EP0615013A1 - Wide, dummy shuttle loom - Google Patents

Abstract

The invention relates to a broad-face projectile loom, especially for the production of flat-woven paper-machine coverings or other industrial fabrics with warp and weft threads, preferably having widths of more than 6 m, with a sley (27, 15) oscillating to and fro in the direction of the warp threads, a weft mechanism (1) and a catching mechanism (3) for projectiles (56) as well as guide elements (50) for guiding the projectiles being provided, the guide elements (50) being designed to move synchronously with the sley (27, 15), and to a method for moving guide elements for projectiles on broad-face looms with an oscillating sley which move synchronously with the sley, a second movement being superposed on the guide elements. <IMAGE>

Description

The invention relates to a wide weaving machine, in particular for the production of flat woven paper machine clothing or other technical fabrics with warp and weft threads, preferably with widths of more than 6 m, with a weaving sway oscillating in the direction of the warp threads, and a method for moving guide elements for Projectiles on wide weaving machines with swinging sley.

Weaving machines for the production of flat-woven paper machine clothing or similar technical fabrics, which are manufactured in widths of 6 - 12 m with high warp tensions and shop slinging forces of up to 5 to / m weaving width, are special weaving machines and cannot be compared with the category of textile weaving machines. Characteristic of the textile weaving machines are their narrow weaving width, their high number of wefts per minute and their light construction adapted to these conditions, which is made clear by the drive of the sley, which is usual with these looms, by means of an oscillating shaft on which the shop supports carrying the sley sit and synchronize with it move. In these machines, this oscillating shaft is driven by a cam mechanism (FIG. 10). While the above-described special weaving machines according to the current state of the art with a number of weft of about 50 wefts / min. work, the textile weaving machines run with mechanical weft insertion several 100 weft / min. and weaving machines with pneumatic weft insertion even up to 1000 weft / min. and more.

An important reason for the relatively low number of wefts in the special weaving machines is that the weft insertion is currently carried out by means of so-called rapier weavers, which in terms of their dimensions and their mass - which not only accelerate but also have to be brought to a standstill safely and accurately - larger weft numbers not allow.

Attempts have therefore also been made to miniaturize the rapier shooters. However, these measures were limited by the fact that their dimensions and weight-reduced gripper shooters, which were shot through the shed without guidance, were unstable and in extreme cases flew out of the shed.

An embodiment of a miniaturized rifle shooter has been described by the German document DT 15 35 561.

The unstable rifle flight also limited the rifle speeds and thus the performance increase of these machines.

From the German patent DE-A1 32 42 121 it can be seen, inter alia, that the disadvantages of the unstable rifle barrel are to be eliminated according to the invention by providing guide elements for the shooter. Although this measure also prevented the shooter from flying out, there are still disadvantages to this system in that the shooter rolls along the warp threads of the lower shed, which is supported on the sley. This affects in the case of a dirty sub-compartment or when the weaving drawer is overpacked, ie if not all of the warp threads of the sub-compartment lie perfectly next to each other, but partly one above the other, brakes heavily on the shooters and thus also impairs the increase in performance.

The invention is therefore based on the object of designing a wide weaving machine which eliminates the aforementioned disadvantages which have hitherto hindered an increase in performance in these special weaving machines.

This problem was solved by the measure that a shot and catch mechanism for projectiles and guide elements for guiding the projectiles are provided, the guide elements being designed to move synchronously with the sley. Surprisingly, on the basis of a weft insertion system known from textile weaving machines, an increase in performance can also be achieved with wide weaving machines.

In an embodiment of the invention it is provided that a second movement is superimposed on the guide elements. As a result, the guide elements, which are necessary for guiding the projectiles, emerge from the compartment after the weft entry and thus no longer interfere with the striking of the reed against the fabric edge. In this context, it is therefore a movement component which is superimposed essentially in the direction perpendicular to the warp threads in addition to the usual weaving movement, which takes place essentially in the direction of the warp threads on a circular arc.

This movement, which additionally causes the guide elements to emerge from the compartment, can be achieved by superimposing a second movement on the sley. If the sley also moves synchronously in the vertical direction, the guide elements can be firmly attached to the sley so that they do not have to move relative to the sley.

The masses which have to be accelerated and decelerated again with this additional movement component are advantageously reduced if the guide elements are fastened to a guide rail which can be pivoted about a pivot point which is arranged on the sley.

In terms of design, the additional movement component can also be impressed, despite the higher mass of the sley, if the guide elements are firmly attached to the sley, the sley being designed to be pivotable about a fulcrum, which is itself pivoted on a lever with a fixed fulcrum, the lever is preferably designed to be driven by a cam.

The required precision in the interaction of the various movement components can be achieved most favorably if the superimposed movements are designed to be derived from a common drive shaft.

This can be achieved in that the drive shaft is designed as a crankshaft with connecting rods as a drive for the sley and preferably has bearing rings for the guide carrier rail. The The guide support rail thus has a pivot point on the sley and is connected via a joint to a bearing ring which can be freely rotated on the crankshaft and which serves as a fixed attachment point.

So that the quality of the fabric is improved, it is provided that the sley has a reed, which is arranged at a front reversal point of the sley perpendicular to the center shed plane. The stop therefore takes place in the direction of the warp threads.

In order to be able to master the mechanical problems that arise as a result of the large weaving widths, high lifting forces, large masses to be accelerated and decelerated, it is advantageous if the sley has more than two drawer supports, the drawer supports being part of a kinematic quadrilateral joint in the drive mechanism are arranged with crankshaft.

Characterized in that one or more cam disk drives are provided as the drive for the crankshaft, which are preferably arranged symmetrically to the machine center, in particular are designed as complementary cam disk drives, the machine can be built in the required width without the movements being precise due to torsion of the

Drive shafts suffer. The measure that the movements of the sley and the guide elements are designed to be mechanically synchronized also serves to precisely control the time of the different movements, in particular one connecting the drives to synchronize the cam mechanism Synchronous shaft is provided.

It serves the same purpose if the movement of the guide elements is derived mechanically, preferably by means of a joint system, from the movement of the sley. For this purpose, the guide elements can be articulated via a lever system on the one hand at a pivot point which is fixed relative to the machine frame and on the other hand at a second pivot point which moves with the sley. The drive is thus carried out via the sley.

In order to correct errors and for band-free weaving, it is advantageous if the weaving machine can be separated from the weft and catch mechanism by means of a coupling and is designed to be able to reverse. In this case, the fabric is moved in the reverse movement sequence without weft insertion in the direction opposite to the weaving direction.

In particular for the movement of the guide elements, linear drives, in particular piston-cylinder units, can advantageously be provided as a drive for the superimposed movement.

In a further embodiment of the invention it is provided that the weft and catch mechanism is designed to swing with the sley.

The procedural task is solved in that a second movement is additionally superimposed on the guide elements. This method makes it possible to provide the weaving movement independently of the required movement of the guide elements. The amplitude of the weaving movement can thus be kept as small as possible, which is the same

Productivity, i.e. same number of shots, lower accelerations and decelerations of the masses involved. The mass forces acting on the machine are consequently reduced, which results in an overall smoother machine run. On the other hand, with the same load, the number of shots can be increased accordingly, so that productivity is improved. Finally, the direction of the stop can be designed independently of the exchange movement of the guide elements. The stop is in the direction of the warp threads. In this case, the stop at a reed directed perpendicular to the plane of the warp threads takes place relatively close to its clamping point, so that the high stop forces can be controlled by the short clamping length of the reed.

The method according to the invention can also be implemented by superimposing a second movement on the sley. The guide elements can then be firmly attached to the sley.

The masses to be moved in wide weaving machines can be reduced if the otherwise large and bulky guideways for guiding the rapier shooters are replaced by guide elements for projectiles by using projectile weft and catch mechanisms on wide weaving machines of a width of more than 6 m.

Further advantages, details and features essential to the invention result from the following description of a preferred embodiment of the invention with reference to the attached figures, the same parts being provided with the same reference numerals.

The preferred embodiments are described in particular below.

Fig. 1

eine Draufsicht auf eine Projektilwebmaschine mit den relevanten Einzelheiten und ihre Positionierung in schematischer Darstellung,

Fig. 2

einen Schnitt durch die erfindungsgemäße Projektilwebmaschine gemäß Schnittlinie II-II aus Figur 1,

Fig. 3

eine perspektivische Darstellung eines Antriebssystems für die Ladenbewegung

Fig. 4

eine Schnittzeichnung durch eine erfindungsgemäße Weblade mit Darstellung eines Projektilführungssystems in hinterer Totpunktlage,

Fig. 5

eine Schnittzeichnung durch die Weblade mit Darstellung des Projektilführungssystems in vorderer Totpunktlage,

Fig. 6

eine alternative Ausgestaltung eines Antriebs für die Führungselemente mittels elektrischer, pneumatischer oder hydraulischer Mittel,

Fig. 7

eine bevorzugte Anordnung der Kupplungsmittel für ein feststehendes Schuß- und Fangwerk,

Fig. 8

eine alternative Ausführungsform eines Antriebes für an der Weblade befestigte Projektilführungselemente,

Fig. 9

eine alternative Anordnung eines Schuß- und Fangwerkes, welches sich mit der Weblade bewegt und

Fig. 10

einen typischen Webladenantrieb für Textilmaschinen mit einer Schwingwelle und einem Kurvenscheibenantrieb in schematischer Darstellung.

Show it:

Fig. 1

a plan view of a projectile weaving machine with the relevant details and their positioning in a schematic representation,

Fig. 2

2 shows a section through the projectile weaving machine according to the invention along section line II-II from FIG. 1,

Fig. 3

a perspective view of a drive system for the shop movement

Fig. 4

2 shows a sectional drawing through a weaving drawer according to the invention, showing a projectile guidance system in the rear dead center position,

Fig. 5

2 shows a sectional drawing through the weaving shed showing the projectile guidance system in the front dead center position,

Fig. 6

an alternative embodiment of a drive for the guide elements by means of electrical, pneumatic or hydraulic means,

Fig. 7

a preferred arrangement of the coupling means for a fixed shooting and catching mechanism,

Fig. 8

an alternative embodiment of a drive for projectile guide elements attached to the sley,

Fig. 9

an alternative arrangement of a weft and catch mechanism, which moves with the sley and

Fig. 10

a typical weave drive for textile machines with an oscillating shaft and a cam drive in a schematic representation.

For a better understanding of the difference to wide weaving machines, FIG. 10 first shows a typical shop drive for unprotected textile weaving machines.

The reed a and the guide teeth b are fastened together to a drawer c, which extends across the entire weaving machine width.

The load carrier c is firmly connected to the multiple supports d, which in turn are all firmly connected to the oscillating shaft e.

Via a cam drive f with a fulcrum in g and a two-armed roller lever h, which is also firmly connected to the oscillating shaft e, the oscillating shaft e and the elements a, b, c and d attached to it are given an angularly synchronous movement.

This relatively low-mass shop drive system is due to the much higher demands on wide weaving machines and the considerable kinematic energies required here for the Shop stop practically not applicable.

The projectile weaving machine according to the invention shown in FIG. 1 has a left outer frame wall 2 carrying the weft mechanism 1 and a right outer frame wall 4 carrying the catch mechanism 3. Between these outer frame walls 2 and 4 there is a main drive 5 on the left and a further main drive 6 on the right side of the machine and between them, depending on the machine width, more than two middle frame walls 7.

As can be seen in FIG. 2, the outer frame walls 2 and 4, the main drives 5 and 6 and the middle frame walls 7 are connected to one another via tubular longitudinal connectors 8 and breast beam 9 and form the so-called frame.

A chain 11 coming from a warp beam 10 is deflected over a coating tube 12, through heald eyes 13 of heald frames 14 through a reed 16 attached to a saddle carrier 15 and via a height-adjustable circular rail 17 onto the breast tube 9. The shedding is done by means of known dobby machines. The weft insertion at right angles to the warp thread direction creates the fabric or fabric formation in the front dead center position of the reed 16 at the front edge.

The goods formed from here run over the round rail 17 and deflected through the breast tree tube 9 into the roller system of a fabric take-off, consisting of the rollers 18, 19, 20, 21 and the take-off gears 22 and is corresponding to the respective weft density deducted. The crankshaft 23, which swings back and forth over the entire weaving machine width, is supported on both sides between the chest boom tube 9 and the package of the shafts 14.

The crankshaft is shown in perspective in FIG. 3 with its drive. Crank arms 25 with pivot point 26a are rotatably articulated in the cranked portions 24 of crankshaft 23 and transmit the movements imposed on them at pivot point 26 to shop supports 27 which in turn move about pivot point 28 (FIG. 2).

A weaving rack 15 (FIGS. 4 and 5) is fastened on the shop supports 27 and swings back and forth with it. During the rest in the rear dead center position of the sley 15, the weft is inserted and in the front dead center position the weft stop on the fabric edge. According to the embodiment, the crankshaft 23 is driven via the main gears 5 and 6 (FIG. 1), one of which is shown schematically in FIG. 3 without a housing.

The preferably selected three-phase motor 29 transmits its movement via a V-belt pulley 30 and a V-belt drive 31 to a detachable drive pulley 32 which is arranged on the input drive shaft 33 of the main drive.

Via a pinion 34, which is fixedly connected to the drive shaft 33, and intermediate edges 35 and 36, the drive is carried out on cam disk wheel 37, which is connected to the complementary cam disk shaft 38, to the complementary cam disks 39 fastened thereon and 40, which in turn cause the toothed segment 41 to oscillate via the arms 42 and 42a located on the gear segment 41 and the cam rollers 43. The pendulum movement is transmitted to the crankshaft output point 45 via a wheel 44 which is in engagement with the toothed segment 41. The connection of the individual crank strokes in accordance with the modular design takes place by means of the shaft couplings 46. The synchronization of the main drives 5 and 6 arranged to the right and left of the machine center takes place via a synchronous shaft 47 running fast in relation to the camshaft shaft, which connects both transmissions 5 and 6 via coupling 48.

FIGS. 4 and 5 show the sectional drawer 15 fastened over the entire weaving width and fastened to the shop supports 27 with the clamped reed 16. The weaving rack is also the basis for a projectile guide system 49, consisting of guide elements 50, a guide rail 1, a transmission lever 52 with its pivot points 53 and 54, and a bearing ring 55 for the pivot point 54 in plate 57, which is movably seated on the crankshaft 23. The bearing ring 55 is freely rotatable on the crankshaft 23. The guide system 49 with the guide elements 50 fastened to the guide carrier rail 51 extends over the entire weaving width. In the rear shop position shown as FIG. 4, the weft is inserted by means of projectile 56 (FIG. 9). For this purpose, it is necessary for the guide elements 50 to be absolutely congruent with the outlet channel of the firing unit 1 (FIG. 1). This is made kinematic by the Articulated arrangement of the guide system is achieved, wherein, in order to stabilize the end position of the guide elements 50, supporting legs of the guide support rail 51 are brought into abutment by means of spring means (not shown) on the surface of the tray 15 parallel to the leg.

After the weft has been inserted, which takes place when the sley is stationary, the sley carrier 15 now swings into the front dead center position shown as FIG. 5 and connects the weft thread. The projectile guidance system 49 with the guide elements 50 executes a relative movement to the sley 15 and the reed 16 by the arrangement of the articulation points 53 and 54 to the fulcrum of the crankshaft 53 such that the guide elements 50 are in the front dead center position before the reed 16 stops have inevitably moved out the lower compartment of the warp threads.

Another embodiment is shown in FIG. 6. Support bearings 79 and pivot points 73 for movement levers 75 are arranged on the weaving rack 15. At the pivot point 78 of the support bearing 79, a linear drive 77 is supported, which can consist, for example, of a piston-cylinder unit or a magnetic drive. At the other end, drive 77 engages pivot point 76 of movement lever 75. Via a machine control, not shown, the drives 77 generate a lifting movement, which causes the guide elements 50, which are fixedly connected to the movement levers 75 via the guide support rail 51, to be in the shed at the time of the weft insertion and to be in place again after the weft entry before the loading stop move out of the shed.

Figure 7 shows schematically the arrangement of the coupling means for the shooting and catching mechanism, by means of which they can be separated from the main drives. The main drives 5 and 6 each have an output shaft 60 and 61 which run at a speed ratio of 1: 1 to the crankshaft shaft 38 (FIG. 3). The rotary movement of the output shafts 60 and 61 is transmitted via coupling means 62 and 62a to the weft mechanism 1 via chain drives 63 and to the catching mechanism 3 via chain drive 64.

Overload clutches 65 and 65a are preferably provided in this drive system.

FIG. 8 shows an alternative embodiment as an example. The guide elements 50 are fixedly connected to the weaving rack 15 and arranged in a fixed position relative to the weaving reed 16. The shop supports 27 are moved back and forth about the pivot point 28 via the crankshaft 23 and crank arms 25 in the manner described.

The pivot point 28 is located on a roller lever 66 which has its pivot point 67 in the bearing 68. By means of the complementary cam 69, which is seated on a drive shaft 70, the shop support 27 with the elements 15, 16 and 50 attached to it is lowered so far after the weft insertion that the guide elements 50 are no longer in the area of the shed 13 at the shop stop. For the position of the weft insertion in the rear shop position, the shop support 27 with the elements 15, 16 and 50 attached to it is raised again accordingly.

FIG. 9 schematically represents an embodiment variant in which the firing mechanism 1 and the catching mechanism 3 are fixed are connected to the weaving rack 15 and swing back and forth with it.

Claims (18)

Wide weaving machine, in particular for the production of flat-woven paper machine clothing or other technical fabrics with warp and weft threads, preferably with widths of more than 6 m, with a weaving sway oscillating in the direction of the warp threads, characterized in that a weft (1) and a catch mechanism (3) for projectiles (56) and guide elements for guiding the projectiles (56) are provided, the guide elements (50) being designed to move synchronously with the sley (27, 15). Wide weaving machine according to claim 1, characterized in that a second movement is superimposed on the guide elements (50). Wide weaving machine according to claim 1 or 2, characterized in that a second movement is superimposed on the sley (27, 15). Wide weaving machine according to claim 1, 2 or 3, characterized in that the guide elements (50) are fastened to a guide rail (51) which can be pivoted about a pivot point (53) which is arranged on the sley (27, 15). Wide weaving machine according to claim 1, 2, 3 or 4, characterized in that the guide elements (50) are fixedly attached to the sley (27, 15), the sley (27, 15) being designed to be pivotable about a pivot point (28), which is itself pivotably articulated on a lever (66) with a fixed pivot point (67), the lever (66) preferably being designed to be driven by a cam disc (69, 70). Wide weaving machine according to claim 1, 2, 3, 4 or 5, characterized in that the superimposed movements are designed to be derived from a common drive shaft (23). Wide weaving machine according to claim 6, characterized in that the drive shaft is designed as a crankshaft (23) with connecting rods (25) as a drive for the sley (27, 15) and preferably has bearing rings (55) for the guide carrier rail (51). Wide weaving machine according to claim 1, 2, 3, 4, 5, 6 or 7, characterized in that the weaving drawer (27, 15) has a weaving reed (16) which is arranged in a front reversal point of the weaving drawer perpendicular to the central shed plane (13a) . Wide weaving machine according to claim 1, 2, 3, 4, 5, 6, 7 or 8, characterized in that the weaving shutter (27, 15) has more than two drawer supports (27), the drawer supports (27) being part of a kinematic Quadrilateral joints (26, 26a, 28, 67) are arranged in the shop drive with crankshaft (23). Wide weaving machine according to claim 1, 2, 3, 4, 5, 6, 7, 8 or 9, characterized in that one or more cam disk drives are provided as drive for the crankshaft, which are preferably arranged symmetrically to the machine center, in particular are designed as complementary cam disk drives. Wide weaving machines according to claim 1, 2, 3, 4, 5, 6, 7, 8, 9 or 10, characterized in that the movements of the sley (27, 15) and the guide elements (50) are mechanically synchronized, whereby for synchronization the cam mechanism is provided in particular with a synchronous shaft (47) connecting the drives. Wide weaving machine according to claim 1, 2, 3, 4, 5, 6, 7, 8, 9, 10 or 11, characterized in that the movement of the guide elements (50) mechanically, preferably by means of a joint system, from the movement of the weaving sley (27 , 15) is derived. Wide weaving machine according to one or more of the preceding claims, characterized in that the weaving machine can be separated from the weft (1) and catch mechanism (3) by means of a coupling (62, 62a) and can be returned. Wide weaving machine according to one or more of the preceding claims, characterized in that linear drives (77), in particular piston-cylinder units, are provided as the drive for the superimposed movement. Wide weaving machine according to one or more of the preceding claims, characterized in that the weft (1) and catch mechanism (3) with the weaving shutter (27, 15) is designed to oscillate. Method for moving guide elements for projectiles on wide weaving machines with a vibrating sley that move synchronously with the sley, characterized in that a second movement is superimposed on the guide elements (50). A method according to claim 16, characterized in that a second movement is also superimposed on the sley. Use of projectile weft and catch mechanisms on wide weaving machines with a width of more than 6 m.

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