EP0908547A1 - Weft inserting device in a loom and loom with such a device - Google Patents

Abstract

The weft insertion device has a cam gear unit (2) with two parallel disks (3,4). The drive (6) is linked to the weft inserter (1) on one side and has two roller bodies (8) at the other side to roll without play on the disks and force a defined movement pattern on the weft inserter. The weft inserter is a beating lever to strike a projectile which carries the weft through the shed. The angular speed of the lever movement is increased by a unit in the drive chain between the cam gearing and the lever. The unit is a symmetrical or asymmetrical quadrilateral linkage for swing angles which can be freely selected, with a lever angle speed adjustment. The drive mechanism has a swing roller assembly, with rollers of different diameters, and at equal or unequal gaps from the swing axis. The disk and roller assemblies are structured to give a positive or force movement and force transmission. An electro-motor, preferably as a geared motor, with a brake clutch coupling, has a drive link to the cam gear. An energy store, as a torsion spring rod in a fixed mounting at one end and connected at the other end to the weft inserter or the control disks, stores the movement energy of the weft inserter to reduce the drive torque. The disks can form a component group unit, as an oscillating mass to store energy. The weft inserter can be a lance strip, with a wheel which is connected to the cam gear. The assembly is a component group of the loom, with a brake mechanism at the cam gear. A reduction gearing is between the main shaft and the cam gear, using elliptical cogwheels to deliver different speed levels within a rotation and relieve the cam gear. The reduction gearing has a whole number reduction ratio, to raise the number of projectile striking actions relating to the reduction ratio.

Description

The invention relates to an insertion device for a Weft thread in a weaving machine according to the generic term of claim 1 and a loom with a such device.

For the entry of a weft thread e.g. two Drive systems for insertion devices are known on the one hand by means of a torsion bar spring Projectile looms and on the other hand by means of a Belt or a bar gripper drive at Rapier weaving machines.

Devices using the former system have a cam mechanism that with the Weaving machine drive and with the torsion bar spring is connected and a striking lever, which with the Torsion bar spring is connected. The torsion bar spring is tensioned by means of the cam mechanism and released to operate the striker.

This type of device has the disadvantages that the launch speed from the tension of the Torsion bar spring is dependent and for adjusting the Tension requires considerable effort only a small portion to accelerate the projectile the energy stored in the torsion bar spring is used up and a much larger proportion Braking in a braking device is lost, so that the efficiency is about 25% and that after the Release of the torsion bar spring of the striking lever from the Loom drive is separated, so within one Weaving cycle a longer period of time for weft insertion must be provided.

Devices using the second system, have a universal joint and a crank arm containing Gear on that with the loom drive and with an entry wheel is connected.

This type of device has the disadvantage that the gear is of complicated construction and is very expensive i.e. the transmission has a very large mass of fast moving parts. These parts limit it the efficiency of the device and need a lot a lot of energy for the operation.

The invention has for its object a Insertion device for a weft thread in one Improve weaving machine so that the above Disadvantages are eliminated.

This object is achieved with the characterizing features of claim 1 solved.

The advantages of the invention are that the Launch speed depends on the speed, that the residual energy is absorbed into the drive train and that the entry time or Entry distance can be specified precisely, and that the fast moving parts necessary for the energy consumption of the Device are responsible, designed very low mass can be.

Further advantages of the invention result from the dependent claims.

The invention is described below with reference to the enclosed Drawings explained.

Fig. 1

eine vereinfachte Darstellung einer Grundausführung eines Schlaghebelantriebes;

Fig. 2

eine Ausführungsform einer erfindungsgemässen Vorrichtung für eine Projektilwebmaschine in räumlicher Darstellung;

Fig. 3

einen Schnitt entlang der Linie III-III in Fig. 2;

Fig. 4a bis c

eine vereinfachte Darstellung des Schlaghebelantriebes gemäss Fig. 2;

Fig. 5

eine bevorzugte Ausführungsform einer erfindungsgemässen Vorrichtung in räumlicher Darstellung;

Fig. 6

eine vereinfachte Darstellung des Schlaghebelantriebes gemäss Fig. 5;

Fig. 7

eine Einzelheit "A" in Fig. 6 im grösseren Massstab;

Fig. 8

eine Einrichtung zum Leistungsausgleich der Vorrichtung;

Fig. 9

eine weitere Ausführungsform eines Kurvengetriebes;

Fig. 10

eine andere Ausführungsform eines Übersetzungsgetriebes;

Fig. 11

eine erste Ausführungsform einer erfindungsgemässen Vorrichtung für eine Greiferwebmaschine in räumlicher Darstellung;

Fig. 12

eine zweite Ausführungsform der Vorrichtung nach Fig. 11 und

Fig. 13

das Viergelenk in den Fig. 11 und 12 im grösseren Massstab.

Show it:

Fig. 1

a simplified representation of a basic version of a hammer lever drive;

Fig. 2

an embodiment of an inventive device for a projectile loom in spatial representation;

Fig. 3

a section along the line III-III in Fig. 2;

4a to c

a simplified representation of the impact lever drive according to FIG. 2;

Fig. 5

a preferred embodiment of an inventive device in a spatial representation;

Fig. 6

a simplified representation of the impact lever drive according to FIG. 5;

Fig. 7

a detail "A" in Figure 6 on a larger scale.

Fig. 8

a device for balancing the performance of the device;

Fig. 9

a further embodiment of a cam mechanism;

Fig. 10

another embodiment of a transmission gear;

Fig. 11

a first embodiment of an inventive device for a rapier weaving machine in a spatial representation;

Fig. 12

a second embodiment of the device of FIGS. 11 and

Fig. 13

the four-bar linkage in FIGS. 11 and 12 on a larger scale.

1 shows, for driving a Impact lever 1 applied a cam mechanism 2. The Transmission comprises two control disks 3, 4 on one Axis 5 are arranged non-rotatably and a Roller arrangement 6, which is non-rotatable on an axis 7 is arranged. The striking lever 1 is on the axis 7 non-rotatably arranged. The roller arrangement 6 comprises a carrier, which is connected to the axis 7 in a rotationally fixed manner is and two rollers 8 which are rotatable at a distance on the carrier are arranged so that the hammer 1 back and forth Float. Axes 5 and 7 are stationary arranged rigid bearings, so that the rollers 8 Roll on the tread without play. At this Design is the contact due to the fixed center distance the control discs 3, 4 and the rollers 8 secured and the forces become perpendicular to the point of contact transfer. Thus the connection between Control discs and roller arrangement form-fitting, so that the hammer 1 is positively controlled, i.e. one performs predetermined movement. Axis 7, 17 can be stored in elastic bearings to Intercept vibrations.

Reference is made to FIGS. 2 and 4a to c. The entry device in question contains the Impact lever 1, the cam mechanism 2, a kinematic Chain 10, on the one hand with the cam mechanism 2 and on the other hand is connected to the impact lever 1 and a geared motor 11 with a not shown Brake clutch unit. The two control disks 3, 4 can be formed as one piece as shown and have a hub 14. The control disks are on a drive shaft 15 attached to the Gear motor 11 is connected and form a Flywheel mass to increase the uniformity of the speed improve. The roller assembly 6 and the kinematic Chain 10 are non-rotatably connected by means of a hub 16 and arranged pivotably on an axis 17 as a unit, with the axle in rigid or elastic bearings is stored. The kinematic chain 10 forms one symmetrical, quasi u-shaped four-bar linkage with three one-armed levers 21, 22, 23. The first lever 21 is on one end with the axis 17 rotatably and at the other End via a joint 25 with the second lever 22 connected. The second lever 22 is on the other hand third lever 23 hinged, which in turn with the axis 26 is non-rotatably connected to which the striking lever 1 is attached.

3 show a greatly simplified representation an embodiment of the joint 25, with which the Hinge axis with respect to the articulated levers 21, 22 is adjustable. The joint 25 is a screw bolt formed with an eccentric section 28. For gearboxes subject to higher dynamic loads can be symmetrical introduction of force can be provided.

During operation of the weaving machine, the two control disks 3, 4 are driven by the geared motor 11. Because the roller arrangement is inevitably guided, a predetermined course of movement is given to the impact lever 1 due to the contour of the two control disks 3, 4 by means of the roller arrangement 6 and the kinematic chain 10. In this drive chain, the kinematic chain forms a fast transmission link in order to achieve the required launch speed. The gear ratio can be set or changed beforehand on the joint 25. The contours of the control disks 3, 4 are designed such that the movement sequence comprises an acceleration phase α ₁ , a braking phase α ₂ and a reset phase α ₃ (FIG. 4c).

4a shows the striking lever 1 in the position immediately before the start of the acceleration phase, a projectile 29 having already been arranged in the firing position. During the acceleration phase α ₁ , the projectile 29 reaches the launch speed. At this point, the braking phase begins and the projectile continues to fly freely (Fig. 4b). The launch speed is therefore dependent on the speed of the main drive shaft of the weaving machine. During the braking phase, which is advantageously chosen to be longer than the acceleration phase, the residual energy is absorbed by the drive train of the impact lever after the projectile has been fired.

The various weaving machine functions are described in Dependence of the angle of rotation of the main drive shaft controlled. The projectile must be open for the weft insertion accelerates the required launch speed be and the reed practically stand still, the Shot channel formed on the reed onto the trajectory of the Projectile. For those in question here standing device is the onset of Acceleration phase at a rotation angle of e.g. approx. 110 ° fixed. The fact that the movement of the Impact lever is specified in accordance with the angle of rotation, the Angle of rotation for the end of the acceleration phase at an angle of rotation of approx. 125 °. In the The device in question here only needs to be used for this about 15 ° later angle of rotation of the shot channel on the Projectile trajectory, i.e. the Swiveling movement of the reed is from this Angular position almost exposed. This has the Advantage that an additional range of rotation angle for Is available, e.g. for an increase in performance can be used. In contrast, the Acceleration using torsion bar spring due to the Decoupling the drive and the impact lever the reed already at the rotation angle position of approx. 110 ° stand still, namely as soon as the torsion bar spring is released.

Reference is made to FIGS. 5 and 6. At In this embodiment, the device contains the Impact lever 1, a cam mechanism 31 and one kinematic chain 32, on the one hand with the Cam gear 31 and on the other hand with the impact lever 1 connected is. To drive the device through the The main drive of a weaving machine is a Gear 33 and a braking device 34 intended. The cam mechanism 31 contains two Control discs 35, 36 which are integrally formed can with e.g. a hub 37, and a roller assembly 38, which compared to the embodiment according to FIG. 2 is modified. The roller assembly 38 includes two Rolls 39, 40, the same or different Have diameters and their distances from the center of the Axis 17 are the same or different. The Control discs 35, 36 are non-rotatable on the axis 15 arranged. The roller assembly 38 and the kinematic Chain 32 are connected to each other and on axis 17 pivotally arranged. The kinematic chain 32 forms a quasi S-shaped, asymmetrical four-bar linkage with three one-armed levers 41, 42, 43. The lever 41 is on one End with the axis 17 torsionally and at the other end connected to the lever 42 via the joint 25 (FIG. 3). The lever 42 is hinged to the lever 43, the on the other hand, twist-proof with the hammer lever axis 26 connected is. The transmission gear 33 can a clutch, not shown, or directly with the Main drive shaft of a weaving machine connected to the drive be. The transmission gear contains a first one Bevel gear 51, which is arranged on the shaft 52 such that it cannot rotate is a second bevel gear 53 which is connected to the first bevel gear 51 meshes, an intermediate shaft 54 on which the second Bevel gear 53 is attached to a first gear 55 which the intermediate shaft 54 is fixed, a second gear 56, which is attached to the drive shaft 15 and with the first gear 55 meshes. The spur or bevel gears have different number of teeth to one Achieve translation quickly.

6 shows the device described above in an operating position at the time of the start of the Acceleration phase, the projectile 29 in the Firing position is arranged. With this device can the impact lever 1 the same sequence of movements be issued, as in the embodiment according to Figures 2 to 4.

With the application of the quasi S-shaped, asymmetrical Four-bar in combination with the roller arrangement 38 the possibility is created to apply the surface pressure the treads, the vibrations and the masses to reduce. As shown in FIG. 7, roles are used for this provided with different diameters R1, R2, the with different distances RR1, RR2 from the Pivot axis of the roller assembly 38 are arranged.

To the load of the drive of the impact lever 1 can reduce a spring element for power equalization be provided. As shown in Fig. 8 is one Torsion bar spring 61 fixedly anchored at one end and connected to the impact lever 1 at the other end. Of the Impact lever 1 is non-rotatable with an axis 62 connected, connected to the four-bar linkage 10 and is pivotally arranged. The axis 62 is as Hollow cylinder formed in which the Torsion bar spring 61 is attached. The flapper will through the cam mechanism 2 or 31 and the four-bar linkage 10 or 32 pivoted back and forth and forms a oscillatory system, in which in an optimal way through the combination of mass (cam drive oscillating mass) and spring action (torsion bar spring) Performance equalization is achieved. Instead of on axis 62 the torsion spring bar can be arranged on the axis 17 become. The torsion bar 61 can with respect to the Angular position of the impact lever 1 in its action relaxed position either in the middle or at one of his End positions or between these to be clamped to the Device during acceleration or Relieve the delay phase.

9 are the Control discs and the rollers with teeth 75, 76 provided to take a roll instead of rapid movements To force sliding movement.

10 shows another embodiment of the Transmission gear 50. To within one revolution to achieve a variable speed and that Relieving cam gears are two ellipticals Gears 81, 82 are provided, the one gear 81 on the axis 15 and the other gear 82 on one Intermediate axis 83 is arranged non-rotatably. On the A gear 84 is also attached to the intermediate axis 83 with the gear 55 of the transmission gear engaged is. Using the elliptical gears, the optimal use of kinetic energy.

Figures 11 and 12 show the application of a Cam gear in a rapier weaving machine of the type with a band or bar gripper. In the 11 are a wheel 91 with a Gripper belt 92 and a gear 93 on an axis 94 attached. The cam mechanism 95 is basically the same as with the device for the projectile loom formed, the contour of the control discs for this purpose can be different. In the drive chain between the gear 93 and the cam gear are one Tooth segment 96, which is fixed on an axis 97 and meshes with the gear 93 and a kinematic chain 98 provided on the one hand with the axis 97 and on the other hand with the roller arrangement of the cam mechanism 95 is connected.

The embodiment shown in Figure 12 differs from the embodiment according to the Figure 11 only in that the Weft insertion by means of a hook 100 he follows.

As can be seen from FIG. 13, the kinematic chain 98 a first lever 103 which e.g. on the hub 16 (Fig. 5) of the roller assembly attached and is pivotally arranged on the axis 17, a second Lever 104, which is attached to the axis 97 and one third lever 105 on the first and second Lever is connected. With a gripper as well Projectile loom it is required both Time of start or end of the Weft insertion process as well as the insertion distance (Rapier weaving machine) or launch speed (Projectile weaving machine). To adjust the At the time the second lever 104 is connected to the axis 97 formed as a clamp connection 106 to the Wheel 91 or the position of the striking lever 1 adjust. For setting the entry distance or the Stroke stroke is for connecting the first lever 103 with the third lever 105 in the first lever 103 Elongated hole 107 formed and a screw 108 intended. This slot is preferably on one Circular arc with center point on the upper joint of the Lever 105, thereby the starting position of the gripper belt (Rod) or impact lever when adjusting the stroke maintain.

The device contains an entry means 1 and a Cam gear 2 with two control discs 3, 4 on an axis 5 are attached and with a Output arrangement 6, which with the entry means 1 is connected and has rollers 8. The roles are in positive connection with the control discs, see above that the entry means 1 with a back and forth movement a positively guided, predetermined movement sequence for Entry of a weft thread carrier 29 is granted.

In the case of a projectile weaving machine, this is used Device accelerates a projectile, the Projectile launch speed from speed is dependent. With a rapier weaving machine, a Entry wheel rotated back and forth, starting the entry and the entry length are adjustable.

Claims (19)

Insertion device for a weft thread in one Loom, with a weft thread carrier and with a drive device for the weft thread carrier, wherein the drive device is a drive, a Gearbox and an entry means comprising the Weft thread carrier is in operative connection or can be brought to the weft carrier by means of a translational movement or acceleration in one Enter the shed, characterized in that the Gear (2, 31) as a cam gear with two Control discs (3, 4; 35, 36) running in parallel are to each other and with an output arrangement (6, 38) is formed, the output arrangement (6, 38) on the one hand with the entry means (1) is connected to the drive and on the other hand with two Rolling elements (8) is provided, which are intended for this purpose to roll on the control discs without play and the Entry means (1) a positively driven, to issue predetermined movement. Device according to claim 1, characterized that the entry means is a striking lever (1) and that a device (10, 32) is provided which into the drive chain of cam gears (2, 31) and Impact lever (1) is arranged to the Increase the angular velocity of the impact lever. Device according to claim 2, characterized in that the establishment is a symmetrical quadrilateral (10) or an asymmetrical four-bar linkage (32). Device according to one of claims 1 to 3; characterized in that the swivel angle α1 and α2 are freely selectable (Fig. 6). Device according to one of claims 1 to 4, characterized characterized in that the output arrangement (38) a Contains roller assembly which is pivotally arranged and that the rolling elements (8) are the same or have different diameters (R1, R2) and in same or different distances (RR1, RR2) are arranged from the pivot axis (Fig. 7). Device according to one of claims 1 to 5, characterized characterized that the control discs and the Roller arrangement are designed or arranged so that the movement and power transmission form- or done non-positively. Device according to one of claims 2 or 3, characterized by means (25) for the Impact lever angular velocity (1) adjust. Device according to one of claims 1 to 7, characterized by an electric motor (11) with a brake clutch unit that with the Cam gear (2, 31) is connected to the drive. Device according to claim 8, characterized in that the electric motor is a geared motor (11). Device according to one of claims 1 to 9, characterized by an energy store (61), which is the kinetic energy of the entry means saves to the drive torque of the drive to reduce. Apparatus according to claim 10, characterized in that the energy storage is a torsion bar spring (61) is arranged on the one hand and on the other hand with the entry means (1) or Control discs (3, 4; 35, 36; 71, 72) is connected. Apparatus according to claim 6, characterized in that the control discs are designed as a structural unit and are designed to create a flywheel Form energy storage. Device according to claim 1, characterized in that the entry means a tape or bar gripper with a wheel (91) that with the cam gear (95) is connected to the drive. Loom with a device according to one of the Claims 1 to 13, characterized in that the Device as an assembly in the weaving machine is arranged. Weaving machine according to claim 13, characterized by a braking device (34), the cam gear (2) is assigned. Loom with a main drive shaft after Claim 15, characterized by a Gearbox (33) on the one hand with the Main drive shaft (52) and on the other hand with the Cam gear (2, 31) is connected to the drive. Weaving machine according to claims 15, characterized characterized in that the transmission gear (50) elliptical gears (81, 82) identifies to inside a variable speed to one revolution achieve and relieve the cam gear (Fig. 11). Loom according to one of claims 16 or 17, characterized in that the transmission gear (33, 50) an integer gear ratio having. Loom according to one of claims 14 to 18, characterized in that the loom is a Projectile loom is and that that Gearbox (33) is intended to Number of strokes corresponding to the To increase gear ratio.

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