EP1516947A2 - Système d'entraínement de lames pour machines à tisser - Google Patents

Système d'entraínement de lames pour machines à tisser Download PDF

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Publication number
EP1516947A2
EP1516947A2 EP04018093A EP04018093A EP1516947A2 EP 1516947 A2 EP1516947 A2 EP 1516947A2 EP 04018093 A EP04018093 A EP 04018093A EP 04018093 A EP04018093 A EP 04018093A EP 1516947 A2 EP1516947 A2 EP 1516947A2
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EP
European Patent Office
Prior art keywords
movement
shaft
input element
drive
shaft drive
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
EP04018093A
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German (de)
English (en)
Other versions
EP1516947B1 (fr
EP1516947A3 (fr
EP1516947B2 (fr
Inventor
Johannes Dr. Bruske
Bernhard Münster
Armin FÄLLER
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Groz Beckert KG
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Groz Beckert KG
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Publication date
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Application filed by Groz Beckert KG filed Critical Groz Beckert KG
Publication of EP1516947A2 publication Critical patent/EP1516947A2/fr
Publication of EP1516947A3 publication Critical patent/EP1516947A3/fr
Publication of EP1516947B1 publication Critical patent/EP1516947B1/fr
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    • 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
    • D03C13/02—Shedding mechanisms not otherwise provided for with independent drive motors
    • D03C13/025—Shedding mechanisms not otherwise provided for with independent drive motors with independent frame drives
    • 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
    • D03C1/144—Features common to dobbies of different types linking to the heald frame
    • 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
    • D—TEXTILES; PAPER
    • D03—WEAVING
    • D03C—SHEDDING MECHANISMS; PATTERN CARDS OR CHAINS; PUNCHING OF CARDS; DESIGNING PATTERNS
    • D03C9/00—Healds; Heald frames
    • D03C9/06—Heald frames
    • D03C9/0683—Arrangements or means for the linking to the drive system

Definitions

  • the invention relates to a shaft drive for at least a weave of a loom.
  • Such a dobby is for example from the DE 697 02 039 T2 known.
  • the between the eccentric and the driving shaft arranged latch switching mechanism is here for each shaft movement, i. for an upward movement of the shaft or for a downward movement of the shaft respectively switched on for half a shaft rotation.
  • Such Dobby machines are very flexible. However, such Dobby machines the working speed of eccentric machines do not reach.
  • the work of the pawl switching mechanisms is susceptible to wear. An increase in the working speed does not only lead to ratchet wear, but also to strand and shank breaks.
  • the shaft movement is now determined that neither a pure sinusoidally oscillating up and down Movement of the shaft still a swinging up and down movement with downtimes in the upper and lower reversal point is obtained. Rather, the drive does not enforce only during the movement phases, but now also during the resting phases of the shaft in which the shaft otherwise usually in the upper or lower reversal point rest, a continued movement of the same.
  • This measure opens up the possibility of maximum acceleration of the Shank to reduce.
  • the avoidance of acceleration jumps leads to a smooth running of the shafts, the even at high working speeds to no excessive Vibrational excitations.The limit for the working speed, occur in the shaft fractures and strand breaks, can thus very far to higher working speeds be moved.
  • the corresponding, from the shaft to be traversed motion curves, according to a first Embodiment of the invention, by means of freely programmable Drives are achieved, which move the shaft.
  • a the Drives assigned control device calls the drives during the movement phases a high speed off to the shaft as quickly as possible from the one reversing position into another reversal position. This process is for shedding necessary to warp threads from the warp thread level move up or down. approaches the shaft of its intended reversal position slows down the control device the output of the shaft drive, the e.g. formed by connecting rods, and leaves him then commute to the same when reaching the reverse position. ever after residence in the reverse position, the pendulum oscillation go through one or more maxima and minima (wave trains).
  • the pendulum movement in the resting phases has the advantage that the Shaft drive can specify shaft movements, the lower Have acceleration values.
  • the Shaft movement in the course of time in the transition from one Reversal into the other of a harmonic function (sinus or cosinus) and, in the reverse position, enters a time function over, at the beginning of which the acceleration is the same Value has the same as when leaving the curve branch of the transition movement.
  • the acceleration curve is thus continuous.
  • the movement curves also called "laws of motion" be
  • the movement curves for the transition of the shaft from a reversal position in the other, as well as for commuting within the reversal areas can in a simple embodiment in one Data storage to be stored.
  • the controller calls then the respective cams from the data memory on and controls the one or more motors of the shaft drive accordingly at.
  • the cams can also advance or be calculated in real time, with the calculation case by case depending on the respective given boundary conditions according to special Optimization criteria can be done.
  • optimization criteria For example, be that a minimum opening time must not be fallen below, that the maximum accelerations are to limit that acceleration jumps inadmissible are that the shaft speed is to be limited or that given a maximum acceleration a maximum operating speed is calculated.
  • the curves resulting from these optimization criteria can then be cached and for driving the shaft drive be applied.
  • the pendulum movement of the shaft in the upper and lower turning point area has the other Advantage that by the pendulum movement of the Webschaft the Warp threads can be somewhat relaxed, causing the weft stop can facilitate.
  • the shaft via a Coupling device optionally connected to a first drive be a constant between the two reversals oscillating motion generated, or with another drive, the pendulum about the upper or the lower reversal position Movement generated.
  • the switching is preferably carried out during existing synchronization phases.
  • the corresponding coupling can be a linear motion transmitting clutch.
  • the shaft drive according to the invention can according to another Embodiment one with a rotary drive device connected input shaft, which ultimately serves to drive a gear assembly, the back and forth generated by the weaving movement.
  • the between the Input shaft and the gear assembly provided clutch assembly has at least two input elements and a Output element connected to the gear assembly is.
  • the input elements generate at tapping the movement from the inside at least temporarily a synchronous movement.
  • the clutch assembly from one input element to the other input element switch.
  • the switching is thus neither as a jerk nor noticeable as a shock in the drive train. Reducing the Rotational speed of the input shaft is therefore to switch not necessary. It can be done without accepting excessive Wear or shaft or strand breaks a Achieve increased working speed of the loom and even if individual healds are always activated and must be disabled.
  • the shaft drive that is first input element is a clutch disc that is fixed with the input shaft is connected and thus one of the rotary drive device predetermined uniform rotational movement performs.
  • the second input element is then a clutch disc, which performs a rotary oscillation movement.
  • the rotational oscillation movement is in selected angular ranges, the upper and lower reversal points of the weave correspond, respectively briefly or completely in synchronism with the rotational movement of the first input element. This is regardless of whether it is the rotational movement or the up and down movement to harmonic or non-harmonic Moves.
  • the second input element back to after a rotation the first input element by 180 ° turn over a certain angular range in synchronism with the first input element mitzusted.
  • the oscillating motion of the second input element can be achieved by a cam drive that is rigid with the input shaft is connected.
  • a cam drive whose shaft with double input shaft speed runs, so with a single cam both the short synchronous movement for the upper one Reversal point as well as the short synchronous movement for the lower one Reversal point can be generated.
  • the oscillating movement by electric, hydraulic or pneumatic drives are generated.
  • a switching element is preferably one with the output element circulating pawl used that over at least to operate one, preferably two shifter is where she passes.
  • the shifters can directly be operated electrically or pneumatically. It will, however preferred, it via a control clutch from a cam drive to drive. The control clutch can then with very low power are operated, on the other hand sufficient large forces are generated to the shifter too move.
  • the clutch can e.g. via stationary control magnets be controlled and driven by a swinging Selection finger be formed. This gives a precise appealing and low energy controllable Control arrangement for the clutch arrangement.
  • the two Input elements of the clutch assembly by cams formed, both in sync with the input shaft rotate and are driven by this.
  • the starting element the coupling arrangement here forms a curve follower, the alternative with one or the other cam can be engaged.
  • the curve follower generates a swinging movement and is therefore not just part of Coupling arrangement but also part of a transmission arrangement for generating the reciprocating motion the rotational movement of the input shaft. Switching the cam follower from the tap of the one cam the other cam takes place in a rotational position of the Cams in which their arcs coincide, so that the here from the one cam tapped movement synchronous to the tapped from the other cam Movement is.
  • One of the two cam discs can be designed in this way be that they have the necessary training for movement generated while the other cam disk as a reversing disk is formed and the oscillating reversal position movement generated. As such, it only has each to take over the cam follower element serving short synchronous arcs and otherwise a profile on the webshaft no shiftworking movement but only the reversal vibration generated. In the simplest case, she is one Disc with double circumferential vibration and less radial stroke. It can also be two or more cams with different working profiles are provided. Between These cam disks can each reversing disks be arranged, which is the oscillating reversal position movement generate at the curve follower.
  • each pulley set its curve follower assign and the curve follower optionally with a Coupling output shaft.
  • the cams then form the input elements of the corresponding curve follower while the output element of the clutch assembly with a Linkage that operates the weave shaft.
  • FIG. 1 is a weaving shank 1 with associated shaft drive 2 illustrates.
  • the weave 1 is by a formed with strands 95 provided frame, which in operation like indicated by an arrow 3 is moved up and down.
  • To the Drive is a linkage 4, which on the weaving 1 to two or more places 5, 6 attaches and the output of the Shaft drive 2 forms.
  • To the shaft drive 2 include a or multiple drive sources, for example in the form of motors M1, M2. These are, for example, electric servomotors, the linkage 4 via a screw jack, a Belt transmission or another, the rotational movement of the motors connected in a linear motion converting gear are. Alternatively, linear motors, linear stepper motors or similar are used. It is enough in some Cases a single engine, while in others two or more Engines are required.
  • the motors M1, M2 are of an example on controlled by a microcontroller-based controller C, which is connected to a memory unit M.
  • the Control device C controls the motors M1, M2 so that the heald 1 for shedding up and down accordingly becomes.
  • This can for example be based on two or more in the memory unit M stored curves K1, K2 take place, wherein the first curve K1 the movement of the weave shaft 1 pretends between its reversal positions, while the Curve K2 a movement of the hive 1 in his Pretends reversals.
  • the movement of the Webshaft 1 as follows:
  • the shaft movement is based on in the direction of the arrow 3 in Figure 1 designated X coordinate of Webschafts 1 plotted over time t.
  • the course of the Movement is indicated by a curve I, e.g. can follow the shaft movement of a sine function.
  • the curve goes I of the movement, however, in a vibrational motion with reduced amplitude and reduced acceleration over. This marks a curved branch II.
  • the peculiarity of this Kurvenasts is that this in angular ranges of e.g. ⁇ 15 ° around the upper reversal point TO, which is indicated in FIG Sinusoidal oscillation without technically relevant deviation follows.
  • FIG. 4 illustrates that the reversal point oscillation can be sustained over several cycles.
  • the rest phase R occurring between the first and the last vertex may extend over one, two or more cycles of the basic oscillation of the shaft movement represented by dashed lines.
  • fundamental vibration is meant the harmonic function, with which the heald 1 is transferred from its lower reversal point TU to its upper reversal point TO. The latter takes place during its movement phases B.
  • Figure 5 illustrates a modified implementation of the idea illustrated above, namely the weave 1 during its resting phase R a movement with less Imposing amplitude, with the movement in the upper Reverse point range BTO or just in a lower Reversing point area remains.
  • the vertices are the dashed basic vibration of the hedge 1, for the transfer of a reversal point in the serves other, marked by a Kurvenast V whose second time derivative in the times t1, t2, the Mark vertices of the fundamental, the same Acceleration value has the same as the fundamental.
  • curve branch VI illustrates. But there are curves according to Figure 3 or 4 because of the associated with them web technical advantages preferred.
  • the mentioned movements of the loin 1 in the phases of movement B and the resting phases R can also be used with a mechanical Shaft drive 2 can be achieved, as in the Figures 6 to 10 is illustrated.
  • Linkage 4 include angle lever 7, 8, the Shaft movement from the movement of a pull and push rod 9 derive and on the one hand with the weaving 1 and on the other directly or indirectly with the pull and push rod 9 are connected.
  • This is connected to the shaft drive 2, the output side a rocker 11, the one Pivoting movement follows.
  • the shaft drive 2 generates from the uniform rotational movement of an input shaft 12th the illustrated in Figure 6 by an arrow 13 hinund Moving movement, this movement on the weave 1 as largely harmonic oscillatory motion in Appearance occurs.
  • FIG. 7 can be at a small distance several heald frames 1, 1a, 1b can be arranged one behind the other, that of the common shaft drive 2 and thus of the common input shaft 12 are driven.
  • a rotary drive device 14 connected by a Servomotor, another electric motor or an output shaft a central drive device is formed, the other organs of the loom drives.
  • the shaft drive 2 ( Figure 7) comprises for each weave 1, 1a, 1b are each a gear assembly 15 (15a, 15b) for converting the rotational movement of the input shaft 12 in the reciprocating motion of the respective output side Levers 11 (11 a, 11 b), and a coupling arrangement 16 (16a, 16b) over which the gear assembly 15 optionally with connect to the input shaft 12 and to separate from this is.
  • the clutch assembly 16 and the transmission assembly 15th are illustrated schematically in Figures 8 and 9.
  • the coupling arrangement serves to control the movement of the Webschafts and is in this respect the mechanically trained here Controller C.
  • the structure ( Figure 9) is as follows:
  • the gear assembly 15 is replaced by an eccentric 17th formed, the lever 11 via a connecting rod 18 ( Figure 7) swinging drives.
  • the gear assembly 15 thus serves for converting the rotational movement of the eccentric 17 in a reciprocating motion.
  • the eccentric 17 is at the same time the output element of the coupling arrangement 16 (FIG. 7), to the two input elements in the form of a first Disc 21 and a second disc 22 belong.
  • Both Discs 21, 22 preferably have the same diameter on. However, they can also have different diameters and are for the sake of clarity in FIG 9 also illustrated with different diameters.
  • the first disc 21 is connected to the input shaft 12 and over this connected to the rotary drive device 14. She is rotating thus evenly with substantially constant speed. This symbolizes in Figure 9, an arrow 23.
  • the second Disk 22 is rotatably mounted about the same axis of rotation 24 like the first disc 21. However, it is not constantly turning but turning back and forth, i. rotationally oscillating or driven swinging pendulum. This is illustrated by arrow
  • the rocker switch has a first Switching nose 29 and a second switching nose 30, wherein the Switching lugs 29, 30 on different sides of the pin 28 are arranged.
  • the switching nose 29 are two each other 180 ° opposite recesses 31, 32 in the Disc 21 assigned.
  • the switching nose 30, however, are two each other by 180 ° opposite recesses 33, 34th assigned.
  • the rocker switch 27 At its the switching nose 31 adjacent End is the rocker switch 27 with a control roller 35 provided, which thus by the spring of the rocker switch 27 in Regulated relative to the axis of rotation 24 radially outwardly is.
  • the shape of the switching lugs 29, 30 and the recesses 31 to 34 is shown in FIG.
  • the switching lugs 29, 30 and the recesses 31 to 34th designed so that the engagement and disengagement as possible facilitated is.
  • These are the switching nose 29 and the front and Rear edge of the recesses 31, 32 preferably about radially oriented.
  • the leading edge of the recesses 31, 32 is slightly lowered against the circumference to the Engaging the switching nose 29 in the recesses 31, 32nd to facilitate.
  • the reciprocating disc 22nd is assigned, preferably inclined forward against the radial. Run the locking lug 30 on the sloping trailing edge the latching recess 33, 34, the latching lug 30th pulled into the disc 22. This will be the switching process accelerated and clearly defined. Has, however, the locking lug 29 at least partially in the recess 31, 32 found and oscillates the disc 22 back, pushes their preferably rounded front edge of the locking lug 30 to the outside and thus causes the switching completely the rocker switch 27.
  • rocker 27 perform two-part, so that the switching nose 29 carrying Arm and the switching nose 30 bearing arm independently from each other around the pin 28 can rotate. Thereby can during the synchronous phase, in which the discs 21, 22 briefly run synchronously, both detents 29, 30 engaged be. The period in which both detents 29, 30 engaged are, can and may be due to the division of the rocker switch 27 be larger compared to the one-piece design. By relieving the respective disengageable switching nose 29, 30, this can then at the appropriate moment from its recess Find out 31, 32 or 33, 34.
  • the rocker 27 are two levers 36, 37 associated ( Figure 9), each one for actuating the control roller 35 serving cylindrically curved button 38, 39th exhibit.
  • the buttons 38, 39 are approximately concentric to the rotation axis 24.
  • the shift lever 36, 37 can, as from Figure 8 shows, pivoted radially inwards and outwards become. They are about pivot axes 41, 42 pivoted.
  • the inner pivot position is chosen so that the switching nose 29 from its respective recess 31, 32nd is lifted when the control roller 35 at the button 38, 39 runs along. Accordingly, then the Switching nose 30 engaged in the recess 33, 34.
  • a cam drive 43 ( Figure 8), which is connected to the input shaft 12 and, for example, has two cams. This is associated with a cam follower lever 44, which is designed as an angle lever and the shift lever 36, 37 actuated via a selection finger 45, which serves as a control clutch 46.
  • the selection finger 45 is vertically oscillated by the cam follower lever 44 and thus actuates depending on the pivot position either the free end 47 of the shift lever 36 or the free end 48 of the shift lever 37 by the respective end 47, 48 for the time of the deflection of the cam follower lever 44 is pressed down.
  • the shaft drive 2 described so far operates as follows (FIG. 9):
  • the buttons 38, 39 of the shift levers 36, 37 extend over an angular range, as the switching range can be viewed.
  • the cam follower 53 forms together with the cam 54 a pendulum drive 55th This imposes a rotary pendulum movement on the disc 22, always then synchronous with the movement of the disc 21, when the Rocker 27 passes through the switching areas.
  • These phases of movement are characterized in that the cams of Cam drive 43 the end of the cam follower lever 44 after crowd on the outside.
  • a modified embodiment of the shaft drive 2 is apparent from Figure 11.
  • the input shaft 12 is here with provided a profile teeth and carries one of several Cams 61, 62, 63 existing disc package.
  • the Cams 61, 62, 63 form the input elements of Coupling arrangement 16.
  • the output element is here by a Kurven Eisenrelement formed, the outer circumference of a the cam disks 61, 62, 63 scans.
  • This serves a role 64, rotatably mounted at one end of a rocker 65 is.
  • the role is thus both an initial element the clutch assembly 16 as well as the other gear arrangement 15 for converting the rotational movement of the shaft 12 in a reciprocating motion.
  • the other end of the seesaw 65 is connected via the connecting rod 18 with the lever 11 to to give this a pivoting movement.
  • a fluid cylinder 66 may also serve to keep the roller 64 constantly against to bias the cams 61, 62, 63.
  • the cams 61, 62, 63 are as a package on the profiled input shaft 12 mounted axially displaceable. To shift a control fork 67 and one of these serves assigned, only schematically illustrated linear Actuator 68.
  • the cams 61, 62, 63 have, e.g. from FIG 12, different circumferential profiles.
  • the cam disks 61 and 63 may be used as neutral disks be formed, which is the reversing point oscillation in the upper and in the lower reversal point pretend. Are they active i.e. rolls off the roller 64 at its periphery, performs the rocker 65 a pivoting movement, so that the weave around its reversal point e.g. with double frequency in proportion vibrates to the fundamental (range R of Figure 3).
  • At least one of the adjacent disks 61, 62, 63 has a Outer circumference, which serves as a working profile.
  • the between the discs 61, 63 arranged disc 62 has a work profile on, from an inner minimum diameter R1 to a Maximum diameter R2 and leads back from this. follows the roller 64 its profile, the shaft performs a working movement (Area B of Figure 3).
  • relative small synchronous angular ranges S1, S2 agrees the circumferential profile each with the profile of the cam 61 and 63, respectively match.
  • the cam 61 is designed as a neutral disc, who swing the weave in a turning point leaves when the roller 64 runs at its periphery.
  • the cam 63 leaves the weave in the other turning point swing when the roll runs along it.
  • the from the cams 61, 62, 63 existing package will be moved axially, around the roller 64 with the adjacent cam 61st or 63 to engage. That way, the movement can of the lever 11 within the synchronous areas S1, S2 smoothly switched on and off.
  • the synchronous operation refers to the radial component of movement of the roller 64 while they are in the embodiment of Figure 6 to 10 on the Rotational movement of the discs 21, 22 relates.
  • FIG. 14 is a modified embodiment of the reversible cam drive illustrates which manages without sliding curves.
  • FIG. 14 illustrates, belong to the cam drive a total of four cams 60, 61, 62, 63, wherein, for example, the cam discs Figures 60 and 62 are dashed lines in Figures 3, 4 and 5, respectively illustrated fundamental vibrations for the transfer of the weave 1 from one reversal to the other, while the cams 61, 63 the vibration in the upper or in the lower reversing point position.
  • the use of four cams 60, 61, 62, 63 allows it, the up and down movement of a heald 1 in time to move.
  • the cam followers 71, 72, 73, 74 are pivotally mounted a rotatably mounted shaft 77, which via a lever 78 and a link 79, the rocker 11 is actuated.
  • the wave 77 can be designed as a hollow shaft and the clutch assembly 16, optionally one of the curve followers 71, 72, 73, 74 rotationally fixed to the shaft 77 is connected.
  • To the clutch assembly 16 is then one of the shaft 16th passing cylindrical body 81, which is for each curve follower 71 to 74 each with a radially oriented Fluid channel 82 is provided.
  • their flattened part-cylindrical heads for the operation of Coupling rollers 85, 86 serve.
  • a novel shaft gearbox for harmonic in and out Turn off individual healds and derive their Motion from the rotation of a single input shaft has a coupling arrangement with two input elements 21, 22, 61, 62.
  • one of the input elements serves to the output element of the clutch assembly 16 to drive permanently, the other input element 22, 62 only to the output element 17 and 64 for a short time to synchronize to the first input element 21, 61.
  • the Switching takes place in the short synchronization phases in selected Angular ranges corresponding to the upper or lower reversal point correspond to the weave.
  • Such new shaft drives do not require a catch of the input shaft or Shaft drive for switching.

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  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Looms (AREA)
  • Transmission Devices (AREA)
EP04018093A 2003-09-17 2004-07-30 Système d'entraînement de lames pour machines à tisser Expired - Lifetime EP1516947B2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10343377A DE10343377B3 (de) 2003-09-17 2003-09-17 Schaftantrieb für Webmaschinenschäfte
DE10343377 2003-09-17

Publications (4)

Publication Number Publication Date
EP1516947A2 true EP1516947A2 (fr) 2005-03-23
EP1516947A3 EP1516947A3 (fr) 2006-08-02
EP1516947B1 EP1516947B1 (fr) 2008-03-26
EP1516947B2 EP1516947B2 (fr) 2012-08-29

Family

ID=34177828

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04018093A Expired - Lifetime EP1516947B2 (fr) 2003-09-17 2004-07-30 Système d'entraînement de lames pour machines à tisser

Country Status (5)

Country Link
US (1) US7140399B2 (fr)
EP (1) EP1516947B2 (fr)
JP (1) JP4383292B2 (fr)
CN (1) CN100507110C (fr)
DE (2) DE10343377B3 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1700939A3 (fr) * 2005-03-07 2008-10-15 Groz-Beckert KG Système d'entraînement de lames pour métiers à tisser
US7475708B2 (en) 2004-11-17 2009-01-13 Groz-Beckert Kg Shaft drive for heald shafts of weaving machines
EP2365116A1 (fr) 2010-03-12 2011-09-14 Stäubli Faverges Ratière rotative et métier à tisser équipé d'une telle ratière
WO2012163571A3 (fr) * 2011-06-01 2013-08-01 Textilma Ag Métier à ratière et procédé de tissage correspondant
EP3327190A1 (fr) * 2016-11-25 2018-05-30 Kabushiki Kaisha Toyota Jidoshokki Dispositif et procédé de formation de la foule pour métier à tisser

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005059911B3 (de) 2005-12-15 2007-02-08 Groz-Beckert Kg Schaftantrieb für eine Webmaschine
FR2899602B1 (fr) * 2006-04-11 2008-05-23 Staubli Faverges Sca Ratiere rotative, metier a tisser comprenant une telle ratiere et procede de commande d'une telle ratiere
US20080053555A1 (en) * 2006-07-19 2008-03-06 Groz-Beckert Kg Shaft drive transmission and coupling rod
EP2069564B1 (fr) * 2006-09-28 2016-05-11 Textilma Ag Dispositif de formation de la foule pour un métier à tisser mécanique, en particulier un métier à tisser les rubans
DE102007015411A1 (de) 2007-03-28 2008-10-02 Groz-Beckert Kg Kurvenscheibe für Exzentermaschine einer Webmaschine
DE502007005459D1 (de) * 2007-03-28 2010-12-09 Groz Beckert Kg Kurvenscheibe für eine Fachbildeeinrichtung einer Webmaschine
EP1992724B1 (fr) * 2007-05-14 2012-01-25 Groz-Beckert KG Corde à lisse pouvant être divisée en deux parties
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
EP2278052B1 (fr) 2009-07-20 2014-03-05 Groz-Beckert KG Dispositif d'entraînement pour un cadre de lisses d'un métier à tisser
CN106948061B (zh) * 2016-12-30 2019-08-06 江苏宋和宋智能科技有限公司 一种独立伺服综框
CN106868680B (zh) * 2017-04-07 2018-08-17 杨国惠 一种平衡综框静力、惯性力的开口机
JP7321949B2 (ja) * 2020-02-03 2023-08-07 津田駒工業株式会社 織機における製織方法及びその製織方法を実現するための開口装置
US11926209B2 (en) * 2020-02-19 2024-03-12 Deere & Company Electric power take off
CN117416402B (zh) * 2023-12-18 2024-04-23 南通睿博电器有限公司 一种运输设备及其运输方法

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Publication number Priority date Publication date Assignee Title
US7475708B2 (en) 2004-11-17 2009-01-13 Groz-Beckert Kg Shaft drive for heald shafts of weaving machines
EP1700939A3 (fr) * 2005-03-07 2008-10-15 Groz-Beckert KG Système d'entraînement de lames pour métiers à tisser
EP2365116A1 (fr) 2010-03-12 2011-09-14 Stäubli Faverges Ratière rotative et métier à tisser équipé d'une telle ratière
FR2957366A1 (fr) * 2010-03-12 2011-09-16 Staubli Sa Ets Ratiere rotative et metier a tisser equipe d'une telle ratiere
WO2012163571A3 (fr) * 2011-06-01 2013-08-01 Textilma Ag Métier à ratière et procédé de tissage correspondant
CN103582725A (zh) * 2011-06-01 2014-02-12 泰克斯蒂尔玛股份公司 剑杆织机和相应的纺织方法
CN103582725B (zh) * 2011-06-01 2015-10-21 泰克斯蒂尔玛股份公司 剑杆织机和相应的纺织方法
EP3327190A1 (fr) * 2016-11-25 2018-05-30 Kabushiki Kaisha Toyota Jidoshokki Dispositif et procédé de formation de la foule pour métier à tisser

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DE502004006644D1 (de) 2008-05-08
EP1516947B1 (fr) 2008-03-26
CN1598106A (zh) 2005-03-23
US20050056334A1 (en) 2005-03-17
DE10343377B3 (de) 2005-04-28
EP1516947A3 (fr) 2006-08-02
JP2005089954A (ja) 2005-04-07
JP4383292B2 (ja) 2009-12-16
EP1516947B2 (fr) 2012-08-29
CN100507110C (zh) 2009-07-01
US7140399B2 (en) 2006-11-28

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