EP0467824A1 - Loom with a weft changing device - Google Patents

Abstract

The weft-changing device (12) contains a changer element (21) controllable by the loom drive and having a plurality of yarn take-ups (22a, 22b, 22c, 22d), each movable into a yarn transfer position, and a drive device (20) which has a single servo-motor (50), two drive parts (23, 24), each adjustable between two specific operating positions, with force accumulators (25, 26) and a summing gear (27) with an output part (28) which is coupled to the changer element (21) and which is adjustable via the summing gear (27) between four specific operating positions. The servo-motor (50) is connected to a driving shaft (44) which can be fixed in four angular positions offset respectively at 90 DEG relative to one another and which contains two coupling parts which are arranged offset relative to one another at an angle alpha = 90 DEG about the axis of the driving shaft (44) and which are each coupled to one of the drive parts (23 and 24). Consequently, in each of the four operating positions of the changer element (21), each of the other three operating positions can be obtained by means of a simple quarter rotation of the driving shaft (44) in one direction of rotation or the other or by means of a half revolution of the driving shaft (44) and consequently within correspondingly short response times. <IMAGE>

Description

The invention relates to a weaving machine with a multi-weft device for changing the one to be entered. Weft thread, which contains a changer element that can be controlled by the weaving machine drive and has a plurality of thread transmitters, each of which can be moved into a thread transfer position, and a drive device that has two drive parts that can be adjusted between two defined operating positions, two connected to them, for temporary storage of the adjusting force introduced via them, and one force storage device Contains drive part that can be coupled to the changer element and that is adjustably connected to the energy stores via a summing gear between four defined operating positions.

In looms of the type mentioned, it is known to derive the drive of the multi-weft device from a shaft rotating at the speed of the main shaft, the drive device, for example, two lifting knives moving up and down in opposite directions with each rotation of the main shaft and two sinkers which can optionally be coupled with one of these lifting knives contains, via which the two drive parts each adjusted to one or the other operating position or held in the relevant operating position (DE patent specification 17 10 356). The four possible combinations of the operating positions of the two drive parts result in four defined operation: positions of the changer element that can be adjusted via the summing gear and the driven part.

The known design allows a precise and - for weaving machines with the usual weft insertion performance - a sufficiently quick change of the thread feeder to be brought into the thread transfer position. However, the known design requires a relatively large mechanical effort, which increases above average especially when the weft insertion rate is increased and requires a correspondingly increased amount of energy. Due to the relatively rigid mechanical coupling of the drive device to the main shaft or a shaft connected to it, depending on the design of the associated control device, the length of the shot or color repeat that can be produced at a reasonable cost can also be limited.

The invention has for its object to provide a weaving machine, in particular improved in this regard, with a simplified multi-weft device compared to previous versions, which allows the drive parts to be controlled independently of the respective angular position of the main shaft and which allows an increase in the weft insertion numbers with little effort and at the same time precise setting and adjustment of the changer element guaranteed.

This object is achieved according to the invention in that the drive device has a servomotor and a contains this drivable, in four angular positions staggered by 90 ° relative drive shaft with two coupling parts, which are offset from each other by an angle α = 90 ° around the axis of the drive shaft and each coupled to one of the drive parts.

The design according to the invention provides a compact construction of the drive device which requires fewer mechanical components than previous designs. At the same time, in a simple manner - if necessary using a large part of the transmission elements developed and proven in practice for previous drive devices, which are available in numerous kits, e.g. are available for the conversion of existing weaving machines - a significant reduction in the time required for the control of the drive parts, since in each of the four operating positions of the changer element each of the three other operating positions is extremely short-term, by a quarter turn of the drive shaft in one or the other other direction of rotation or by half a turn of the drive shaft.

Embodiments of the invention are specified in the dependent claims.

• Fig. 1 eine erfindungsgemäss ausgebildete Webmaschine mit einer Mehrschussvorrichtung, von der Warenseite her gesehen;
• Fig. 2 Einzelheiten der Mehrschussvorrichtung nach Fig. 1 in einer axonometrischen Teilansicht;
• Fig. 3 Einzelheiten der Mehrschussvorrichtung in einer Teilansicht mit Teilschnitt entsprechend der Linie III-III in Fig. 2
• Fig. 4 Teile der Mehrschussvorrichtung nach den Fig. 2 und 3 in vier Betriebsstellungen;
• Fig. 5 Teile einer Mehrschussvorrichtung nach einer anderen Ausführungsform, in einer Teilansicht mit Teilschnitt entsprechend der Linie V-V in Fig. 6;
• Fig. 5a, 5b und 5c unterschiedliche Betriebsstellungen eines Teils der Mehrschussvorrichtung nach Fig. 5;
• Fig. 6 die Mehrschussvorrichtung nach Fig. 5 in einem Teillängsschnitt entsprechend der Linie VI-VI in Fig. 5;
• Fig. 7 Teile einer Mehrschussvorrichtung in einer weiteren abgewandelten Ausführungsform.

Further features and details emerge from the following description of exemplary embodiments of the invention shown schematically in the drawing. Show it:

• 1 shows a weaving machine designed according to the invention with a multi-weft device, seen from the goods side;
• FIG. 2 details of the multi-shot device according to FIG. 1 in a partial axonometric view;
• 3 details of the multi-shot device in a partial view with partial section along the line III-III in Fig. 2nd
• 4 parts of the multi-shot device according to FIGS. 2 and 3 in four operating positions;
• 5 shows parts of a multi-shot device according to another embodiment, in a partial view with partial section along the line VV in FIG. 6;
• 5a, 5b and 5c different operating positions of a part of the multi-shot device according to FIG. 5;
• 6 shows the multi-shot device according to FIG. 5 in a partial longitudinal section along the line VI-VI in FIG. 5;
• Fig. 7 parts of a multi-shot device in a further modified embodiment.

The weaving machine shown in FIG. 1 contains a machine frame with two side cheeks 1 and 2, between which a warp beam 3 with warp threads 4 running from it, a warp beam 5 for receiving a fabric 6 to be produced, and guide and tensioning devices (not shown) for the warp threads 4 and a reed 7 are arranged. In the side walls 1 and 2 there is also a main shaft 10 which can be driven via an electric motor 8 and a clutch 9 and from which the drives for the mechanical functions of the weaving machine. On the side cheek 1, a weft mechanism 11 and a multi-weft device 12 and a frame 13 for weft thread spools 14 arranged outside the shed are fastened, from each of which a weft thread 15 is drawn off, which is inserted into the shed by a weft insertion means, as shown, a projectile 16 the reed 7 is struck on the fabric 6. The projectiles 16 are each fired by the firing mechanism 11 against a catching mechanism 17 which, together with a control device 18, is arranged on the side cheek 2. The multi-weft device 12, in the example shown a four-weft device, feeds one of four weft threads 1-5 to the projectile 16 for a weft insertion in a manner still to be described, in accordance with a predetermined weft repeat (color repeat). Instead of projectiles 16, other entry means, for example a gripper belt, gripper bars or a fluid entry means, can also be provided.

According to FIG. 2, the multi-weft device 12 contains a drive device 20 that can be influenced via a single servomotor 50, in the embodiment shown a stepper motor, and a changer element 21 that can be adjusted via this, with four thread transmitters 22a, 22b, 22c and 22d, in which four weft ends 15a, 15b , 15c and 15d are held. The drive device 20 contains two rod-shaped drive parts 23 and 24, each of which is coupled to a rod-shaped output part 28 via an energy accumulator 25 or 26 and a summing gear 27. The output part 28 is articulated on a pivot lever 30 connected to the changer element 21, by means of which the changer element 21 is held pivotably about a stationary axis 31. The changer element 21 has four notches 32a, 32b, 32c and 32d for receiving one Locking roller 33 is provided, which is arranged on a lever 34 pivotable about an axis 35. The lever 34 is connected via a rod 36 to a guide pin 37 which engages in a control groove 38 of a grooved washer 39. The grooved washer 39 is fastened on a shaft 41 which is driven at a speed corresponding to the number of weft of the weaving machine.

As can be seen in particular from FIG. 3, the drive device contains a drive shaft 44 which is mounted in a housing 43 and on which two cams 45 and 46 and a gearwheel 47 are attached in a rotationally fixed manner. The cams 45 and 46 are offset from each other by an angle α = 90 ° around the axis of the drive shaft 44 and are designed with identical cam tracks, each of which has two circular sections, one of which has a radius r over a quadrant of the cam plate 45 and 46 runs and the other runs with a larger radius R over the diametrically opposite quadrant of the relevant cam 45 or 46. The gear 47 is in engagement with a pinion 48 of the servomotor 50 which is flanged to the housing 43. In a modified embodiment, the drive shaft 44 can also be coupled directly to the shaft of the servomotor 50. The cams 45 and 46 each interact with a rocker arm 51 and 52, which is articulated on one of the drive parts 23 and 24. The rocker arms 51 and 52 are pivotally mounted on an axis 49 mounted in the housing 43 and are each held against one of the cam plates 45 and 46 by means of guide and clamping means, not shown. Instead of the cam 45 and 46 shown in simplified form in FIG. 3, two corresponding pairs of double cams can be provided, each of which cooperates with a pair of rollers arranged on the associated rocker arms 51 and 52, respectively.

The rocker arms 51 and 51 can be adjusted back and forth via the cams 45 and 46 each about the axis 49 between an end position 51b or 51a shown in full lines in FIG. 2 and an end position 51a or 51b indicated by dash-dotted lines and in each of these End positions ascertainable. As can be seen in particular from FIG. 3, four combinations of the end positions of the rocking levers 51 and 51 are determined by four different angular positions of the cams 45 and 46, each offset by 90 ° from one another, each of which via the drive part 13 or 14 and the associated one Energy store 15 or 16 is coupled to a swivel arm 53c or 54c of a three-armed lever 53 or 54.

The levers 53 and 54, as parts of the summing gear 17, are each pivotably mounted on the machine frame about a fixed axis 55 and are coupled to one another via a balance lever 56, which, according to the illustration, is articulated at one end to an arm 53b of the lever 53 pointing away from the housing 43 and to the the other end is articulated on an arm 54a of the lever 54 pointing towards the housing 43. At an articulation point 57 which the distance between these articulation points in a predetermined ratio, e.g. 2: 1, divided, the output part 18 is articulated on the balance lever 56. Pistons 58 are further articulated on the arms 53a and 54b of the levers 53 and 54, each of which is guided in a cylinder 60 which contains a damping liquid, e.g. Contains oil.

For more information on the structure and operation of the energy storage 15 and 16, the summing gear 17 and the damping device, which are not the subject of the present invention, reference is made to the aforementioned DE-PS 17 10 356.

In the angular position of the cams 45 and 46 shown in FIG. 3, the upper end of the rocker arm 51 is held in the right end position 51b (FIG. 2) and the upper end of the rocker arm 52 in the left end position 52a. Correspondingly, with relaxed energy accumulators 25 and 26, the lever 53 is held in an operating position inclined to the right, and the lever 54 is held in an operating position inclined to the left, so that the balance lever 56 assumes its lowest position 56d as shown (FIG. 4) which corresponds to the position of the changer element 21 shown in FIG. 3, in which the thread take-up 22d assumes the thread transfer position.

Via the control motor 50, which can be controlled via the control device 18 in accordance with a program predetermined by the shot or color repeat, the cams 45 and 46 can be adjusted in both directions of rotation by 90 ° or 180 ° from a given angular position and in the new angular position noticeable. If the cams 45 and 46 are adjusted clockwise, for example from the angular position shown in FIG. 3 and 90 °, the rocker arm 52 is pivoted into the position 52b (FIG. 2), while the rocker arm 51 maintains its position 51b. When the changer element 21, as shown in Fig. 2, is blocked by the locking roller 33, the lever 54 is held in its operating position shown in Figs. 2 and 3, inclined to the left, in a known manner, for example in DE-PS 17 10 356 described manner, by tensioning a spring element in the associated energy accumulator 26, the adjusting force of the drive part 24 is stored. As soon as the locking roller 33 is pivoted out of the incision 32d in the corresponding angular position of the grooved disk 39 allowing the thread transfer and thus the changer element 21 is released, the lever 54 is moved over the Relaxing energy accumulator 26 is pivoted from the illustrated operating position, which is inclined to the left, into an operating position which is congruent with the operating position of the lever 53 according to FIG. 3, the balance lever 56 being set in a position inclined to the right 56c (FIG. 4), in which it runs essentially parallel to the arms 53a, 53b and 54a, 54b of the levers 53 and 54, the changer element 21 being pivoted via the abrasion part 28 into a position in which the pivot lever 30 is in a position 30c (FIG. 4) arrives, the incision 32c receives the blocking roller 33 moved back into the locking position and the thread feeder 22c is held in the thread transfer position.

If the cams 45 and 46 are adjusted 90 ° counterclockwise from the angular position shown in FIG. 3, the rocker arm 51 is pivoted into the position 51a (FIG. 2), while the rocker arm 52 remains in the position 52a shown. Accordingly, when the changer element 21 is unlocked in the manner described, the lever 53 is adjusted from the position inclined to the right in FIG. 3 to an operating position congruent with the position of the lever 54 and inclined to the left in FIG. 3, so that its arms 53a and 53b run parallel to the arms 54a and 54b of the lever 54 and the balance lever 56 reaches a corresponding position 56b inclined to the left (FIG. 4). Correspondingly, the changer element 21, via the driven part 58 and the pivoting lever 30 pivoted into a position 30b, reaches a position in which the incision 32b receives the locking roller 33 and in which the thread transmitter 22b is held in the thread transfer position.

In a corresponding manner, the cams 45 and 46 can be moved from the angular position according to FIG this angular position offset by 180 ° can be adjusted, the levers 51 and 52 each being pivoted into the opposite end position 51a or 52b (FIG. 2). Accordingly, when the changer element 21 is unlocked, the levers 53 and 54 are each pivoted into the oppositely inclined operating position, the balance lever 56 reaching its uppermost position 56a (FIG. 4). Correspondingly, the changer element 21, via the driven part 58 and the pivoting lever 30 pivoted into a position 30a, reaches a position in which the incision 32a receives the locking roller 33 and in which the thread transmitter 22a is held in the thread transfer position.

With the arrangement described, the changer element 21 can be extremely briefly from each of its four defined operating positions - by a quarter turn of the drive shaft 44 carrying the cams 45 and 46 in one or the other direction of rotation or by half a turn of the drive shaft 44 - in each of the three other operating positions can be adjusted. In particular, the actuating motor 50, which can be controlled independently of mechanical transmission means, ensures that the drive device 20 responds quickly and independently of the respective position of the main shaft 10 of the weaving machine. In cooperation with the force accumulators 25, 26, which allow the parts to be moved for the weft thread change to be preset independently of the respective position of the changer element 21, and with the damping device associated with the summing gear 27, the pistons 58 of which have precisely adjustable stops for the levers 53 and 54 form, the drive arrangement described in a simple manner compared to previous versions achieves an actual reduction in the response time of the multi-weft device and thus enables an increase in the weft insertion numbers of the weaving machine. This is due to the relatively large Parts of the drive device 20 which interact with each other, but can be precisely adjusted by the damping device, even when using a servomotor 50 designed for relatively large steps in a correspondingly simple, robust and inexpensive construction, an exact positioning of the changer element 21 corresponding to the respectively selected shot or color repeat guaranteed.

5 and 6, a drive device 62 can contain two coupling parts in the form of eccentric discs 63 and 64, to which the drive parts 23 and 24 are articulated directly. The eccentric disks 63 and 64 are each connected in a rotationally fixed manner to the drive shaft 44 mounted in the housing 43 or to a shaft journal 44a coaxial therewith and also via a crank journal 65 or 66 to a common central eccentric disk 67. The drive parts 23 and 24 are articulated on the crank pins 65 and 66, which are each arranged at an equal distance from the axis of the drive shaft 44 in the circumferential direction by an angle α = 90 °. Via the servomotor 50, which can be directly coupled to the drive shaft 44 via a gear or, as shown in FIG. 6, the eccentric disks 63, 64 and 67 are also in this embodiment between four defined angular positions, each offset by 90 ° adjustable and ascertainable in each of these angular positions.

In the angular position shown in FIG. 5 of the eccentric disk 67 connected to the two crank pins 65 and 66, the levers 53 and 54 of the summing gear 27 are held in the operating positions according to FIG. 3, in which the balance lever 56 assumes its lowest position 56d. It is useful if the articulation points of the drive parts 23 and 24 on the levers 53 and 54 in the two operating positions lie in a plane E running through the axis of the drive shaft 44 and when the crank pins 56 and 66 are each held in the same position by this plane E in the angular position of the eccentric disk 67 shown.

The eccentric disk 67 connected to the eccentric disks 63 and 64 can be moved from the angular position according to FIG. 5 by a quarter-turn clockwise to an angular position 67a according to FIG. 5a, or by a quarter-turn counterclockwise into an angular position 67b according to FIG. 5b or by one half a revolution of the drive shaft 44 can be adjusted into an angular position 67c according to FIG. 5c.

5a, the lever 54 remains in the position shown in FIG. 5, while the lever 53 - with the changer element 21 unlocked in the manner already described - from the position shown into a congruent one to the lever 54 , operating position inclined to the left and thus the balance lever 56 is moved into position 56b (FIG. 4). Correspondingly, in the angular position 67b according to FIG. 5b, the lever 54 is adjusted with the changer element 21 unlocked into an operating position which is congruent with the position of the lever 53 and is inclined to the right, the balance lever 56 reaching the position 56c (FIG. 4). Likewise, in the angular position 67c according to FIG. 5c, both levers 53 and 54 are moved from the operating positions according to FIG. 5 to the opposite inclined operating position when the changer element 21 is unlocked, the balance lever 56 moving into the position 56a (FIG. 4).

5 and 6 is thus in each of the four operating positions with the Balance lever 56 connected changer element 21 each of the three other operating positions of this changer element 21 adjustable by a quarter turn of the drive shaft 44 in one or the other direction of rotation or by half a turn of the drive shaft 44.

The rocker arms 51 and 52, which are driven according to FIG. 3 via the cam disks 45 and 46, can, as shown in FIG. 7, be coupled to the driven part 58 via a summing gear 77, which has two comb levers 73 and 74, each pivotable about a fixed pin 75 contains, to which one of the drive parts 23 or 24 is articulated. The comb levers 73 and 74 are each designed with a sprocket segment 70 and each adjustable between an operating position 73b or 74a shown in full lines and an operating position 73a or 74b shown in broken lines, the operating positions 73b and 74a depending on the position shown in FIG. 7 shown end position 51b and 52a of the relevant rocker arm 51 and 52 respectively, while the operating positions 73a and 74b each correspond to the opposite end position 51a and 52b according to FIG. 2. The ring gear segments 70 of the comb levers 73 and 74 are each in engagement with a toothed wheel 71 or 72, which is mounted on a fixed pin 76. The gear wheels 71 and 72 are each provided with an eccentrically arranged crank pin 78 or 80, the gear ring segments 70 and the gear wheels 71, 72 being matched to one another in such a way that a pivoting of the comb lever 73 between the two operating positions (end positions) 73b and 73a or the comb lever 74 between the operating positions (end positions) 74a and 74b each corresponds to half a revolution of the gear 71 and 72 in question. The gear wheels 71 and 72 are coupled to the driven part 58 via the balance lever 56, which is articulated on one of the crank pins, as shown on the crank pin 78, and on another crank pin 80 is slidably guided via a longitudinal slot 81. 7, the gears 71 and 72 are set such that in the illustrated operating position 73b and 74a of the comb lever 73 and 74, the crank pins 78 and 80 each assume their bottom dead center position, the balance lever 56 being the deepest shown Position 56d (Fig. 4). Correspondingly, in the operating position 73a or 74b of the comb lever 73 or 74, which is inclined in the opposite direction, the crank pins 78 and 80 each assume their top dead center position, the balance lever 56 being held in the uppermost position 56a (FIG. 4). Correspondingly, the intermediate positions of the balance lever 56, as described in connection with FIG. 3, are achieved by holding the balance lever 56 in the position 56b (FIG. 4) in the operating positions 73a and 74a of the comb lever 73, while it sets itself in the operating positions 73b and 74b of the comb levers 73, 74 in the position 56c. In this embodiment as well, through the appropriate combination of the end positions of the rocker arms 51 and 52, the summing gear 77 makes four precisely definable operating positions of the driven part, each determined by one of the four possible combinations of the lower and upper dead center positions of the crank pins 78 and 80 58 and the associated changer element 21 achieved. Accordingly, the damping device provided in the embodiment according to FIGS. 2 and 3 can optionally be omitted.

Instead of a stepper motor as described above, other types of servomotors can also be used, e.g. a frequency controlled DC motor, a hydraulic motor or a pneumatic motor

Claims (4)

Weaving machine with a multi-weft device (12) for changing the weft thread to be inserted, which contains a changer element (21) which can be controlled by the loom drive and has a plurality of thread feeders (22a, 22b, 22c, 22d), each movable into a thread transfer position, and a drive device, each of which has two between two Defined operating positions adjustable drive parts (23, 24), two associated with them, for temporary storage of the respective adjusting force initiated via this force storage (25, 26) and one with the changer element (21) couplable output part (28), which contains the energy storage (25, 26) are adjustably connected between four defined operating positions by means of a summing gear (27, 77), characterized in that the drive device (20, 62) has a servomotor (50) and one which can be driven by it, in four each at 90 ° to one another contains offset angular positions lockable drive shaft (44) with two coupling parts, which are offset from one another by an angle α = 90 ° about the axis of the drive shaft (44) and are each coupled to one of the drive parts (23 or 24). Weaving machine according to claim 1, characterized in that the coupling parts are formed by essentially identical cams (45 and 46) connected in a rotationally fixed manner to the drive shaft (44) and in that the drive parts (23 and 24) each have one for cooperation with one of the cams (45 and 46) certain rocker arms (51 and 52) are articulated. Weaving machine according to claim 1, characterized in that the coupling parts are formed by eccentric discs (63 and 64) which are connected in a rotationally fixed manner to the drive shaft (44) and which are at an angle α = 90 ° to one another offset articulation points (65 or 66) for each of the drive parts (23 or 24) are executed. Weaving machine according to claim 1 or 2, characterized in that the summing gear (77) has two ring gear segments (70) each pivotable about a fixed axis (75) and each coupled to one of the drive parts (23 or 24) and two driven each via these Contains gear wheels (71 and 72) which can be rotated by 180 ° about a fixed axis (76), which are each provided with a crank pin (78 and 80) which can be locked in a lower and an upper dead center position and which are connected to the crank pin (78 and 80) articulated balance lever (56) are coupled to the operating part (28), the four defined operating positions of which are determined by one of the four combinations of the lower and upper dead center positions of the crank pins (78 and 80).

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