant radius, wherein these toothed gears are in a state of constant engagement. Each uniform rotation of the input shaft thus causes a non-uniform rotation of the following shaft that is driven by the eccentric toothed gearing.
  • the eccentric toothed gearing thereby generates a modulation of the rotational speed, wherein the modulation interval is set for one input shaft rotation.
  • the generated rotational speed modulation is furthermore predetermined as a result of the shape of the gears of the eccentric toothed gearing. In any case, it cannot be further influenced at this location of the drive assembly.
  • the eccentric toothed gearing represents a simple and cost-effective solution for achieving a heddle shaft movement that deviates considerably from the sinusoidal shape, in particular if the heddle shaft dwells for a longer period in the upper or lower extreme position (dead center position) than is the case for the approximately sinusoidal movement and must travel faster through the transitional region between the upper and lower dead center position than would be the case for a sinusoidal movement.
  • the eccentric toothed gearing is thus capable of transmitting considerable torque, while the structural size and the material use are low. Thanks to modem production methods (CNC production), an eccentric toothed gearing can be produced in series and cost-effectively.
  • a polynomial to the seventh power is selected as the law of motion for the shaft, at least for one preferred embodiment, wherein the torque increase during the introduction and completion of the movement is soft.
  • this shaft drive is suitable for continuously operating heddle shafts (eccentric machines) as well as for heddle shafts that must be started and stopped (heddle machines), for example, for generating complicated weaving patterns.
  • the gearing is provided with a coupling device, which in one operating position transmits the driving movement without problem and, in a second operating position, interrupts the transmission of the movement.
  • a coupling device By extending the dwell time for the shaft in the extreme stroke positions, a longer time interval and a larger angle region is provided there for engaging and disengaging the coupling device, wherein the engaging and disengaging occurs essentially without load and with a minimum torque as well as minimum rotational speed for the coupling elements. Load jolts and the coupling load are reduced and/or minimized.
  • the coupling arrangement of one preferred embodiment permits a pendulum movement of the power take-off, or generates such a movement, in case of an interruption of the drive movement.
  • the pendulum movement on the one hand can be used to minimize the accelerations of the heddle shaft and, on the other hand, to create synchronous phases in which the coupling can softly engage or disengage.
  • the coupling device for the preferred embodiment is installed between the eccentric toothed gearing and the power take-off.
  • the eccentric toothed gearing can either be a component of a standard shaft drive or can be embodied as supplementary gear. In the latter case, it is advantageous that existing shaft drives can still be used and that a single eccentric toothed gearing is sufficient to generate a modulated rotational movement for all power take-offs of the heddle machine. In individual cases, it may make sense to provide two or more eccentric toothed gearings, which generate different output movements at their output shafts. With weaving looms having eccentric cam plates, these different output movements can be used for directly operating the eccentric cam plates. With heddle machines, these different output movements can be used to drive the coupling devices.
  • the eccentric toothed gearing is preferably provided with spur wheels having a whole number ratio of the teeth, relative to each other.
  • the number of teeth on the toothed gears is the same.
  • a transmission ratio of 1:1 is obtained on the whole, meaning on the average, wherein this transmission ratio is above or below one at each rotational angle, in dependence on the respective rotational position of the toothed gears relative to each other.
  • the toothed gears of one simple exemplary embodiment are elliptical in shape, wherein toothed gears of this type can be slightly counterbalanced and increase and/or reduce the transmission ratio twice during one rotation of the input shaft.
  • a connected eccentric cam plate for the power take-off of the shaft drive can thus be delayed in both extreme positions. With this measure, the angle at which the shed is at a standstill can be increased, meaning more time is available for inserting the weft yarn into the shed.
  • FIG. 1 is a schematic total view of a heddle shaft and a shaft drive
  • FIG. 2 shows the details of the heddle machine and heddle shafts, in a view from above;
  • FIG. 3 illustrates the shaft drive according to FIGS. 1 and 2 in a schematic block diagram
  • FIG. 4 is a schematic representation of an eccentric toothed gearing for the shaft drive according to FIG. 3 ;
  • FIG. 5 is a basic representation of a coupling device for the shaft drive according to FIG. 3 ;
  • FIG. 6 is a diagram illustrating the shaft stroke in dependence on the angle of rotation for the drive shaft.
  • FIG. 1 illustrates a heddle shaft 1 with thereto assigned heddle machine ore dobby 2 , which drives the shaft via a rod assembly, embodied as lever gear 3 .
  • FIG. 2 shows that additional heddle shafts 1 a , 1 b , etc. are provided parallel to the heddle shaft 1 , wherein these shafts are also driven by the heddle machine 2 . Insofar, this arrangement is a traditional arrangement.
  • the heddle shafts, which function to drive heddles 4 up and down as indicated by arrow 5 are moved up and down by the lever gear 3 .
  • the swinging movement (arrow 7 ), executed by a rocker 6 functioning as power take-off for the heddle machine 2 is converted by the lever gear 3 into the vertically directed shaft movement with the aid of a steering gear 8 , an angle lever 9 , 10 , and a connecting rod 11 .
  • the heddle machine 2 is provided with rockers 6 a , 6 b as power take-off for driving the additional heddle shafts 1 a , 1 b .
  • rockers are driven by means of a shaft 13 , via coupling devices 12 , 12 a , and 12 b .
  • the shaft 13 is stimulated to execute a non-uniform rotation, meaning a rotation with modulated angle speed, by an eccentric toothed gearing 14 .
  • the eccentric toothed gearing 14 is preferably driven with uniform rotations via a drive shaft 15 by a drive source 16 in the form of an electric motor, which can be a component of a weaving loom.
  • the eccentric toothed gearing 14 together with the coupling devices 12 , 12 a , 12 b forms a gear mechanism 17 , for which the rockers 6 , 6 a , 6 b form the power take-off.
  • the drive assembly formed in this way is again shown schematically in FIG. 3 for a single power take-off.
  • the coupling device 12 in this case is optional and is used for driving an eccentric shaft 18 with eccentric cam plate 19 , which drives the rocker 6 , not shown in further detail herein, by means of a connecting rod 20 .
  • the coupling device 12 is provided with at least one input in the form of an input shaft 22 .
  • the input shaft 22 executes a rotation with modulated speed, wherein the directional sense remains unchanged.
  • the coupling device 12 in one switching position can transmit this rotational movement to the eccentric shaft 18 .
  • the coupling device with several input shafts 22 , 21 . All input shafts can respectively be coupled to the eccentric toothed gearing 14 and can respectively be driven with the modulated speed (see FIG. 3 ). It is furthermore possible to control the input shaft 21 directly with the aid of the drive source 16 and via the drive shaft 15 .
  • the input shaft 22 preferably executes a non-uniform rotation, without change in direction. This rotational movement is converted to a back and forth rotating movement with the aid of additional means, not shown herein, such as an eccentric cam plate or cams/cam followers. In the switching and/or coupling position shown in FIG. 3 , the coupling device 12 transmits this rotational pendulum movement to the eccentric shaft 18 .
  • the input shaft 22 and the input shaft 21 are driven by means of the eccentric toothed gearing 14 , which comprises two spur wheels 23 , 24 that are attached in the center of the respective shafts and have a non-constant radius.
  • the spur wheels 23 , 24 are illustrated in FIG. 4 .
  • they are approximately elliptical in shape and are embodied such that they constantly mesh. They have identical numbers of teeth and thus define an average transmission ratio of 1:1.
  • the uniform rotation of the spur wheel 23 forces a continuously accelerated and delayed rotation of the spur wheel 24 .
  • the spur wheel 24 For each rotation, the spur wheel 24 is accelerated twice and delayed twice, wherein the acceleration and delay in both acceleration/delay phases is identical if the toothed gear is embodied symmetrical.
  • the spur wheels 23 , 24 can also be embodied more or less asymmetrical in order to generate two different, spaced apart movement modulations during a complete rotation, at the 180° distance.
  • the drive shaft 15 In order to equalize the rotation of the drive shaft 15 , it is preferably provided with a balancing weight 25 , so that the load fluctuations are mostly kept away from the drive source 16 and the drive source 16 has a uniform load.
  • FIG. 5 illustrates a possible embodiment for the coupling device 12 .
  • the coupling device 12 is provided with a cam 26 that is driven by the input shaft 21 and forms a pendulum drive 28 together with the cam follower 27 .
  • the cam follower 27 is connected to a coupling disk 29 , which performs a back and forth rotating movement.
  • an additional coupling disk 30 which is arranged concentric to the coupling disk 29 , executes a rotational movement that is preset by the input shaft 22 .
  • the coupling disk 30 is fixedly connected to the input shaft 22 .
  • the eccentric shaft 18 is connected to a disk 31 that forms the power take-off for the coupling device 12 .
  • the disk 31 is provided with a pawl 32 , which alternatively engages in the coupling disk 29 or the coupling disk 30 with the aid of the switching levers 33 , 34 , positioned swinging, and are moved via a selection finger 35 on an activation lever 36 .
  • This lever oscillates back and forth with the aid of electromagnets 37 , 38 , thereby activating either the switching lever 33 or the switching lever 34 .
  • Springs 39 , 40 pre-stress the switching levers 33 , 34 in the desired direction.
  • the heddle machine 2 described so far operates as follows:
  • the input shaft 22 clearly rotates slower than the drive shaft 15 , whereas it rotates noticeably faster at other times.
  • the heddle shaft 1 consequently remains in the upper and lower reversing regions over a longer rotational angle of the drive shaft 15 , thereby increasing the time for the weft yarn insertion. This is particularly important for wide weaving looms and high machine speeds.
  • the heddle shaft 1 combines a traditional heddle machine 2 with an eccentric toothed gearing 14 for purposely extending the dwell times for the heddle shaft 1 in the upper and lower reversing region and for reducing any accelerations that occur. This permits an increase in the weaving speed and/or the weaving widths.
  • a coupling device 12 is additionally provided, which is intended to provide the heddle shaft 1 during the idle periods, meaning the period when no sheds are formed, with a pendulum movement having a stroke of a few millimeters to several centimeters.

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  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Looms (AREA)
  • Transmission Devices (AREA)
US11/639,199 2005-12-15 2006-12-15 Shaft drive for a power loom Abandoned US20070137719A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005059911A DE102005059911B3 (de) 2005-12-15 2005-12-15 Schaftantrieb für eine Webmaschine
DE102005059911.7 2005-12-15

Publications (1)

Publication Number Publication Date
US20070137719A1 true US20070137719A1 (en) 2007-06-21

Family

ID=37670261

Family Applications (1)

Application Number Title Priority Date Filing Date
US11/639,199 Abandoned US20070137719A1 (en) 2005-12-15 2006-12-15 Shaft drive for a power loom

Country Status (4)

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

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050194055A1 (en) * 2004-03-02 2005-09-08 Promatech S.P.A. Weaving loom with motor-driven frames
US20090014085A1 (en) * 2007-07-12 2009-01-15 Groz-Beckert Kg Control Device For a Shift Clutch of a dobby
US20100101679A1 (en) * 2008-10-24 2010-04-29 Groz-Beckert Kg Spreader with clamping and ventilating devices
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

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109402827B (zh) * 2017-08-15 2020-07-14 郑川田 可形成双织口的多臂机

Citations (35)

* 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
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
US3168166A (en) * 1962-12-04 1965-02-02 American Brake Shoe Co Railroad car retarders
US3228427A (en) * 1961-05-05 1966-01-11 Rueti Ag Maschf Dobbies
US3407678A (en) * 1966-12-19 1968-10-29 Ncr Co Mechanism for producing rotary output motion with harmonic displacement characteristics
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
US3871419A (en) * 1971-12-10 1975-03-18 Sulzer Ag Deflecting beam for warp threads in a weaving machine
US3889720A (en) * 1973-01-25 1975-06-17 Saurer Ag Adolph Heald machine
US4041986A (en) * 1975-08-25 1977-08-16 Elitex Koncern Textilniho Strojirenstvi Device for forming a shed in a weaving machine
US4151866A (en) * 1977-10-19 1979-05-01 Gloor Wilbur T Loom for the weaving of two and/or three thread fabrics
US4314588A (en) * 1979-02-15 1982-02-09 Textilma Ag Loom
US4444225A (en) * 1981-10-29 1984-04-24 S.A. Des Etablissements Staubli Rotating dobbies
US4461325A (en) * 1981-11-05 1984-07-24 S.A. Des Etablissements Staubli Electromagnetic device for controlling dobbies and other weaving systems
US4544000A (en) * 1983-02-07 1985-10-01 S. A. Des Establissements Staubli (France) Synchronized rotating dobby for weaving looms
US4643231A (en) * 1984-04-18 1987-02-17 W. Schlafhorst & Co. Rotary dobby
US4651784A (en) * 1983-06-27 1987-03-24 Elitex, Koncern Textilniho Plain weave shedding mechanism
US4858655A (en) * 1986-03-26 1989-08-22 S.A. Des Etablissements Staubli (France) Rotating dobby for weaving looms
US4905738A (en) * 1987-01-05 1990-03-06 Ernst Kleiner Control for a rotary dobby heald frame connecting rod
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
US5908050A (en) * 1996-12-31 1999-06-01 Staubli Faverges Actuator spacing for pivoting arms of a rotary dobby
US5918645A (en) * 1996-12-31 1999-07-06 Staubli Faverges Catch configurations for the pivot arms of a rotary dobby
US6092560A (en) * 1997-07-30 2000-07-25 Staeubli Gmbh Shaft driving device for heald shafts
US6135163A (en) * 1998-12-07 2000-10-24 Lindauer Dornier Gesellschaft Mbh Method and apparatus for compensating warp thread tension or elongation variations during loom shedding
US20050056334A1 (en) * 2003-09-17 2005-03-17 Groz-Beckert Kg Shaft drive system for power loom shafts
US6938647B2 (en) * 2002-07-16 2005-09-06 Staubli Faverges Rotating dobby for weaving loom and weaving loom equipped with such a dobby
US7017617B2 (en) * 2002-02-07 2006-03-28 Staubli Lyon Device for shed formation and Jacquard loom comprising same
US7032624B2 (en) * 2003-09-10 2006-04-25 Groz-Beckert Kg Low-vibration shedding system

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29500594U1 (de) * 1995-01-16 1995-02-23 Stäubli & Trumpelt GmbH, 95448 Bayreuth Modulationsgetriebe für eine Rotationsschaftmaschine in einer Webmaschine

Patent Citations (36)

* 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
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
US3228427A (en) * 1961-05-05 1966-01-11 Rueti Ag Maschf Dobbies
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
US3871419A (en) * 1971-12-10 1975-03-18 Sulzer Ag Deflecting beam for warp threads in a weaving machine
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
US3889720A (en) * 1973-01-25 1975-06-17 Saurer Ag Adolph Heald machine
US4041986A (en) * 1975-08-25 1977-08-16 Elitex Koncern Textilniho Strojirenstvi Device for forming a shed in a weaving machine
US4151866A (en) * 1977-10-19 1979-05-01 Gloor Wilbur T Loom for the weaving of two and/or three thread fabrics
US4314588A (en) * 1979-02-15 1982-02-09 Textilma Ag Loom
US4444225A (en) * 1981-10-29 1984-04-24 S.A. Des Etablissements Staubli Rotating dobbies
US4461325A (en) * 1981-11-05 1984-07-24 S.A. Des Etablissements Staubli Electromagnetic device for controlling dobbies and other weaving systems
US4544000A (en) * 1983-02-07 1985-10-01 S. A. Des Establissements Staubli (France) Synchronized rotating dobby for weaving looms
US4651784A (en) * 1983-06-27 1987-03-24 Elitex, Koncern Textilniho Plain weave shedding mechanism
US4643231A (en) * 1984-04-18 1987-02-17 W. Schlafhorst & Co. Rotary dobby
US4858655A (en) * 1986-03-26 1989-08-22 S.A. Des Etablissements Staubli (France) Rotating dobby for weaving looms
US4905738A (en) * 1987-01-05 1990-03-06 Ernst Kleiner Control for a rotary dobby heald frame connecting rod
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
US5908050A (en) * 1996-12-31 1999-06-01 Staubli Faverges Actuator spacing for pivoting arms of a rotary dobby
US5918645A (en) * 1996-12-31 1999-07-06 Staubli Faverges Catch configurations for the pivot arms of a rotary dobby
US6092560A (en) * 1997-07-30 2000-07-25 Staeubli Gmbh Shaft driving device for heald shafts
US6135163A (en) * 1998-12-07 2000-10-24 Lindauer Dornier Gesellschaft Mbh Method and apparatus for compensating warp thread tension or elongation variations during loom shedding
US7017617B2 (en) * 2002-02-07 2006-03-28 Staubli Lyon Device for shed formation and Jacquard loom comprising same
US6938647B2 (en) * 2002-07-16 2005-09-06 Staubli Faverges Rotating dobby for weaving loom and weaving loom equipped with such a dobby
US7032624B2 (en) * 2003-09-10 2006-04-25 Groz-Beckert Kg Low-vibration shedding system
US20050056334A1 (en) * 2003-09-17 2005-03-17 Groz-Beckert Kg Shaft drive system for power loom shafts
US7140399B2 (en) * 2003-09-17 2006-11-28 Groz-Beckert Kg Shaft drive system for power loom shafts

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050194055A1 (en) * 2004-03-02 2005-09-08 Promatech S.P.A. Weaving loom with motor-driven frames
US7493919B2 (en) * 2004-03-02 2009-02-24 Promatech S.P.A. Weaving loom with motor-driven frames
US20090014085A1 (en) * 2007-07-12 2009-01-15 Groz-Beckert Kg Control Device For a Shift Clutch of a dobby
US7637290B2 (en) * 2007-07-12 2009-12-29 Groz-Beckert Kg Control device for a shift clutch of a dobby
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
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

Also Published As

Publication number Publication date
EP1798320A2 (fr) 2007-06-20
EP1798320B1 (fr) 2011-04-06
JP2007162205A (ja) 2007-06-28
EP1798320A3 (fr) 2008-07-30
DE102005059911B3 (de) 2007-02-08
DE502006009243D1 (de) 2011-05-19

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