EP1281797B1 - Drive means for operating devices of weaving machines - Google Patents

Description

The invention relates to a drive device for working elements on weaving machines, wherein a frame fixedly mounted, reversibly driven drive wheel drives a rectilinear guided parallel to the fabric stop edge working element, wherein for the reversible drive of the gen. Antriebsrades, whose axis is directed perpendicular to the tissue stop edge, on the parallel to the tissue stop edge directed main shaft of the loom at least one cam is provided, wherein the curves of the cam body are scanned by roller lever and the oscillating motion thus generated via an input shaft initially a high translational gear train and then the drive wheel is supplied and wherein the oscillating movement of the roller lever to the main shaft aligned at right angles Input shaft of the high-ratio spur gear is transmitted.

By the GB 2 177 429 A a transmission has been proposed for the drive of gripper bands on looms, in which two arranged on the main shaft parallel cam plates are positively scanned by an interconnected roller lever pair. The oscillating shaft of Rollenhebelpaa res also carries a rocker arm, which transmits the oscillatory motion via a spherical coupling on a segment whose axis is aligned transversely to the main shaft of the loom. The segment transmits the oscillatory motion to a gear which is disposed on the axis of the drive wheel for the rapier band. This arrangement is disadvantageous for various reasons. The translation is only sufficient for weaving machines with a small working width. For carpet looms, which usually have a working width of 4 to over 5 m, this gear is not applicable. Increasing the ratio in the last gear stage, then increases the diameter of the drive wheel for the gripper belt such that the mass to be moved increases in the range of the highest speeds and accelerations such that all elements of the transmission deform elastically. A major cause of this high elasticity of the transmission is the one-sided eccentric force attack of Zahnsegm entes the gear on the output shaft. At different operating speeds significantly different turning positions are achieved. An error-free yarn transfer is not possible - especially in weaving machines with high weft insertion performance.

With the DE 79 08 124 U1 Another drive device of this type has been proposed. It differs from the aforementioned device in that the high-ratio spur gear is a multi-stage transmission. This larger working widths can be realized and the last gear stage no longer requires such a large diameter of the drive wheel for the gripper bar. The disadvantage of this transmission, the additional gear play and especially the multiple one-sided eccentric force attack of the gear elements to each other. A high elasticity of the transmission is the inevitable consequence.
The disadvantages in terms of the GB 2 177 429 A1 have been described, are also unavoidable with this device.

By the US 5,351,723 a gripper drive for weaving machines has been proposed, in which on the main shaft of the loom globoidartig designed curves are arranged. This has the advantage that the roller lever sampled oscillatory motion without change of direction and without spherical coupling can be transmitted to the high-ratio gear train. Thus, the gear play can be reduced. However, the elasticity of the entire gear train, which causes the majority of the speed-dependent overstroke, is not or only insignificantly reduced. The essentially single-stage translation is not sufficient in this case for looms with a large working width. Additional translation levels would be required. These additionally increase the elasticity. In addition, also acts in this device, the one-sided eccentric force attack - not only on the output shaft of the high gear ratio - very disadvantageous.
Also, this drive device is thus not suitable to allow a significant increase in the speed of the loom with reliable operation of the designated working elements.

In the European Patent Application 241,036 the drive for a knife carriage is described which is used for separating a double carpet fabric in the pile plane on a double carpet weaving machine. This knife carriage is moved irrespective of the full width of the fabric produced and on both sides beyond. A parallel to the main shaft of the machine arranged countershaft receives its rotational movement via a multi-stage spur gear from the main shaft of the loom. At the outer, free end of the countershaft, a spherical, rotating crank is attached. The axis of the coupling joint is directed in each phase of its rotational movement to a point on the axis of a rocking shaft, which is arranged perpendicular to the axis of the main shaft. A universal joint transmits a sinoidal oscillating movement of the crank joint to the oscillating shaft.
The oscillating shaft drives for the purpose of translation of the oscillatory motion to her coaxially arranged cycloidal or planetary gear.

The output gear of this cycloidal or planetary gear is designed as a toothed belt pulley and drives over a very long toothed belt the blade carriage iridescent over the required, very large path parallel to the fabric edge.

Even such a trained transmission for very long traversing movements on the loom leads only to unsatisfactory results. Although the crank with the inclined crank pin allows a low-backlash transmission of the drive torque to a 90 ° offset shaft. However, it does not allow a free design of the laws of motion of the work items. The swinging motion always has sinoid character. With the setting of the radius of the spherical crank within narrow limits, one can vary only the stroke size, but not the law of motion itself.

To ensure a nearly constant, technologically conditioned maximum speed during a large stroke range, however, is highly desirable both for moving the knife carriage and for moving the gripper in the shed. This can not be guaranteed with the device just described. Thus, the application of such a device for driving the designated work items on carpet looms with the required higher weft insertion frequency is not appropriate.

• die neben einem geringen Getriebespiel auch eine geringe Getriebeelastizität gewährleistet und
• die es ermöglicht, die Bewegungsgesetze der anzutreibenden Arbeitselemente zum Zweck der Ausnutzung der technologisch bedingten Maximalgeschwindigkeit der Arbeitselemente über große Wegabschnitte frei zu gestalten.

The object of the present invention is therefore to propose a drive device for reversibly movable over long distances working elements of the weaving machine (eg gripper bars, rapier bands, rods or knife carriages), whose direction of movement is aligned parallel to the tissue impact plane,

• which also ensures low gear elasticity in addition to a low gear play and
• which makes it possible to design the laws of motion of the driven working elements for the purpose of exploiting the technologically related maximum speed of the work elements over long distances sections.

This object is achieved by the combinations in claims 1 to 3 in an almost equivalent manner.
The solution according to claim 1 has the advantage that the backlash in the spherical rod ends of the coupling - even after prolonged use - can be kept very low. The elasticity of the spherical coupling and the planetary gear is significantly lower than the elasticity of the usual gear stages. The predetermined with the shape of the cam arbitrary shapable laws of motion can be translated almost error-free to work towards. The backlash and the elasticity of the transmission are - reduced to a minimum - in particular by the waiver of stationary mounted intermediate shafts for additional gear stages and by evenly distributed on the circumference of the sun gear force attacks of the planetary gears.
With the configuration of the gear train as a planetary gear, the number of gear stages and thus the gear play is further reduced. The moving mass can be kept low, in particular in the area of the high speed and high acceleration moving gear elements. The oscillating drive shaft for the planetary gear is aligned coaxially with the output shaft. As a result, the transmission is extremely compact executable. The cost of the transmission and the maintenance costs are within reasonable limits.

The second basic embodiment according to claim 2, is based on the use of other curve systems. The cylinder and globoid curves enable the generation of oscillatory motion directly on the shaft, which is already directed at right angles to the main shaft. The application of a flexible bevel gear stage is avoided. The achievable advantages correspond to those of claim 1.

The solution variant according to claim 3 provides by the use of a screw gear for the change of direction of the oscillatory motion. Also this screw gear ensures the least play the assurance of low elasticity of the transmission. The swinging motion, which is very strong at the end only via Stirnradpaarungen of the planetary gear to be translated at high speeds can be performed with high precision. Again, it is possible to ensure a Hubveränderung by interposing appropriate levers with adjustable joints.

The combination of two basically similar coupling mechanism according to claim 4 allows extremely large translations with few gear stages in a very limited space. This embodiment has the particular advantage that very large strokes, as z. B. occur when driving rods and the drive of knife carriage, can be realized with two gear stages. It is particularly advantageous that the transmission elements which work with the largest paths and the largest accelerations can be equipped with a low mass.

With the distribution of the drive movement of the oscillating shaft or the input shaft of the planetary gear on the web and the ring gear of the planetary gear - according to claim 5 in general and according to claim 6 especially for the embodiment according to claim 1 or 2 - the translation in the first or single stage with the planetary gear increases further.

The design of the spherical coupling according to claim 7 has the advantage of using standardized assemblies and components.

The claim 8 defines the use of cycloidal transmissions, in which the power is transmitted through cams, which in turn are driven by means of eccentric. The use of this transmission has the advantage that you can realize very large translations with a gear stage. The power transmission to the output shaft takes place at several evenly distributed around the circumference positions. The input shaft and the output shaft of the cycloidal gear are coaxially aligned with each other as well as the planetary gear.

Also known under the name "Harmonic Drive" transmission according to claim 9 is able to realize in a gear stage, an extremely large translation. Power is transmitted to the output shaft at least two or more evenly distributed circumferentially. The input shaft and the output shaft of the harmonic drive gear are coaxially aligned with each other as well as the planetary gear.

Fig. 1

eine Draufsicht auf eine erste Variante der erfindungsgemäßen Antriebsvorrichtung in einer Webmaschine,

Fig. 1a

einen Schnitt durch das Gelenk einer sphärischen Koppel,

Fig. 2

einen Querschnitt durch das Getriebe der Fig. 1 in einer vertikalen Ebene,

Fig. 3

eine zweite Variante der Antriebsvorrichtung mit vertikal geführter Schubstange und Kurvenzylinder,

Fig. 4

eine schematische Darstellung einer dritten Variante, bei der die Eingangswelle des Rädergetriebes mit senkrechter Achse direkt von Rollenhebeln einer Zylinderkurve auf der Hauptwelle getrieben wird,

Fig. 5

eine Globoidkurve für eine Antriebsvorrichtung nach Fig. 4 und

Fig. 6

einen Kegelkurvenantrieb für die Antriebsvorrichtung nach Fig. 4.

The invention will be explained in more detail below by exemplary embodiments. In the accompanying drawings show:

Fig. 1

a top view of a first variant of the drive device according to the invention in a loom,

Fig. 1a

a section through the joint of a spherical coupling,

Fig. 2

a cross section through the transmission of FIG. 1 in a vertical plane,

Fig. 3

a second variant of the drive device with vertically guided push rod and cam cylinder,

Fig. 4

a schematic representation of a third variant in which the input shaft of the gear train is driven with a vertical axis directly from roller levers of a cylinder cam on the main shaft,

Fig. 5

a Globoidkurve for a drive device according to Fig. 4 and

Fig. 6

a conical-curve drive for the drive device according to FIG. 4.

On the main shaft 1 of the weaving machine, which extends parallel to the fabric stop edge 81, a cam pair 11 is arranged torsionally rigid. A double roller lever 21 cooperates with this cam pair 11 in such a way that it is moved positively with a swinging movement about the axis of the oscillating shaft 2.

On the oscillating shaft 2, there is first a rocker arm 26. It is rigidly connected to the oscillating shaft 2. At the free end of the rocker arm 26 engages a spherical coupling 30, which has two mutually offset by 90 ° joints. Each of these joints is designed as a pendulum bearing. As a rule, spherical roller bearings 301 are used for this embodiment. Both axes of the joints are regularly aligned transversely to the main direction of movement of the spherical coupling 30.

The second joint of the spherical coupling 30 cooperates with a drive lever 42 on the input shaft 4 of the gear train 5 together. In the gear train 5, which is designed here as a planetary gear, drives the input shaft 4, the web 51, are mounted on the planet gears 52. The planet gears 52 roll inside of the teeth of the ring gear 53 and drive inside the sun gear 54 at.

The sun gear 54 is rotationally rigidly connected to the web 541 of a second planetary gear. This web 541 also leads planet gears 55, which roll on the internal teeth of the ring gear 56 and drive the sun gear 57. The ring gear 56 is firmly anchored in the machine frame. The last sun gear 57 is rigidly connected to the output shaft 571, which carries the drive wheel 6 at its upper end. The drive wheel 6 drives in the present case, the gripper belt 61. However, it can also be designed for the drive of a toothed belt, which drives the knife carriage.

In the embodiment of FIG. 2, a further oscillating lever 25 is driven by the oscillating shaft 2. This rocker arm 25 is directed opposite to the rocker arm 26. He carries at its outer end a second spherical coupling 31, which is connected via a spherical joint with the ring gear 53 at 531. By this measure, the ratio in the first stage of the gear train 5 is additionally increased. With appropriate adjustments to the length of one or both of the couplers 30, 31 in the radial direction of the rocker arms 25, 26, the vibration magnitude, which is then finally translated, can be brought to a required level.

The connection of the double roller lever 21 and the rocker arm 25, 26 on the rocker shaft 2 can be made very stable with known measures, so that no torsion and no deflection can occur between these elements.

The coupling 30 and 31 are charged only to train or pressure. They are considered to be rigid in the gear train in terms of the elasticity of the transmission. If the input shaft and its connection to the web 51 and the drive lever 42 are also made very stable, torsions and other deformations are largely excluded there as well. Stellstellungen for changing the stroke size can be provided in this area.

The achievable, unadulterated oscillating movement of the web 51 and the ring gear 53 is then translated into the planetary gears described above with little play and without further elastic deformation and guided to the gripper belt 61 or other working element.

The rapier band 61 or the other respective working element performs a very large stroke movement even at very high operating speeds with minimal play.

A second variant of the drive is shown in FIG. Instead of the two different cams 11, the main shaft 1 of the loom drives a cam 15 of the same diameter. Their stroke is positively removed by the cam rollers of a push rod 7.

This push rod 7 has at its upper end two plungers 71, 71 ', which are guided in frame-fixed guide rails 72, 72'. These plungers 71, 71 'are equipped with drive rollers 711, 711'. These engage in the groove of a screw 431, which is attached to a cam cylinder 43. The cam cylinder 43 advantageously has two offset by 180 ° relative to each other screw curves 431, the pitch angle is preferably greater than 45 °.

In this way, the lifting movement of the push rod 7 is converted with minimal play and elimination of any elastic elements directly into a rotational movement in changing directions of the input shaft 4 "This oscillating movement of the input shaft 4" can be selected to be greater than the oscillatory movement of the input shaft 4 'in FIG 4 and the vibration path of the input shaft 4 in FIG.

By this measure, it will u. U. possible to form the gear train 5 in the form of a single-stage planetary gear. The design of this transmission is very compact and extremely stable; its elasticity is low.

Also in this context, we would like to point out that with the interposition of a one-sided frame fixedly mounted lever between the push rod 7 and the plunger 71 with radially adjustable bearings (not shown, because in itself known), the stroke size can be made adjustable within certain limits.

The embodiment of FIG. 4 shows the drive of the input shaft 4 'of the gear train 5 directly above the roller lever 22, which is moved by a cylinder cam 12 swinging form fit. A bevel gear or complicated measures to prevent torsions are avoided in this embodiment.

In the embodiment of Figure 4 on the output shaft 571 of the gear train 5, two drive wheels 6, 6 'are fixed, which drive the gripper bars 62, 63. The gripper bars 62, 63 are moved in a known manner into two superposed looms of a double carpet loom for the purpose of weft insertion. These registered weft threads are struck in the usual way by means of loading on the fabric stop edge 81. Thus, a further Web progress is achieved on double carpet fabric 8.

In Fig. 5, the drive assembly is shown by a globoid cam 13 and a corresponding roller lever 23. This arrangement may replace the cylinder cam arrangement 12, 22 in FIG. 4.

Finally, Fig. 6 shows a further variant for the replacement of the drive with cylinder curves 12 or with Globoidkurven 13 by cone curves 14 which drive a roller lever 24 positively. However, the use of such a drive for a swinging movement of the roller lever 24 is only possible where the shaft end of the main shaft 1 is available.

In the above description, the one or two-stage planetary gear has been described as a high gear ratio. For the technical problem to be solved in this context, to realize an extremely large ratio with a single gear stage if possible, is also possible with so-called "CYKLO transmissions" or a so-called "harmonic drive" transmission.

Under the cycloid or "CYCLO" gear we understand a transmission in which the power is transmitted through cams, which in turn are driven by an eccentric. Such transmissions should be able to achieve translations of 1: 119 in a very compact design.

The so-called "Harmonic Drive" gearbox has an elliptical rotating steel disc on the circumference of a flexible toothed ring with external teeth is easily rotatable. This toothed ring runs in the region of the larger diameter on the internal toothing of a ring gear, which has a slightly larger number of teeth than the toothed ring. Again, similarly large translations are possible, as described in cycloidal transmissions.

LIST OF REFERENCE NUMBERS

1

main shaft

11

Cam pair

12

cylinder cam

13

globoid cam

14

cone curves

15

Curve of the same diameter

2, 2 '

oscillating shaft

21

Double roller lever

22

roller lever

23

roller lever

24

Angle roller lever

25

rocker

26

rocker

30

paddock

301

Spherical roller bearings

31

paddock

4, 4 ', 4 "

input shaft

41

camp

42

drive lever

43

cam cylinder

431

screw curve

5

gearing

51

web

52

planetary gears

53

ring gear

54

sun

541

web

55

planetary gears

56

ring gear

57

sun

571

output shaft

6, 6 '

drive wheel

61

rapier

62

gripper bar

63

gripper bar

7

pushrod

71

tappet

711, 711 '

drive rollers

72, 72 '

guide rail

8th

Double carpet fabric

81

Cloth edge

Claims (9)

1. A drive mechanism for operating elements on looms,
   wherein a frame-mounted, reversibly driven drive wheel (6) drives in rectilinear manner an operating element guided parallel to the beat-up edge (81),
   wherein for reversibly driving the aforementioned drive wheel (6), the axis of which is oriented vertically to the beat-up edge (81), at least one cam body (11) is provided on the main shaft (1) of the loom which is oriented parallel to the beat-up edge,
   wherein the cams of the cam body (11) are swept by means of roller followers (21) and the oscillating movement thus produced is transmitted via an input shaft (4) initially to a high-conversion spur gear (5) and then to the drive wheel (6),
   wherein the cam bodies on the main shaft (1) are in known manner pairs of cam discs (11), with which roller followers (21) are associated on an oscillating shaft (2) oriented parallel to the main shaft (1),
   wherein the oscillating shaft (2) is connected via an oscillating lever (25) and at least one spherical-joint connecting-rod (30) to the oscillating input shaft (4, 4', 4") of the wheel gear (5) and
   characterised in that
   the wheel gear (5) is in the form of a planetary gear (5) with spur wheels (52, 53, 54) and
   the carrier (51) of the planetary gear (5) is in a drive connection with the input shaft (4, 4', 4") which is driven in oscillation, and the sun gear (54) is in a drive connection with the drive wheel (6) for the operating element (61; 62, 63).
2. A drive mechanism for operating elements on looms,
   wherein a frame-mounted, reversibly driven drive wheel (6) drives in rectilinear manner an operating element guided parallel to the beat-up edge (81),
   wherein for reversibly driving the aforementioned drive wheel (6), the axis of which is oriented vertically to the beat-up edge (81), at least one cam body (11) is provided on the main shaft (1) of the loom which is oriented parallel to the beat-up edge,
   wherein the cams of the cam body (11) are swept by means of roller followers (21) and the oscillating movement thus produced is transmitted via an input shaft (4) initially to a high-conversion wheel gear (5) and then to the drive wheel (6),
   wherein the cams on the main shaft are in the form of cylindrical (12), conical (14) or globoid cams (13) and
   wherein the roller followers (22; 23; 24) are connected to the input shaft (4') of the wheel gear (5) which is arranged at right-angles to the main shaft (1),
   characterised in that
   the wheel gear (5) is in the form of a planetary gear (5) with spur wheels (52, 53, 54) and
   the carrier (51) of the planetary gear (5) is in a drive connection with the input shaft (4, 4', 4") which is driven in oscillation, and the sun gear (54) is in a drive connection with the drive wheel (6) for the operating element (61; 62, 63).
3. A drive mechanism for operating elements on looms,
   wherein a frame-mounted, reversibly driven drive wheel (6) drives in rectilinear manner an operating element guided parallel to the beat-up edge (81),
   wherein for reversibly driving the aforementioned drive wheel (6), the axis of which is oriented vertically to the beat-up edge (81), at least one cam body (11) is provided on the main shaft (1) of the loom which is directed parallel to the beat-up edge and
   wherein the cams of the cam body (11) are swept by means of follower rollers and the oscillating movement thus produced is transmitted via an input shaft (4) initially to a high-conversion wheel gear (5) and then to the drive wheel (6),
   characterised in that
   the cam bodies on the main shaft (1) are in known manner cam discs (11; 15), with which is associated at least one tappet (71) oriented and guided transversely to the main shaft (1),
   a cylindrical cam body (43) with helix (431) is arranged parallel to the tappet (71), the axis of which body is connected to the input shaft (4") of the wheel gear (5),
   the tappets (71) are provided with drive rollers (711, 711'), at least one of which cooperates with a helix (431) of the cam cylinder (43),
   the wheel gear (5) is in the form of a planetary gear (5) with spur wheels (52, 53, 54) and
   the carrier (51) of the planetary gear (5) is in a drive connection with the input shaft (4, 4', 4") which is driven in oscillation, and the sun gear (54) is in a drive connection with the drive wheel (6) for the operating element (61; 62, 63).
4. A drive mechanism according to one of Claims 1 to 3,
   characterised in that
   the wheel gear (5) consists of two planetary gears (51, 52, 53, 54; 541, 55, 56, 57) of the same construction arranged coaxially to one another,
   the sun gear (54) of the first planetary gear (51, 52, 53, 54) is connected to the carrier (541) of the second planetary gear (541, 55, 56, 57) and the sun gear of the second planetary gear is connected to the drive wheel (6).
5. A drive mechanism according to Claim 1, 2 or 3,
   characterised in that
   two opposing oscillating movements are derived from the oscillating shaft (2) or the input shaft (4, 4', 4"),

   - of which the first oscillating movement is passed directly to the carrier (51) of the planetary gear (51, 52, 53, 54) and

   - the second oscillating movement is passed with a direction of rotation counter to that of the carrier (51) to the ring gear (53) of the planetary gear (51, 52, 53, 54).
6. A drive mechanism according to Claim 5,
   characterised in that
   the oscillating shaft (2) has two oscillating levers (25, 26) directed in opposite directions, of which the first oscillating lever (25) is in a drive connection via a first spherical-joint connecting-rod (30) with the carrier (51) of the planetary gear (51, 52, 53, 54) and
   the second oscillating lever (26) is in a drive connection via a second spherical-joint connecting-rod (31) with the ring gear (53) of the planetary gear (51, 52, 53, 54).
7. A drive mechanism according to Claim 6,
   characterised in that
   the spherical-joint connecting-rods (30; 31) have two articulations offset relative to one another by 90° and directed transversely to the direction of stroke, and
   that the articulations of the spherical-joint connecting-rods (30, 31) are provided with spherical bearings (301).
8. A drive mechanism according to one of Claims 1 to 3,
   characterised in that
   a cycloidal gear is provided instead of the planetary gear, in which cycloidal gear the power is transmitted by eccentrically revolving cam discs.
9. A drive mechanism according to one of Claims 1 to 3,
   characterised in that
   instead of the planetary gear (5) what is called a harmonic drive gear with a deformable annular gear revolving on an elliptical disc is provided, the annular gear meshing with the internal teeth of a ring gear which has a slightly larger number of teeth.

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