EP1281797A2 - Drive means for operating devices of weaving machines - Google Patents

Abstract

Loom drive system, e.g. for the gripper rods, has cam disks at the main shaft with a transmission linkage to the input shaft at the high reduction gear mechanism. The reversible drive mechanism for loom components, e.g. the weft grip insertion rods, has a cam body on the main shaft (1) as a pair of cam disks (11), with their roller levers (21) on a swing shaft (2) which is parallel to the main shaft. The swing shaft is linked to the high reduction gearing (5) through a swing lever (25) and a coupling link (30) to the gear input shaft. The reduction gearing assembly is wholly of paired rim gears.

Description

The invention relates to a drive device for working elements on weaving machines, a reversibly driven, fixed to the frame Drive wheel is a working element that runs parallel to the fabric stop edge drives, whereby for the reversible drive of the gen. drive wheel, whose axis is directed perpendicular to the tissue stop edge the main shaft of the weaving machine, which is directed parallel to the fabric stop edge at least one curve body is provided and the curves of the cam body can be scanned using roller levers and the generated in this way Swinging motion via an input shaft, first of all a highly translating one Gear and then the drive wheel is fed.

DE 33 25 591 C2 is a gear for driving gripper bars on looms, in which two on the Main shaft cam plates arranged parallel to each other interconnected pair of roller levers are positively scanned. The oscillating shaft of the pair of roller levers also carries a segment that the Transfers swinging motion to the first gear of a gear train that with a multi-stage translation the changing drive movement for the gripper bar creates.

In this gear transmission there is regularly a bevel gear pair which is suitable for the change in the axial direction of the gearbox, to a cross to the fabric stop edge aligned wave, is responsible.

A disadvantage of this transmission is that the stroke movement z. B. for the gripper bar cannot be adjusted at any point. A second, very essential The disadvantage is that there is an uncontrollable in the overall transmission Play and an uncontrollable elasticity is present, which only with high Storage expenses can be limited.

When using such a gear for driving the gripper bars Carpet weaving machines guide the rapier rods into their end positions uncontrollable overstroke. This hinders the proper functioning of the Weaving process, especially when the weft insertion frequency is increased further.

This drive device is therefore not suitable, a significant increase in speed the weaving machine with reliable operation of the designated To enable work items.

DE 43 37 406 A1 describes another transmission for driving a Pair of rapier rods on double carpet weaving machines. The basic structure of the gearbox essentially corresponds to that with respect was described on DE 33 25 591 C2. The transmission of the lifting movement from the oscillating shaft to the oscillating drive segment of the The gear train is carried out here with the help of a flat coupling, the joints the coupling on the respective rocker arms are adjustable.

In the area of the second gear stage, a torsion spring is provided, which is to eliminate the play in the gear - starting with the roller gear up to the second gear stage - by means of an appropriately leading or trailing tensioning gear. The axis direction in the gearbox is changed only by a bevel gear in the penultimate gear stage. The torsion spring therefore has no effect on the compensation of the elasticity of the bevel gear. It also has no positive effects on the gear elements moving at high speed and with high acceleration.
This gearbox is therefore not suitable for ensuring a further increase in the speed of the weaving machine.

When using the described gearbox for driving the gripper bars can be an absolute at different working speeds reliable transfer of the weft threads in the middle of the shed not regularly be guaranteed.

Another disadvantage of the drive devices described is that large number of gear stages. It leads to a large number of gamblers and / or elastic coupling areas between gear elements. The The cost of installing and maintaining the transmission is high. The The service life of the gear elements leaves many wishes unfulfilled.

In European patent application 241 036 the drive for one Knife carriage described for separating a double carpet fabric is used in the pile plane on a double carpet weaving machine. This knife sled is iridescent across the full width of the manufactured Fabric and moved beyond on both sides. One parallel to The main shaft of the machine arranged countershaft receives its rotary movement via a multi-stage spur gear from the main shaft of the weaving machine. At the outer, free end of the countershaft there is a spherical, rotating crank attached. The axis of the coupling joint is in everyone Phase of their rotational movement on a point on the axis of an oscillating shaft directed, which is arranged perpendicular to the axis of the main shaft. On The universal joint transmits a Sinoid swinging motion of the crank joint on the vibrating shaft.

The oscillating shaft drives for the purpose of translating the oscillating movement a cycloidal or planetary gear arranged coaxially to it. The driven gear this cycloid or planetary gear is as a toothed belt pulley trained and drives the knife carriage via a very long toothed belt iridescent over the required, very large path parallel to the fabric stop edge.

Even a gear designed in this way for very long traversing movements on the loom only leads to unsatisfactory results. The crank with the inclined crank pin allows transmission with little play of the drive torque on a shaft offset by 90 °. However, it leaves no free design of the laws of motion of the work elements. The Swinging movement is always Sinoid in character. With the setting of the Radius of the spherical crank within narrow limits can only be the stroke size vary somewhat, but not the law of motion itself.

An almost constant, technologically determined maximum speed To ensure during a large stroke range is for both Moving the knife carriage as well as moving the grippers in the Shed highly desirable. You can do this with the not guarantee device described. So that's the application such a device for driving the designated work elements on carpet weaving machines with the required higher weft insertion frequency not useful.

• 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 working elements of the weaving machine which can be reversibly moved over long distances (e.g. rapier rods, rapier belts, rods or knife slides), the direction of movement of which is aligned parallel to the plane of the fabric stop,

• which, in addition to low gear play, also ensures low gear elasticity and
• which makes it possible to freely design the laws of motion of the work elements to be driven for the purpose of utilizing the technologically determined maximum speed of the work elements over large sections of the path.

This object is based on the combinations in claims 1 to 3 almost equivalent way solved.

The solution according to claim 1 has the advantage that the gear play in the spherical rod ends of the paddock - even after prolonged use - very much can be kept low. The elasticity of the spherical paddock is clear lower than the elasticity of the conventional bevel gear stages. The ones that can be designed as desired with the shape of the cam disks Laws of motion can be almost flawless right down to the work element translate. The gear play and the elasticity of the gear are on reduced to a minimum.

The second basic embodiment according to claim 2, starts from the Use of other curve systems. The cylinder and globoid curves enable the oscillation movement to be generated directly on the shaft, which is already perpendicular to the main shaft. The application of a elastic bevel gear stage is avoided. The achievable advantages correspond to those of claim 1.

The solution variant according to claim 3 ensures the use of a Screw gear for changing the direction of the swinging motion. Also this screw gear ensures the safety with minimal play a low elasticity of the gear. The end exclusively about Helical gear pairings can be very strongly translated swinging motion high working speeds with high precision. Also here it is possible by using appropriate levers adjustable joints to ensure a change in stroke.

With the design of the gear train as a planetary gear - accordingly the embodiment according to claim 4 - the number of gear stages and thus further reducing the gear play. The moving mass can especially in the area of high speed and high acceleration moving gear elements are kept low. The swinging The drive shaft for the planetary gear is aligned coaxially with the output shaft. This makes the gearbox extremely compact. The Costs for the gearbox as well as the maintenance effort are reasonable Limits.

The combination of two basically identical coupling gear according to claim 5 enables extremely large gear ratios with a few gear stages very limited space. This version has the particular advantage that very large lifting movements, such as B. when driving rods and Knife carriage drive occur, implemented with two gear stages can be. It is particularly advantageous that the one with the largest routes and the largest accelerations working gear elements with a low mass can be equipped.

With the division 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 6 in general and according to claim 7 specifically for the execution according to claim 1 - the translation in the first or single stage with the planetary gear further enlarged.

The design of the spherical coupling according to claim 8 has the advantage of Use of standardized assemblies and components.

The claim 9 defines the use of cycloid gears, in which the Power is transmitted through cams, which in turn are by means of eccentrics are driven. The use of this gear has the advantage that you can can achieve very large gear ratios with one gear stage.

Also the gearbox known as "Harmonic Drive" according to claim 10 is capable of an extremely large gear ratio in a gear stage to realize.

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 using exemplary embodiments. In the accompanying drawings:

Fig. 1

2 shows a plan view of a first variant of the drive device according to the invention in a weaving machine,

Fig. 1a

a section through the joint of a spherical coupling,

Fig. 2

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

Fig. 3

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

Fig. 4

1 shows a schematic representation of a third variant, in which the input shaft of the gear transmission with a vertical axis is driven directly by roller levers of a cylinder curve on the main shaft,

Fig. 5

a globoid curve for a drive device according to Fig. 4 and

Fig. 6

a bevel cam drive for the drive device of FIG. 4th

On the main shaft 1 of the weaving machine, which is parallel to the fabric stop edge 81 extends, a pair of cams 11 is arranged rotationally rigid. A double roller lever 21 works with this pair of cams 11 in this way together that he is form-fitting with a swinging motion around the axis the oscillating shaft 2 is moved.

A rocker arm 26 is initially located on the rocker shaft 2 the oscillating shaft 2 rigidly connected. At the free end of the rocker arm 26 attacks a spherical paddle 30, which offset two by 90 ° to each other Possesses joints. Each of these joints is designed as a self-aligning bearing. In spherical roller bearings 301 are generally used for this configuration. Both axes of the joints are regularly transverse to the main direction of movement the spherical coupling 30 aligned.

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

The sun gear 54 is torsionally rigid with the web 541 of a second planetary gear connected. This web 541 also guides planet wheels 55 which roll the internal toothing of the ring gear 56 and the sun gear 57 float. 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 on its upper end carries the drive wheel 6. The drive wheel 6 drives in the present Case the gripper belt 61. However, it can also be used to drive a toothed belt be designed, which drives the knife carriage.

In the exemplary embodiment in FIG. 2, a vibration wave 2 is used further rocker arm 25 driven. This rocker arm 25 is opposite directed to the rocker arm 26. It has one at its outer end second spherical coupling 31, which has a spherical joint with the Ring gear 53 is connected at 531. Through this measure, the translation additionally enlarged in the first stage of the gear train 5. With corresponding settings on the length of one or both couplers 30, 31 in the radial direction of the rocker arms 25, 26, which is then finally translated to a required level.

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

The couplers 30 and 31 are only loaded under tension or pressure. You are in Gear train with regard to the elasticity of the gear as rigid. Will the input shaft and its connection to the web 51 and the drive lever 42 is very stable, then there are torsions and other deformations largely excluded. Also positioning options You can provide for changing the stroke size in this area.

The attainable, undistorted oscillating movement of the web 51 and the Ring gear 53 is then in the planetary gears described above little play and without further elastic deformation and translated to Gripper belt 61 or another work element performed.

The gripper belt 61 or the other respective working element carries a very large stroke movement even at very high working speeds least play out.

A second variant of the drive is shown in Fig. 3. Instead of two different cams 11 drives the main shaft 1 of the Loom a cam 15 of the same diameter. Their lifting movement is positively through the cam rollers of a push rod 7 decreased.

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

In this way, the lifting movement of the push rod 7 is minimal Game and with the elimination of any elastic elements directly in one Rotational movement in changing directions of the input shaft 4 "converted. This oscillating movement of the input shaft 4 "can be chosen larger are referred to as the swinging motion of the input shaft 4 'in Fig. 4 and the Vibration movement of the input shaft 4 in FIG. 2.

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

In this context, we would like to point out that under Interposition of a lever fixed on one side of the frame between the Push rod 7 and the plunger 71 with radially adjustable bearings (not shown because known per se) the stroke size within certain limits can be made adjustable.

The embodiment of FIG. 4 shows the drive of the input shaft 4 'of Gear 5 directly above the roller lever 22, which is a cylinder curve 12 is positively moved swinging. A bevel gear or complicated Measures to avoid torsion are used in this version avoided.

In the embodiment of Figure 4 are on the output shaft 571 of Gear mechanism 5 two drive wheels 6, 6 'attached to the gripper bars 62, 63 drive. The gripper bars 62, 63 are known in two superimposed looms of a double carpet weaving machine for Moving purposes of the shot entry. These registered weft threads are in the usual way by means of a drawer on the fabric stop edge 81 struck. This is another step forward in the weaving of double carpets 8 reached.

In Fig. 5, the drive arrangement by a globoid curve 13 and one corresponding roller lever 23 shown. This arrangement can be the cylinder curve arrangement 12, 22 in Fig. 4 replaced.

Finally, Fig. 6 shows a further variant for the replacement of the drive with cylinder curves 12 or with globoid curves 13 by cone curves 14, the drive a roller lever 24 in a form-fitting manner. The use of such However, the drive for an oscillating movement of the roller lever 24 is only there possible where the shaft extension of the main shaft 1 is available.

In the above description, it was considered a high-ratio gear described the one- or two-stage planetary gear. For those in this Technical problem to be solved, an extremely large translation if possible with a single gear stage is also possible with so-called "CYKLO gearboxes" or a so-called "harmonic drive" gearbox possible.

By the cycloid or "CYCLO" gearbox we mean a gearbox, at which the power transmission takes place through cams, which in turn from be driven by an eccentric. Such gears are said to be very compact design ratios of 1: 119 can achieve.

The so-called "harmonic drive" gearbox has an all-round steel disc, on the circumference a flexible toothed ring with external teeth easily is rotatably guided. This toothed ring runs in the area of the larger diameter on the internal toothing of a ring gear, which is a slight has a larger number of teeth than the toothed ring. Here too are translations of similar size possible, as described for cycloid gears.

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 (10)

Drive device for working elements on weaving machines,
wherein a reversibly driven drive wheel (6) which is fixed to the frame drives a working element guided parallel to the fabric stop edge (81) in a straight line,
at least one cam body (11) is provided for the reversible drive of the generic drive wheel (6), the axis of which is directed perpendicular to the fabric stop edge (81), and on the main shaft (1) of the weaving machine, which is directed parallel to the fabric stop edge
wherein the curves of the cam body (11) are scanned by means of roller levers (21) and the oscillating movement thus generated is first fed to a high-gear wheel transmission (5) and then to the drive wheel (6) via an input shaft (4),
characterized in that the cam bodies on the main shaft (1) are pairs of cams (11) in a manner known per se, to which roller levers (21) are assigned on an oscillating shaft (2) aligned parallel to the main shaft (1),
that the oscillating shaft (2) is connected to the oscillating input shaft (4) of the wheel transmission (5) via an oscillating lever (25) and at least one spherical coupling (30) and
that the gear train (5) has only spur gear pairs for the translation of the oscillating movement. Drive device for working elements on weaving machines,
wherein a reversibly driven drive wheel (6) which is fixed to the frame drives a working element guided parallel to the fabric stop edge (81) in a straight line,
at least one cam body (11) is provided for the reversible drive of the generic drive wheel (6), the axis of which is directed perpendicular to the fabric stop edge (81), and on the main shaft (1) of the weaving machine, which is directed parallel to the fabric stop edge
wherein the curves of the cam body (11) are scanned by means of roller levers (21) and the oscillating movement thus generated is first fed to a high-gear wheel transmission (5) and then to the drive wheel (6) via an input shaft (4),
characterized in that the curves on the main shaft are designed as cylinder (12), cone (14) or globoid curves (13),
that the roller levers (22; 23; 24) are connected to the input shaft (4 ') of the gear train (5), which is arranged at right angles to the main shaft (1), and
that the gear train (5) has only spur gear pairs. Drive device for working elements on weaving machines,
wherein a reversibly driven drive wheel (6) which is fixed to the frame drives a working element guided parallel to the fabric stop edge (81) in a straight line,
at least one cam body (11) is provided for the reversible drive of the generic drive wheel (6), the axis of which is directed perpendicular to the fabric stop edge (81), and on the main shaft (1) of the weaving machine, which is directed parallel to the fabric stop edge
wherein the curves of the cam body (11) are scanned by means of feeler rollers and the oscillating movement thus generated is first fed to a high-gear wheel transmission (5) and then to the drive wheel (6) via an input shaft (4),
characterized in that the cam bodies on the main shaft (1) are cam disks (11; 15) in a manner known per se, to which at least one tappet (71) aligned and guided transversely to the main shaft (1) is assigned,
that a cylindrical cam body (43) with a screw cam (431) is arranged parallel to the tappet (71), the axis of which is connected to the input shaft (4 ") of the gear train (5),
that the plungers (71) are provided with drive rollers (711, 711 '), at least one of which interacts with a screw cam (431) of the cam cylinder (43) and
that the gear train (5) has only spur gear pairs for the translation of the oscillating movement. Drive device according to one of claims 1 to 3,
characterized in that the gear train (5) is designed as a planetary gear (51, 52, 53, 54) and
that the web (51) of the planetary gear (5) with the vibratingly driven input shaft (4, 4 ', 4 ") and the sun gear (54) with the drive wheel (6) for the working element (gripper belt 61; gripper bar 62, 63) are drive-connected is. Drive device according to one of claims 1 to 4,
characterized in that the gear train (5) consists of two planetary gears (51, 52, 53, 54; 541, 55, 56, 57) of the same type arranged coaxially to one another,
that the sun gear (54) of the first planetary gear (51, 52, 53, 54) is connected to the web (541) of the second planetary gear (541, 55, 56, 57) and the sun gear of the second planetary gear is connected to the drive gear (6) , Drive device according to claim 1, 2 or 3 and claim 4,
characterized in that two oscillating movements directed in opposite directions are derived from the oscillating shaft (2) or the input shaft (4, 4 ', 4 "), of which the first oscillating movement directly on the web (51) of the planetary gear (51, 52, 53, 54) and the second oscillating movement with the direction of rotation opposite to the web (51) is guided onto the ring gear (53) of the planetary gear (51, 52, 53, 54). Drive device according to claims 1 and 6, characterized in that the oscillating shaft (2) has two oppositely directed oscillating levers (25, 26), of which the first oscillating lever (25) has a first spherical coupling (30) with the web (51). the planetary gear (51, 52, 53, 54) is drive-connected and
that the second rocker arm (26) is connected to the drive via a second spherical coupling (31) with the ring gear (53) of the planetary gear (51, 52, 53, 54). Drive device according to Claims 1 and 7, characterized in that the spherical couplings (30; 31) have two joints which are offset by 90 ° and directed transversely to the stroke direction, and
that the joints of the spherical couplers (30, 31) are provided with self-aligning bearings (self-aligning roller bearings 301). Drive device according to one of claims 1 to 3,
characterized in that the wheel gear (5) is designed as a cycloid gear (CYCLO gear) in which the force is transmitted by means of eccentrically rotating cams. Drive device according to one of claims 1 to 3,
characterized in that the gear train (5) is designed as a so-called harmonic drive gear with a deformable toothed ring rotating on an Egyptian disc, the toothed ring meshing with the internal toothing of a ring gear which has a slightly larger number of teeth.

Images