EP1516947B2 - Système d'entraînement de lames pour machines à tisser - Google Patents

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

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Publication number
EP1516947B2
EP1516947B2 EP04018093A EP04018093A EP1516947B2 EP 1516947 B2 EP1516947 B2 EP 1516947B2 EP 04018093 A EP04018093 A EP 04018093A EP 04018093 A EP04018093 A EP 04018093A EP 1516947 B2 EP1516947 B2 EP 1516947B2
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EP
European Patent Office
Prior art keywords
movement
shaft
drive
disc
input element
Prior art date
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Application number
EP04018093A
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German (de)
English (en)
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EP1516947B1 (fr
EP1516947A3 (fr
EP1516947A2 (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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    • 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 switching drive for at least one heald of a loom.
  • a plurality of healds are generally provided on looms, each having a plurality of mutually parallel strands are guided by the thread eyes the warp thread.
  • the healds are moved up and down very quickly.
  • Serve shaft drives which are referred to as dobby or eccentric machines. So-called eccentric machines generate from the rotating movement of a drive shaft the up and down movement of the weaves, whereby high weaving speeds can be achieved.
  • eccentric machines are inflexible. The creation of patterns or different bindings is limited. Therefore, shaft drives are widely used, in which a pawl clutch is provided between a drive shaft and the eccentric for generating the shaft movement.
  • Such a dobby is for example from the DE 697 02 039 T2 known.
  • the pawl shifting mechanism disposed between the eccentric and the driving shaft is here switched on for each shaft movement, ie for an upward movement of the shaft or for a downward movement of the shaft in each case for half a shaft rotation.
  • Such dobby are very flexible.
  • Such dobby machines can not reach the working speed of eccentric machines.
  • the work of the pawl switching mechanisms is susceptible to wear. An increase in the operating speed, however, not only leads to ratchet wear, but also to strand and shank breaks.
  • the movement to be performed by the shaft during the rest phase is generated or predetermined mechanically.
  • the shaft is over a Coupling device optionally connected to a first drive which generates a constantly oscillating between two reversing positions movement, or with another drive which generates the oscillating about the upper or lower reversal position movement. Switching takes place during existing synchronization phases.
  • the shaft drive according to the invention has an input shaft connected to a rotary drive device, which ultimately serves to drive a gear arrangement which generates the reciprocating movement of the heald shaft.
  • the clutch assembly provided between the input shaft and the transmission assembly has at least two input members and an output member connected to the transmission assembly.
  • the input elements generate at least temporarily a synchronous movement when tapping the movement from the inside.
  • the clutch arrangement can switch from one input element to the other input element. The changeover is thus not noticeable as a jolt nor as a shock in the drive train. Reducing the rotational speed of the input shaft is therefore not necessary for switching. It can be achieved without accepting excessive wear or shaft or strand breaks increased operating speed of the loom and even if individually Web shafts must be repeatedly activated and deactivated.
  • the first input element is a clutch disc that is fixed with the input shaft is connected and thus performs a predetermined by the rotary drive means uniform rotational movement.
  • the second input element is then a clutch disc that performs a rotational oscillation movement.
  • the rotational oscillatory movement is in each case for a short time completely or nearly synchronously with the rotational movement of the first input element in selected angular ranges which correspond to the upper and lower reversal points of the heald.
  • the second input element then rotates back to run in synchronism with the first input element over a certain angular range after a rotation of the first input element through 180 ° again.
  • the oscillating motion of the second input member may be achieved by a cam gear rigidly connected to the input shaft.
  • a cam drive is used whose shaft is running at twice the input shaft speed, so that both the short synchronous movement for the upper reversal point and the short synchronous movement for the lower reversal point can be generated with a single cam.
  • the oscillating motion can be generated by electrical, hydraulic or pneumatic drives.
  • a rotating with the output member pawl is used, which is operated via at least one, preferably two shifter, where it passes.
  • the shifters can be directly electrically or pneumatically confirmed. However, it is preferred to drive them via a control clutch from a cam drive ago.
  • the control clutch can then be operated with very low power, on the other hand, sufficiently large forces are generated to move the shift lever.
  • the clutch can e.g. Be controlled by stationary control magnets and be formed by a swinging driven selection finger. This results in a precisely responsive and with low energy controllable control arrangement for the clutch assembly.
  • the two input elements of the clutch assembly are formed by cams, both of which rotate synchronously with the input shaft and are driven by this.
  • the starting element the coupling arrangement forms a cam follower, which can alternatively be brought into engagement with one or the other cam disk.
  • the cam follower generates a swinging motion and thus is not only part of the clutch assembly but also part of a gear assembly for generating the reciprocating motion from the rotational movement of the input shaft.
  • the switching of the cam follower from the tap of the one cam to the other cam takes place in a rotational position of the cam in which their arcs match, so that the tapped here of the one cam is synchronous with the movement tapped by the other cam disc movement.
  • One of the two cams may be configured to generate the motion required for shedding while the other is constructed as a reversing shim and to generate the oscillating reverse position movement. As such, it only has short synchronizing arches respectively serving to take over the cam follower element and otherwise a profile which does not generate a shedding motion on the weaving sheave but only the reversing position oscillation. In the simplest case, it is a disc with double circumference and lower radial stroke. It is also possible to provide two or more cams with different working profiles. In each case reversing ply disks can be arranged between these cams, which produce the oscillating reversing position movement on the cam follower.
  • each cam set with its cam follower and to couple the cam followers optionally with an output shaft.
  • the cams then form the input elements of the corresponding cam followers, while the output member of the coupling assembly is connected to a linkage which actuates the heald.
  • FIG. 1 a heald 1 with associated shaft drive 2 is illustrated.
  • the heald 1 is formed by a provided with strands 95 frame, which is in operation as indicated by an arrow 3 moves up and down.
  • a linkage 4 which attaches to the weaving shank 1 at two or more points 5, 6 and forms the output of the shaft drive 2.
  • the shaft drive 2 includes one or more drive sources, for example in the form of the motors M1, M2. These are, for example, electric servomotors, which are the linkage 4 via a screw jack, a belt transmission or other, the rotational movement of the motors in a linear motion converting gear are connected. Alternatively, linear motors, linear stepping motors or the like can be used. It suffices in some cases, a single engine, while in other two or more engines required are.
  • the motors M1, M2 are controlled by a control device C, for example based on a microcontroller, which is connected to a memory unit M.
  • the control device C controls the motors M1, M2 in such a way that the heald 1 is moved up and down in accordance with the shed formation. This can be done, for example, by means of two or more curves K1, K2 stored in the memory unit M, wherein the first curve K1 specifies the movement of the heald 1 between its reversal positions, while the curve K2 specifies a movement of the heald 1 in its reversal positions.
  • the movement of the weave shaft 1 is as follows:
  • FIG. 3 is the shaft movement based on the in the direction of arrow 3 in FIG. 1 designated X coordinate of the heald 1 plotted against the time t.
  • the course of the movement is indicated by a curve I, eg the shaft movement can follow a sine function.
  • the curve I of the movement passes into a vibratory motion of reduced amplitude and reduced acceleration. This marks a curve branch II.
  • the peculiarity of this Kurvenasts is that this in angular ranges of eg ⁇ 15 ° to the upper reversal point TO, the in FIG. 3 indicated sinusoidal oscillation without technically relevant deviation follows.
  • the particular characteristic of the movement impressed on the motors M1, M2 by the control device C is thus that the heald 1 does not rest in the upper reversal point TO but executes a vibration in a reversal point area BTO.
  • the effect of this measure can be seen from the dashed curve III plotted in the same diagram, which illustrates the downward acceleration of the heald 1, which is therefore plotted with negative signs. If the movement of the heald shaft 1 initially follows a sine movement, the shaft acceleration is also a sine function. In the region of the upper vertex, when the upper reversal point TO is reached, the control device C now changes from the curve I to the curve II (FIG. FIG. 2 ).
  • FIG. 3 To illustrate the benefits of Umlopeddlingschwingung in the upper or corresponding at the lower reversal point is on FIG. 3 referenced in which a dot-dash curve branch IV connects the upper vertices of the shaft movement together. If the heald shaft 1 would follow this curve IV after reaching its upper reversal point TO, the acceleration which just has the value A1 would suddenly fall to the value 0 at the time T1. The resulting acceleration peak generated on the weaving shank 1 and the strands and on all associated transmission parts loads that can lead to shaft and strand breaks. Such loads are minimized or largely limited by the pendulum movements, because by the same accelerations are kept to a minimum.
  • FIG. 4 illustrates that 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.
  • FIG. 12 illustrates a modified realization of the above-illustrated idea of imparting low amplitude motion to the heald 1 during its resting phase R, the movement remaining in the upper turning point range BTO or, correspondingly, in a lower turning point range.
  • the vertexes of the prime 1 of the heald 1 illustrated in dashed lines which serves to transfer from one reversal point to the other, are marked by a curve branch V whose second time derivative has the same acceleration value at times t1, t2 marking the vertices of the fundamental like the fundamental.
  • the acceleration of the heald 1 is stepless or continuous, as the Kurvenast VI illustrates. However, it will curve according to FIG. 3 or 4 preferred because of the web technical advantages associated with them.
  • the said movements of the heald shaft 1 in the movement phases B and the resting phases R can also be achieved with a mechanical shaft drive 2, as described in US Pat FIGS. 6 to 10 is illustrated.
  • a mechanical shaft drive 2 As described in US Pat FIGS. 6 to 10 is illustrated.
  • linkage 4 include angle lever 7, 8, which derive the shaft movement of the movement of a pull and push rod 9 and on the one hand to the heald 1 and on the other hand directly or indirectly connected to the pull and push rod 9.
  • This is connected to the shaft drive 2, the output side of a rocker 11, which follows a pivoting movement has.
  • the shaft drive 2 generates from the uniform rotational movement of an input shaft 12 in FIG. 6 illustrated by an arrow 13 reciprocating motion, this movement on the heald 1 as a largely harmonic oscillatory motion in appearance.
  • a plurality of heald frames 1, 1a, 1b can be arranged at a small distance one behind the other, which are driven by the common shaft drive 2 and thus by the common input shaft 12.
  • This is connected to a rotary drive device 14, which is formed by a servo motor, another electric motor or an output shaft of a central drive device, which drives other organs of the loom.
  • the shaft drive 2 ( FIG. 7 ) comprises for each weaving shank 1, 1a, 1b respectively a gear arrangement 15 (15a, 15b) for converting the rotational movement of the input shaft 12 into the reciprocating movement of the respective output side lever 11 (11a, 11b), and a coupling arrangement 16 (16a , 16b), via which the gear assembly 15 is to be selectively connected to the input shaft 12 and to be separated from it.
  • the clutch assembly 16 and the gear assembly 15 are in the FIGS. 8 and 9 schematized illustrated.
  • the coupling arrangement serves to control the movement of the heald and is in this respect the mechanically designed here control device C.
  • the structure ( FIG. 9 ) is as follows:
  • the gear assembly 15 is formed by an eccentric 17, which via a connecting rod 18, the lever 11 (FIG. Figur7 ) vibrates.
  • the gear assembly 15 thus serves to convert 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. Figur7 ), to which 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. However, they can also have different diameters and are designed to improve clarity FIG. 9 also illustrated with different diameters.
  • the first disc 21 is connected to the input shaft 12 and via this to the rotary drive device 14. It thus rotates uniformly at a substantially constant speed. This symbolizes in FIG. 9 an arrow 23.
  • the second disc 22 is rotatably supported about the same axis of rotation 24 as the first disc 21. However, it is not constantly rotating but reciprocating, ie driven rotationally oscillating or mospendelnd. This is illustrated by arrow 25.
  • To the clutch assembly 16 from FIG. 7 also includes a switching element 26, shown in FIG. 9 , in the form of a rocker switch 27, which is mounted pivotably about a pin 28 on the eccentric 17.
  • the switching rocker has a first switching nose 29 and a second switching nose 30, wherein the switching lugs 29, 30 are arranged on different sides of the pin 28.
  • the switching lug 29 are assigned to each other by 180 ° opposite recesses 31, 32 in the disc 21.
  • the switching lug 30, however, are assigned to each other by 180 ° opposite recesses 33, 34.
  • the rocker switch 27 is biased with its switching nose 29 on the disc 21 out.
  • the rocker switch 27 is provided with a control roller 35, which is thus biased by the spring of the rocker switch 27 with respect to the axis of rotation 24 radially outwardly.
  • the shape of the switching lugs 29, 30 and the recesses 31 to 34 goes out FIG. 10 out.
  • the switching lugs 29, 30 and the recesses 31 to 34 are designed so that the engagement and disengagement is facilitated as possible.
  • the switching nose 29 and the front and rear flanks of the recesses 31, 32 are preferably oriented approximately radially. The leading edge of the recesses 31, 32 is slightly lowered against the circumference to facilitate the engagement of the switching lug 29 in the recesses 31, 32.
  • both latching lugs 29, 30 can be engaged.
  • the period in which both locking lugs 29, 30 are engaged can and may be greater due to the division of the rocker switch 27 in comparison to the one-piece design.
  • the rocker 27 are two levers 36, 37 assigned ( FIG. 9 ), each having a for actuating the control roller 35 serving cylindrically curved button 38, 39.
  • the buttons 38, 39 are approximately concentric with the axis of rotation 24.
  • the shift lever 36, 37 as can FIG. 8 shows, be pivoted radially inwards and outwards. They are pivoted about pivot axes 41, 42. The inner pivot position is selected so that the shift lug 29 is lifted out of its respective latching recess 31, 32 when the control roller 35 runs along the button 38, 39. Accordingly, the switching nose 30 is engaged in the recess 33, 34.
  • a cam drive 43 ( FIG. 8 ), which is connected to the input shaft 12 and, for example, has two cams. These are assigned a cam follower lever 44, which is designed as an angle lever and the shift lever 36, 37 is 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 rocker switch 27 must constantly connect the disc 21 with the eccentric 17.
  • each of the shift lever 36 and the shift lever 37 must always escape to the outside when the rocker switch 27 passes as a result of the rotation of the disc 21 to the respective shift lever.
  • the control magnets 51, 52 are alternately driven so that the selection finger 45 pushes the end 47 down when the rocker switch 27 passes by the shift lever 36 and that the selection finger 45 pushes the end 48 down when the rocker switch 27 on the shift lever 37 passes.
  • buttons 38, 39 of the shift levers 36, 37 extend over an angular range, which can be regarded as a shift range.
  • the cam follower 53 together with the cam 54, a pendulum drive 55. This imparts the disc 22 to a rotary pendulum motion, which is always synchronous with the movement of the disc 21 when the rocker switch 27 passes through the switching areas.
  • These movement phases are characterized in that the cams of the cam drive 43 urge the end of the cam follower lever 44 to the outside.
  • the clutch assembly 16 can be switched by the respective shift lever 36 or 37 does not escape to the outside. This will ( FIG. 9 ), for example, the switching lug 29 pushed out of the recess 31 and the switching lug 30 engaged in the recess 33.
  • the relevant shift lever 36 or 37 then remains activated by the relevant shift lever 36, 37, for example by springs 56, 57 (FIG. FIG. 8 ) is held in its inner position and is not moved outwardly by the selection finger 45.
  • the eccentric 17 performs only a reciprocating motion in this state, because he is bound to the disc 22.
  • the movement oscillating back and forth by a few degrees, for example 10 °, causes only a slight upward and downward movement of the same in the upper or lower reversal point of the heald, at most only a few millimeters. This does not disturb the shedding and weaving process. However, it allows a synchronous reconnection by only the relevant lever 36, 37, in which the rocker switch 27 is pivoted outwardly.
  • the cam drive 43 causes this at the moment of synchronization of the two discs 21, 22, so that a soft shock-free restart of the eccentric 17 takes place.
  • a modified embodiment of the shaft drive 2 goes out FIG. 11 out.
  • the input shaft 12 is here provided with a profile toothing and carries a plurality of cams 61, 62, 63 existing disk package.
  • the cam disks 61, 62, 63 form the input elements of the clutch assembly 16.
  • the output member is here formed by a cam follower element which scans the outer periphery of one of the cams 61, 62, 63.
  • a roller 64 which is rotatably mounted at one end of a rocker 65. The role is thus at the same time on the one hand output element of the clutch assembly 16 as well as on the other hand gear assembly 15 for converting the rotational movement of the shaft 12 in a reciprocating motion.
  • the other end of the rocker 65 is connected via the connecting rod 18 with the lever 11 in order to give this a pivoting movement.
  • a fluid cylinder 66 may also serve to continually bias the roller 64 against the cams 61, 62, 63.
  • the cams 61, 62, 63 are axially displaceable as a package on the profiled input shaft 12 stored. For displacement serves a control fork 67 and one of these associated, only schematically illustrated linear actuator 68th
  • the cams 61, 62, 63 have, as for example FIG. 12 Obviously, different circumferential profiles.
  • the cams 61 and 63 may be formed as neutral discs, which specify the reversal point vibration in the upper and in the lower reversal point. Are they active, ie rolls off the roller 64 at its periphery, performs the rocker 65 a pivoting movement, so that the weave around its reversal point, for example, with double frequency in relation to the fundamental oscillates (range R from FIG. 3 ).
  • At least one of the adjacent disks 61, 62, 63 has an outer circumference serving as a working profile. This is in the present embodiment, between the discs 61, 63 arranged disc 62.
  • the package consisting of the cams 61, 62, 63 can be displaced axially in order to engage the roller 64 with the adjacent camming disk 61 or 63. In this way, the movement of the lever 11 within the synchronous areas S1, S2 can be switched on and off smoothly.
  • the switching on and off of the drive is also based here on the fact that the switching over from one input element to another occurs during a short synchronous phase.
  • the synchronism refers to the radial component of movement of the roller 64 while in the embodiment according to FIGS. 6 to 10 refers to the rotational movement of the discs 21, 22.
  • the cam drive includes a total of four cams 60, 61, 62, 63, wherein, for example, the cams 60 and 62, the in FIGS. 3, 4 and 5 each identified by dashed lines fundamental vibrations for transferring the heald 1 from a reversal position in the other mark while the cams 61, 63 set the vibration in the upper or in the lower reversing point.
  • the use of four cams 60, 61, 62, 63 makes it possible to offset the up and down movement of a heald 1 in time.
  • the heald 1 after it has been moved by means of the cam 60 in the upper reversal point, transferred by means of the cam 61 in a pendulum motion, from which it is then transferred by the cam 62 down to the lower reversal point.
  • This equals a phase shift of 180 degrees.
  • Each cam 60 to 63 is in each case with a cam follower 71, 72, 73, 74 in connection.
  • FIG. 13 illustrates the cam follower 74, which scans the outer circumference of the cam 63 with two rollers 75, 76.
  • the cam followers 71, 72, 73, 74 are pivotally mounted on a rotatably mounted shaft 77 which actuates the rocker 11 via a lever 78 and a link 79.
  • the shaft 77 may be formed as a hollow shaft and accommodate the clutch assembly 16, which is rotatably connected to the shaft 77 selectively one of the cam follower 71, 72, 73, 74.
  • a shaft 16 passing through cylindrical body 81 which is provided for each cam follower 71 to 74 each having a radially oriented fluid channel 82.
  • piston 83, 84 whose flattened part-cylindrical heads for actuating clutch rollers 85, 86 are used.
  • each cam follower 71 to 74 can be specifically controlled separately, to couple only one of the cam follower 71 to 74 with the hollow shaft 77. In this way, one of the predetermined by the cams 60, 61, 62, 63 motion profiles can be selected, wherein the switching in each case in the synchronization phases according to FIGS. 3 to 5 he follows.
  • a novel shaft gear for harmonic switching on and off of individual healds and for deriving their movement from the rotational movement of a single input shaft has a coupling arrangement with two input elements 21, 22, 61, 62. While one of the input elements serves to permanently drive the output member of the clutch assembly 16, the other input member 22, 62 merely serves to briefly synchronize the output member 17 and 64, respectively, to the first input member 21, 61. Switching takes place in the short synchronization phases in selected angular ranges corresponding to the upper or lower reversal point of the heald. Such new shaft drives do not require a catch of the input shaft or the shaft drive for switching.

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  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Looms (AREA)
  • Transmission Devices (AREA)

Claims (6)

  1. Système d'entraînement pour au moins une lame (1) d'un métier mécanique, comprenant
    au moins un mécanisme de sortie (4) qui est associé à la lame (1) et est lié à celle-ci, afin de la maintenir dans des phases de repos (R) et de lui communiquer, lors de phases de mouvement (B), un mouvement d'avance correspondant à une fonction harmonique entre un point de rebroussement inférieur (TU) et un point de rebroussement supérieur (TO), et
    un dispositif de commande (C, 16) destiné à commander la vitesse actuelle du mécanisme de sortie (4) et donc de la lame (1),
    dans lequel le mécanisme de sortie (4) avec la lame (1) exécute un mouvement oscillant prédéterminé entre un point de rebroussement supérieur (BTO) et un point de rebroussement inférieur (BTU), en dehors des phases de mouvement (B), pendant les phases de repos (R),
    dans lequel le mécanisme de sortie (4), au début d'une phase de repos (R), présente une accélération qui correspond à son accélération à la fin de la phase de mouvement (B) précédente et, au début d'une phase de mouvement (B), présente une accélération qui correspond à son accélération à la fin de la phase repos (R) précédente,
    dans lequel on évite les paliers d'accélérations et on obtient un déplacement sans à-coups de la lame (1),
    dans lequel le mécanisme de sortie (4) présente un dispositif d'accouplement (16) qui est placé entre un dispositif d'entraînement (14) et un mécanisme (15) destiné à transmettre le mouvement d'entraînement à la lame (1),
    dans lequel le dispositif d'accouplement (16) présente un premier élément d'entrée (21), lié au dispositif d'entraînement (14), et un deuxième élément d'entrée (22), ainsi qu'un élément de sortie (17) qui peut être relié de manière sélective au premier élément d'entrée (21) pendant la phase de mouvement (B) ou au deuxième élément d'entrée (22) pendant la phase de repos (R), le dispositif d'entraînement (14) communiquant au premier élément d'entrée (21) un mouvement à direction constante, et le deuxième élément d'entrée (22) étant amené à exécuter un mouvement à direction alternée,
    dans lequel l'élément de sortie, le premier élément d'entrée et le deuxième élément d'entrée sont formés respectivement d'un excentrique (17), d'un premier disque (21) et d'un deuxième disque (22), le premier disque (21) étant lié au dispositif d'entraînement (14) et entraîné en rotation constante par l'intermédiaire d'un arbre d'entrée (12) et le deuxième disque (22) étant monté tournant autour du même axe de rotation (24) que le premier disque (21) et entraîné en rotation alternée,
    dans lequel le dispositif d'accouplement (16) comprend des moyens (36, 37, 46, 44, 43) englobant un élément de manoeuvre (26) qui est relié de manière permanente à l'élément de sortie (17) et de manière sélective au premier ou au deuxième élément d'entrée (21, 22), ledit élément de manoeuvre (26) étant une bascule de manoeuvre (27) montée pivotante autour d'un axe (28) sur l'excentrique (17),
    et dans lequel les premier (21) et deuxième (22) disques sont entraînés en synchronisme pendant une phase synchrone et la commutation a lieu pendant la phase synchrone.
  2. Système d'entraînement de lame selon la revendication 1, caractérisé en ce que le mouvement prédéterminé des phases de repos est défini par le dispositif de commande (C, 16).
  3. Système d'entraînement de lame selon la revendication 1, caractérisé en ce que, dans des positions de manoeuvre prédéterminées par les moyens (36, 37, 46, 44, 43), le mouvement rotatif oscillant du deuxième élément d'entrée (22) est synchrone avec le mouvement rotatif du premier élément d'entrée (21),
    et en ce que les moyens (36, 37, 46, 44, 43) comportent au moins un levier de manoeuvre (36, 37) qui est associé à l'élément de manoeuvre (27) pour accoupler ou désaccoupler celui-ci dans au moins une position de manoeuvre prédéterminée.
  4. Système d'entraînement de lame selon la revendication 3, caractérisé en ce que l'élément de manoeuvre (27) tourne avec l'élément de sortie (17).
  5. Système d'entraînement de lame selon la revendication 4, caractérisé en ce que l'élément de manoeuvre (27) comporte au moins un élément de liaison par obstacle (29, 30) pour chaque élément d'entrée (21, 22).
  6. Système d'entraînement de lame selon la revendication 3, caractérisé en ce que le levier de manoeuvre (36, 37) est relié par l'intermédiaire d'un accouplement de commande (46) à un moyen d'entraînement à cames (43), en ce que l'accouplement de commande (46) présente un doigt de sélection (45) qui peut être déplacé entre au moins deux positions pour activer et désactiver le moyen d'actionnement du levier de manoeuvre (36, 37) par l'intermédiaire du moyen d'entraînement à cames (43), et en ce que le doigt de sélection (45) peut être déplacé par au moins un aimant de commande (51, 52).
EP04018093A 2003-09-17 2004-07-30 Système d'entraînement de lames pour machines à tisser Active EP1516947B2 (fr)

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DE10343377 2003-09-17
DE10343377A DE10343377B3 (de) 2003-09-17 2003-09-17 Schaftantrieb für Webmaschinenschäfte

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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
WO2008037106A1 (fr) * 2006-09-28 2008-04-03 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
EP1975292B1 (fr) * 2007-03-28 2010-10-27 Groz-Beckert KG Disque à came pour un dispositif de formation de la foule d'un métier à tisser
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
FR2957366B1 (fr) 2010-03-12 2012-04-13 Staubli Sa Ets Ratiere rotative et metier a tisser equipe d'une telle ratiere
EP2683862B1 (fr) * 2011-06-01 2015-11-18 Textilma AG Métier à ratière et procédé de tissage correspondant
JP6635006B2 (ja) * 2016-11-25 2020-01-22 株式会社豊田自動織機 織機における開口方法及び開口装置
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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EP1516947B1 (fr) 2008-03-26
CN100507110C (zh) 2009-07-01
US20050056334A1 (en) 2005-03-17
CN1598106A (zh) 2005-03-23
EP1516947A3 (fr) 2006-08-02
EP1516947A2 (fr) 2005-03-23
DE10343377B3 (de) 2005-04-28
JP4383292B2 (ja) 2009-12-16
JP2005089954A (ja) 2005-04-07
DE502004006644D1 (de) 2008-05-08
US7140399B2 (en) 2006-11-28

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