EP1259669B1 - Device for controlling the thread lever of a braider and a braider - Google Patents

Abstract

The present invention relates to a braider (1) comprising a device for controlling the thread lever (10). Said braider is formed by a curved path (30) that is closed in a circular ring-shaped manner, a sliding block (31) appurtenant thereto and a reverse gear (20) by means of which the direction of rotation of the drive motor is reversed in such a way that the group of the upper delivery bobbins and the group of the lower delivery bobbins rotate in opposing directions. The aim of the invention is to enable such a braider (1) to have a higher ceiling speed. The sliding block (31) and the curved path (30) are situated within the surface (32) of rotation, whereby said surface is circumscribed by the course of the thread lever (10) around a central axis (50) in relation to the braider (1), and/or the reverse gear (20) is provided with an internal ring gear which is fixed to the central pipe (3) and has a great reference diameter, a pinion circulating therein and an outer ring gear that is rotatably mounted on the central pipe (3) and has a small reference diameter. The pinion is rotatably mounted on a circulating axle which is rigidly connected to the housing. Said pinion causes the positive fit between the internal ring gear and the outer ring gear.

Description

The present invention relates to a device for Control of the thread lever of a braiding machine according to the generic term of claim 1 and a braiding machine according to the preamble of claim 9.

Such braiding machines are known, see e.g. EP 0 370 959A, catalog Spirka "Spirka quick-weaver". With these quick weavers are, so the catalog, depending on the number of each counter rotating coil groups, speeds up to possible at about 150 per minute.

The multitude of required gear couplings and kinematic parameters make this difficult Increase speed arbitrarily.

One of the key parameters of a braiding machine is the limit speed. This depends on several factors namely the type of control of the thread lever and / or the Type of gear coupling between the drive elements, the reversing gear and the coil carriers.

The thread lever must on the one hand above the weft bobbins be pivoted and on the other hand below the warp spools.

The upper end of the thread lever must be over the Warp spools go that the associated weft can be taken over by a thread guide plate, which the Defines the area of movement of the weft thread above the warp thread.

The control of the thread lever is usually controlled by the Combination of a circular, closed cam track with the associated sliding block. The cam track is arranged outside of that surface of revolution which the thread lever during the rotation of the weft spools circles.

The cam track therefore covers the entire braiding machine.

However, since the thread lever has a relatively large length, relatively high moments of inertia are to be expected as forces from the pair of slideways - consisting of sliding block and cam track- must be applied to the thread lever to impress its quick swivel motion. The relative large distance of the cam track from the center of rotation also causes relatively high relative speeds between Sliding block and curved track, so that here relatively high Surface pressures are expected.

On the other hand, the reverse gear is on braiding machines with central tube essential part to the upper coil former one counter to the lower coil carriers Imprint rotary motion around the central tube.

Since these mechanical gears make a significant contribution to Power requirements of a braiding machine, one always strives to Use gearboxes with low power consumption.

Here, however, the problem arises that in addition to a Reversal of direction of rotation between lower thread spools and upper Thread spools also maintained a predetermined translation must be specified by the braiding process is.

It is therefore an object of the present invention To improve the braiding machine so that higher speeds are possible become.

This problem is solved on the one hand by the invention Features of claim 1, on the other hand with the features of Claim 9.

There are therefore two different measures with which the limit speed of such braiding machines can be increased can.

These measures can be independent of each other and equally linked together on a single braiding machine become.

In the following, the measures of the Claim 1 received.

The advantage of this partial invention is that with a more compact design of the braiding machine, the weft and the warp spools are more accessible.

This advantage is achieved in that the previous one The braiding machine is surrounded by the fixed cam track is eliminated and replaced by an inwardly shifted cam track with which the accessibility of the weft bobbins and the warp bobbin is facilitated.

It is essential in this partial invention that the sliding block and that the cam track within that surface of revolution which are from the thread lever during its rotation is stretched around the central tube of the braiding machine.

The thread lever also executes on this surface of rotation the swivel movement that interweave between Warp and weft leads.

Through this partial invention, the relative speed becomes on the one hand reduced between sliding block and curved track, because the circle of intervention between the sliding block and Cam track is on a smaller radius than if the Cam track would be arranged outside the rotation circle.

Since the law of motion of the thread lever beyond given by the curvature of the so-called thread guide plate the inevitable geometrical result Shape the cam track so that the weft thread is under constant contact on the thread guide plate shifts up and down becomes.

The farther the circle of engagement between the curved track and Sliding block laid to the central axis of the braiding machine, the lower the relative speeds without the specified law of movement of the thread lever negatively affected would. In this respect, the target group should be sought between the sliding block and the curve track within the inner circle of the circumscribed circle. This offers the additional possibility of the swivel axis of the To store the thread lever in a hole in the gear housing, where the sliding block and curve track can lie in an oil bath.

The oil lubrication made possible in this way has so far been expected unreachable relative speeds between sliding block and curve path may be permissible.

The cam track can be used to simplify the construction be arranged on a ring console, which as a separate Component is rigidly connected to the central tube.

In addition, the pivot axis can be tilted in such a way with its end facing the central pipe to the braiding point is inclined. This is practically the exit end of the meant to braid material from the central tube. This enables an effective swiveling movement over the warp thread bobbins and under the warp spools with low forces. The relevant critical angle - measured to the normal plane the central axis - is 45 degrees. This results in being permissible Angular range: 45 °> alpha> O °.

If the cam track is then also around that Angle L inclined, like the swivel axis, results good surface removal between the sliding block and the curved track.

To compensate for voltage fluctuations, that arise when the thread lever is pivoted is additional a thread storage role provided that the temporary Thread placement of the weft thread when pivoting in the The sense is that the weft tension is practically constant remains.

Advantageous results from the other subclaims Developments of the invention. From the second partial invention there is the advantage that the housing for receiving of the braiding machine gearbox considerably smaller and more compact can be built, so that a good one Accessibility for the weft bobbins and the warp bobbins is guaranteed.

Due to the compact design of the housing, the resonance behavior the braiding machine cheaper, the limit speed can thus be increased. In principle, this partial invention is based on the reverse effect, which is caused by the in the internal ring gear revolving pinion is caused. The internal ring gear is certain, the inner circumferential pinion is supported its point of engagement with the external ring gear with a small Pitch circle diameter on the output side of the gear unit, which causes the reversal of the direction of rotation.

At the same time, this planetary gear arrangement allows adjustment the speed ratios required for the braiding process are necessary.

The particular advantage of this partial invention also lies especially in their independence from the measures of the Claim 1.

Nevertheless, this partial invention can be combined with the Features of claim 1 are used.

Fig.1

ein erstes Ausführungsbeispiel der Erfindung,

Fig.2

ein Ausführungsbeispiel der Erfindung mit geneigter Schwenkachse,

Fig.3

eine schematische Darstellung der inneren Kurvenbahn mit eingreifendem Kulissenstein,

Fig.4

ein Ausführungsbeispiel der Erfindung mit einer besonderen Ausgestaltung des Umkehrgetriebes,

Fig.5

das Umkehrgetriebe gemäß Fig.4 an einer Flechtmaschine mit außerhalb der Rotationsfläche liegenden Kulissenbahn.

The invention is explained in more detail below on the basis of exemplary embodiments. Show it:

Fig.1

a first embodiment of the invention,

Fig.2

an embodiment of the invention with an inclined pivot axis,

Figure 3

a schematic representation of the inner cam track with engaging sliding block,

Figure 4

an embodiment of the invention with a special configuration of the reversing gear,

Figure 5

the reversing gear according to Figure 4 on a braiding machine with a slide path lying outside the rotation surface.

Unless otherwise stated below, the following description always for all figures.

The figures show a braiding machine 1 in a schematic manner View.

A central tube 3 is rigid on a machine frame 2 struck.

The central tube 3 serves in the lower area of the receptacle a gear housing 5, which with a gear housing mounting 6 is rotatably arranged on the central tube 3.

Via the drive 4, the gear housing 5 is rotated imprinted, which also with the gear housing 5 connected slideway carrier 7 performs.

In the lower area of the gear housing 5 are lower Bobbin carrier 8 arranged, each having a weft bobbin 9 wear.

The weft thread is indicated by one not specified Breakthrough in the thread lever 10 and runs from there a deflection device 13, which is located at the upper end of the Thread lever 10 is located.

The thread lever 10 is pivotable about a pivot axis 11, which is movable in a pivot axis bearing 12.

From the deflection device 13 the weft runs Braiding point 14 to that on the outer circumference of the to be braided Langguts 15 is to be found.

While the long goods 15 only in the vertical upward direction is promoted, the weft bobbins perform one Rotation in a predetermined direction of rotation around the central tube 3 around. This rotary movement is predetermined by the drive 4.

You can now imagine that the thread lever 10 at its rotation about the central axis 50 a surface of revolution spans, which is concentric to the central axis 50. at the same time the thread lever 10 performs a pivoting movement its pivot axis 11. The pivot axis 11 is above the lower spools, the weft bobbin 9, and is with the Gear housing 5 connected so that the rotational movement of Thread lever 10 and gear housing 5 is synchronous.

As a result, the thread lever 10 and gear housing rotate 5 in a first direction of rotation around the central tube 3 Braiding.

At the same time, the thread lever 10 is through the positive Engagement between a sliding block 31 and an associated one Cam track 30 so positively controlled that he on that Rotation surface 32 on which it is about the central axis 50 rotates, an oscillating pivoting movement 35 takes place, which runs around its pivot axis 11. This Swiveling movement is caused by the course of the curved path 30, the latter on their closed path around the central axis 50 around.

The positive engagement between sliding block 31 and cam track 30 therefore characterizes a corresponding moment a movement on the swivel axis, which is indirect depending on the type or transferred directly to the thread lever 10 becomes. To get a braid with this arrangement, it is necessary to use the warp bobbin 9 in the first Direction of rotation 29a opposite second direction of rotation 29b to rotate.

For this purpose, a reversing gear 20 is provided which consists of a gear ratio 23 and an idler gear 21 exists.

The reverse gear serves the purpose of rotating the Gear housing 5 in an opposite to the first direction of rotation Convert direction of rotation and then the warp thread carriers 18 give up, each a warp bobbin 19th exhibit. The warp thread carriers 18 thus move in the direction of rotation opposite to the first direction of rotation 29a 29b around the central axis 50 and are thereby from the Slideway carriers 7 out, as well as the warp thread carriers 18 are only provided in segments.

This results in the area of the slideway carrier 7 with the warp thread carriers 18 an alternating immersion and Extending movement in that there are slideway carriers 7 and warp thread carriers 18 opposite to each other about the central axis 50 turn around.

For this purpose, the reversing gear 20, which serves as essential component has the intermediate gear 21.

The idler gear 21 is via the idler gear shaft 22 rigidly connected to the slide track carrier 7. It is about here around a bevel gear, which on the one hand with the warp thread carrier 18 and on the other hand with the inner ring 16 in a form-fitting manner Intervention is. The inner ring 16 is independent from the gearbox and also rotatable on the central tube 3 stored. The inner ring bearing 17 thus enables the Inner ring 16 independent of the transmission housing 5 around the central tube 3 turn around.

Since also gearbox 5 and inner ring 16 different Must have revs is according to 1 to 3 a translation stage 23 is also provided is supported on a ring bracket 24.

The ring bracket 24 is rigid with the central tube 3 connected.

4 and 5, the translation stage 23 explained again in a different embodiment become.

Here, the gear ratio 23 consists of an internal ring gear 25, rigid with the fixed ring console 24 connected is.

The internal ring gear faces within the gear ratio 23 the largest pitch circle diameter.

In the internal ring gear 25, a pinion 26 rotates, which opens a rotational axis 28 is rotatably mounted.

The revolving axis 28 is rigid with the gear housing 5 connected.

While the rotating pinion 26 on the one hand with the internal ring gear 25 is engaged, the inner ring 16 an external ring gear 27 with a small pitch circle diameter, with which the rotating pinion 26 also meshes.

The pinion 26 is consequently both with the internal ring gear 25 large pitch circle diameter as well as with the external ring gear 27 small pitch circle diameter in constant engagement and turns around together with the gear housing 5 the central axis 50 and on its orbital axis 28 because it by engaging the rigid internal ring gear 25 with its Gearing is forced to do so.

Therefore, the rotational movements of the inner ring 16 and of the gear housing 5 directed the same way. The direction of rotation is, however, reversed by the intermediate gear 21, so that the Warp thread carrier 18 in an opposite to the slideway carrier 7 Rotational movement is offset.

This is due to the symbols for the first direction of rotation 29a and the second direction of rotation 29b regardless of the respective Rotation speed (absolute) shown.

Since the sliding block 31 during this movement in the first direction of rotation 29a in the fixed cam track 30 expires, can be shown with an appropriate arrangement, for example in Fig.3 or in Fig.5, the thread lever a pivoting movement be imprinted.

The pivoting movement 35 takes place between the lower ones Pivot positions 33a and upper pivot positions 33b, while the thread lever 10 is guided around the central axis 50 becomes.

As Fig. 3 shows in addition, the sliding block sits 31 on a guide lever 44, which is of the geometric Pivot axis 45 of the pivot axis 11 has a distance.

Since the pivot axis 11 is in turn rotatably mounted, can by a suitably designed cam track 30 Thread lever 10 in a reciprocating pivoting movement be displaced while being guided around the central axis 50 becomes.

In the exemplary embodiments according to FIGS. 1 to 4, the Pivot axis 11 mounted in the gear housing 5.

In principle, this also applies to the storage of the Swivel axis in the embodiment according to Figure 5 too.

There, however, the pivot axis does not point towards Central tube 3 out, but away from this.

Accordingly, the cam track 30 sits in an outside of the Rotating surface 32 lying area of the braiding machine and points on the lateral surface facing the central tube 3 an engagement zone for the sliding block running there 31 on.

The cam track 30 is part of a braiding machine comprehensive maturity, which is as compact as possible Design of the reversing gear in the embodiment according to 5 can have a relatively small diameter.

This is also why the compact reversing gear favors the Embodiment according to Figure 5, the increase in the limit speed such braiding machines because the sliding pairing between Sliding block 31 and cam track 30 under relatively low Peripheral speeds.

The geometry of the gear housing 5 according to Figure 5 is not to scale. The actual volume of the gearbox 5 is considerably smaller and thus leaves the inside diameter of the tire with the cam track 30 accordingly shrink.

The respective path-time law of the thread lever movement is predetermined by the basic contour of the thread guide plate 34.

The decisive factor in the exemplary embodiments according to FIG. 1 to 4 that both the sliding block 31 and the cam track 30 lie within the surface of rotation 32 which the thread lever rotates around the central axis 50 circumscribes.

Those initiated on the thread lever to control it Forces will therefore come from an intervention group, the Radius smaller than the rotation area circumscribed by the thread lever 10 32 is.

In addition to this, it is provided that the sliding block 31 and the cam track 30 within the inner end 36 of the Swivel axis 11 lie. In this case, the circle of intervention lies between sliding block 31 and curve track 30 within of the circle that from the inner end 36 of the Swivel axis 11 is circumscribed.

In addition, Figures 1 and 4 show that the pivot axis 11 rotatable in a bore 37 of the gear housing 5 is stored.

It is also intended to mount the gearbox on the central tube and on the outer circumference of the inner ring 16 and also the pivot bearing of the pivot axis 11 seal on the gearbox housing with radial seals 39a-c, the oil level 38 within the gear housing 5 Realize that sliding block 31 and cam track 30 in an oil bath lie. The oil-tight closed gear housing 5 can if necessary, be provided with a suitable drain plug.

Since the cam track 30 in turn on the ring bracket 24 attached, can thus be a wear-free and environmentally clean Permanent lubrication between sliding block 31 and Generate cam track 30, associated with the advantage clearly higher relative speeds and thus higher speeds for the braiding machine.

In any case, however, it is fulfilled that the cam track carrier, the outer circumference in the exemplary embodiments shown the ring console 24, practically in the extension to the central axis 50 of the annular spanned by the pivot axis 11 Rotation plane 40 lies.

This results in a direct and effective transfer the course of the curved path 30 on the thread lever 10, because the force-transmitting links between sliding block 31 and pivot axis 11 are short and compact.

In addition to this, the pivot axis 11 with its for Central tube 3 facing end 41 towards the braiding point 14 be inclined. This measure is effective Braid geometry and is known from the prior art.

To ensure an effective intervention between Sliding block 31 and curve track 30 to come, the curve track be inclined by the same angle of inclination so that the Sliding block with the largest possible contact to the Walls of the cam track 30 attacks.

In addition to this, it is now provided that with the Pivot axis 11 of the thread lever 10 a thread storage roller 43 is connected, which is concentric to the pivot axis 11 Has weft groove 46.

This measure serves to compensate for changes in voltage in the weft, caused by the swiveling movement of the Thread lever 10 between the lower pivot position 33a and upper pivot position 33b are caused.

The geometrically optimal course of the curved path 30, and so that the alternating movement of the sliding block 31 during its circulation is principally due to the curved triangle of threads determined which between the braiding point 14th and the deflection device 13 clamped on the thread lever 10 is and lies above the envelope that the Warp threads between their warp bobbins 19 and the individual Rewrite braiding points 14.

However, since these laws of motion are well known are, see catologe "Spirka Schnellflechter", should be on this not be discussed further.

In the exemplary embodiments according to FIGS. 4 and 5, there is additionally shown that internal ring gear 25, rotating pinion 26 and outer ring gear 27 in one and the same radial plane 48 with respect to the central tube 3 and in this radial plane comb together.

This measure serves to avoid any bending moments on the bearing of the pinion axis, which together with the gear housing 5 rotates and therefore called the rotation axis 28 becomes.

In addition, with one and the same external toothing on the circumferential Pinion 26 including the entire gear coupling the translation between the drive motor and the inner ring 16 causes.

This is achieved in that the pinion 26 both immediately with the internal ring gear 25 as well as directly the outer ring gear 27 meshes, the intermediate gear 21 of the Output side of the external ring gear 27 is acted upon and is at the same time in engagement with a ring gear that is attached to the upper coil former 18 is attached ..

For this purpose, the idler gear sits on an idler gear shaft 22, which is rigidly connected to the gear housing 5 and lies above the radial plane 48, in which inner ring gear 25, rotating pinion 26 and external ring gear 27 with one another comb.

LIST OF REFERENCE NUMBERS

1

braiding

2

machine frame

3

central tube

4

drive

5

gearbox

6

Transmission gearbox bearing

7

sliding way

8th

lower bobbin

9

Cop

10

up lever

11

swivel axis

12

Pivot shaft bearing

13

deflecting

14

braiding

15

long goods to be braided

16

inner ring

17

Inner ring storage

18

warp beam

19

warp thread

20

reverse gear

21

idler

22

idler

23

translation stage

24

ring console

25

Internal ring gear

26

rotating pinion

27

External gear

28

axis of rotation

29a

first direction of rotation

29b

second direction of rotation

30

cam track

31

sliding block

32

surface of revolution

33a

lower swivel position

33b

upper swivel position

34

Fadenleitschild

35

pivotal movement

36

inner end of the swivel axis

37

Bore of the gearbox

38

oil level

39a, b, c

radial seal

40

Rotation plane of the swivel axis

41

end of the swivel axis facing the central tube

42

tilt angle

43

Thread storage roll

44

guide lever

45

geometric pivot axis

46

Weft groove

48

radial plane

50

central axis

Claims (12)

1. Device for controlling the thread lever (10) of a braider (1), formed from the combination of a curved path (30) closed in the manner of a circular ring and an associated sliding block (31) which is disposed inside the transmission housing (5), wherein the thread lever (10) has a pivot axle (11) which is mounted above the lower delivery bobbins (weft yarn bobbins 9) in a bore (37) in the transmission housing (5) which is rotationally driven in a first direction of rotation (29a) about the central pipe (3) of the braider (1), wherein the thread lever (10) circumscribes a surface of rotation (32) by the rotational movement of the transmission housing (5) and on this surface of rotation (32) has an oscillating pivot movement (33a, 33b) about its pivot axle (11) imposed upon it by means of the sliding block (31) and wherein the rotational movement (29a) of the transmission housing (5) is converted by a reversing gear mechanism (20) with an intermediate wheel (21) into a second direction of rotation (29b) opposite to the first direction of rotation (29a) and is then imparted to the bobbin holders of the warp yarn bobbins (19), characterised in that the sliding block (31) and the curved path (30) lie inside the surface of rotation (32) and that the transmission housing (5) and the bore (37) of the transmission housing (5) are closed in an oil-tight manner (39a, b, c) and the sliding block (11) and curved path (30) lie in the oil bath.
2. Device as claimed in claim 1, characterised in that the curved path (30) is positioned on a curved path support in the form of an annular bracket (24) which is connected in a non-rotatable manner to the central pipe (3).
3. Device as claimed in claim 2, characterised in that the annular bracket (24) lies inside the transmission housing (5).
4. Device as claimed in claim 3, characterised in that the curved path support (e.g. annular bracket 24) is disposed practically as an extension of the central axis (50) of the plane of rotation (40) fixed by the pivot axle (11).
5. Device as claimed in any one of claims 1 to 4, characterised in that, with its end (41) which points towards the central pipe, the pivot axle (11) is inclined towards the braiding point (14).
6. Device as claimed in claim 5, characterised in that the angle of inclination (42) with respect to the radial direction of the central pipe (3) is not greater than 45 degrees.
7. Device as claimed in any one of claims 5 or 6, characterised in that the curved path (30) is inclined by the same angle of inclination (42) as the pivot axle (11).
8. Device as claimed in any one of claims 1 to 7, characterised in that a yarn storage roller (43) is connected to the pivot axle (11) of the thread lever (10), the yarn storage roller preferably having a weft yarn groove (46) concentric to the pivot axle (11).
9. Braider (1) having a central pipe (3) and a transmission housing (5) rotationally driven in a first direction of rotation (29a) about the central pipe (3), on which transmission housing bobbin holders (8) for the lower delivery bobbins (9) are positioned, and having upper bobbin holders (18) for the upper delivery bobbins (19) which are also rotatably mounted about the central pipe (3), wherein between the lower delivery bobbins and the upper delivery bobbins a positive-locking reversing gear mechanism (20) is provided having an intermediate wheel (21) which on the input side is influenced by the direction of rotation (29a) of the housing and on the output side produces the second direction of rotation (29b) opposite to the first direction of rotation (29a), the upper bobbin holders (18) of the upper delivery bobbins (19) being influenced by this second direction of rotation, having a device in accordance with the preamble of claim 1 or one of the preceding claims, characterised in that
   the reversing gear mechanism (20) has an inner toothed ring (25) of large reference diameter, which is fixed with respect to the central pipe (3), a pinion (26) circulating therein and an outer toothed ring (27) of a small reference diameter rotatably mounted on the central pipe (3), and that the circulating pinion (26)
   is rotatably mounted on a circulating axle (28) rigidly connected to the transmission housing (5) and
   produces the positive-locking connection between the inner toothed ring (25) and the outer toothed ring (27),
   and that the transmission housing (5) is closed in an oil-tight manner and the sliding block (31) and curved path (30) lie in the oil bath.
10. Braider as claimed in claim 9, characterised in that the inner toothed ring (25), the circulating pinion (26) and the outer toothed ring (27) mesh with each other in the same radial plane (48) of the central pipe (3).
11. Braider as claimed in claim 9 or 10, characterised in that the circulating pinion (26) meshes both directly with the inner toothed ring (25) and also directly with the outer toothed ring (27) and that the intermediate wheel (21) is influenced by the driven side of the outer toothed ring (27) and is mounted on an axle (28) which is rigidly connected to the housing (5) and is at the same time in engagement with a toothed ring, on which axle the upper bobbin holders (18) are positioned.
12. Braider as claimed in any one of the preceding claims, characterised in that the rotational speed ratio of the rotational speed of the outer toothed ring (27) to the housing (5) is 3:1.

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