US3241573A - Reed and shuttle driving apparatus for a progressively shedding type loom - Google Patents

Description

4 Sheets-Sheet 1 H. FEND PROGRESSIVELY SHEDDING TYPE LOOM REED AND SHUTTLE DRIVING APPARATUS FOR A March 22, 1966 Filed July 15, 1963 M xx March 22, 1966 H. FEND 3,241,573

REED AND SHUTTLE DRIVING APPARATUS FOR A PROGRESSIVELY SHEDDING TYPE LOOM 4 Sheets-Sheet 2 Filed July 15, 1963 mm W March 22, 1966 H FE 3,241,573

ND REED AND SHUTTLE DRIVING APPARATUS FOR A PROGRESSIVELY SHEDDING TYPE LOOM Filed July 16, 1963 4 $heecs-Sheet :3

March 22, 1966 H. FEND REED AND SHUTTLE DRIVING APPARATUS FOR A rnoeamssxvwz SHEDDING TYPE LOOM 4 Sheets-Sheet 4 Filed July 15, 1963 M M E $5 A fm m mr a 6 mm W n?" m m z WH 1 a 3 I 227 NI l q W w United States Patent 3,241,573 REED AND SHUTTLE DRIVING APPARATUS FOR A PROGRESSIVELY SHEDDING TYPE LOOM Heinrich Fend, Zurich, Switzerland, assignor to Verwaltungsgeseilschaft der Werlizeugmaschinenfabrik Oeriilion, Zurieh-Oerlilron, Switzerland Filed July 15, 1963, Ser. No. 294,958 Claims priority, application Switzerland, July 23, 1962, 8,797 62 3 Claims. (Cl. I39-12) The invention relates to beat-up means for progressive shedding looms with a plurality of exchangeable shuttle driving members lying side by side and distributed over the whole width of the warp. On each member there is attached a group of reed teeth for beating up the weft thread, the reed teeth of all groups having a constant dent over the whole width of the beat-up assembly. It is then important, that by exchanging the individual shuttle driving members having a certain number of reed teeth against others having a difierent number of teeth it is made possible to utilize a great many different warp densities in such a manner that the number of warp threads between .any two adjacent feed teeth remains constant over the whole width of the weave.

With known beatup devices of the kind referred to which have an electromagnetic drive of the shuttles, the groups of reed teeth have a width, and accordingly their driving members have also a uniform width or pitch, in the order of magnitude of 1.9685 inches. With such a width it is easily possible to grade the number of reed teeth per group finely enough to accommodate a large range of warp densities.

For progressive shedding looms, in which the same driving members mechanically drive the shuttles as well as the groups of reed teeth for beating up the weft thread, such a pitch is unsuitable, as will be explained hereinafter.

In progressive shedding looms of ordinary width of about 5 feet to 6.5 feet it is usual to drive about 6 to 8 shuttles simultaneously through the warp one behind the other, with as many individual travelling sheds formed by their driving members. With shuttles driven in such a manner, about a dozen of driving members continuously relieving one another are engaged simultaneously on the shuttle. An even larger number of driving members outside the region of a shuttle serve to, inter alia, beating-up the weft thread just laid in a traveling shed which is between 10 inches to inches in length. Assuming about forty driving members for each travelling shed, the length of such a shed having the usual width of 1.9685 inches would amount to about 6.56 feet, i.e., six to eight times as much as permissible in the usual loom.

The object of the invention consists in providing a beat-up device for progressive shedding looms with a common mechanical drive for the shuttles and the reed having narrow exchangeable packets of reed teeth to allow a variety of warps having a great variety of densities to be used with a constant number of warp threads between any two adjacent reed teeth.

For purposes of clarity the term progressive shed is limited to the sheds formed across the width of the warp and the term wave is intended to include those areas of the warp in which a shed is formed and the reed and drive means involved in functioning in each formed shed and the undulating configuration through which they and the warp threads move.

With this and other objects in view, which will become apparent later from this specification and the accompanying drawings, I provide a beat-up device for progressive shedding looms, comprising in combination: a fixed casing, a plurality of shuttle drive members lying side by side distributed over the whole width of the warp, and guided on said casing, a group of reed teeth mounted on each of said drive members for beating up the weft thread, the reed teeth being uniformly spaced over the whole width of the warp and the individual groups of reed teeth differing from one another in their number of reed teeth, and driving means mounted on said casing in operation reciprocating said members with a mutual ofiset corresponding to the wave or shed shape.

In this manner any densities of warp threads can be taken into account, since the quotient of the sum of all Warp threads and that of all driving members need no longer be a whole number, such as ihitherto, which restricted considerably the number of the various warp densities hitherto usable.

In addition to a figure for the explanation of various relations, an embodiment of a beat-up device for a flat weaving machine, and a modification of a beat-up device according to the invention are illustrated in the accompanying drawings, in which:

FIGURE 1 is a side elevation in section of a beatup device with the shuttle drive, and with the shuttle in the weaving shed, some components lying further back being omitted;

FIGURE 2 shows the same arrangement in front elevation with the casing broken away and with the reed teeth partly broken oif;

FIGURE 3 is a plan view showing diagrammatically the driving members with the reed teethpartly broken olt in their positions offset wave shape in the form of one travelling wave length;

FIGURE 4 diagrammatically shows three groups of reed teeth with equal numbers of teeth according to the prior art, for the explanation of various relations;

FIGURE 5 diagrammatically shows in elevation five groups of reed teeth having different numbers of teeth according to the invention;

FIGURE 6 diagrammatically shows a modification of six groups of reed teeth having different numbers of reed teeth;

FIGURE 7 illustrates a detail of FIGURE 1 upon an enlarged scale; and

FIGURE 8 is a View illustrating two consecutively ararnged cross-sections as indicated by the section lines VIII.

In FIGURE 1, on a shaft 9 and 9a, respectively, sets 3 and 4 of cam discs are fitted by means of keys 10 and 10a, respectively which cam discs are individually denoted 3a, 3b, 3c, 3d etc. and 4a, 4b, 4c, 4d etc. in FIGURE 1 and are arranged one behind the other, each of these cam discs being angularly offset a certain amount on the shaft 9 and 9a, respectively, relative to the subsequent cam disc. On an axle 6, levers 1 with rollers 2 are mounted pivotally independently of each other, those levers individually denoted 1a, 1b, 10 etc. with a roller 2a, 2b, 2c etc. journalled on a pin 5a, 5b, 50 respectively being arranged between each cooperating pair of discs such as 3a and 4a, 3b and 4b, 3c and 40 etc. of the discs, respectively.

A plurality of slides 7, consisting of individual slides such as 7a, 7b, 7c constructed as members for driving and completely guiding the shuttles 16, are guided predominantly in the direction of the warps in slots 8 lying side by side. These slots 8 are arranged in the casing 32. In the casing 32 there is a cut-out from below extending over the length B, through which the levers I reach upward into the slots 8 and wherein they are guided laterally. On the levers I slider blocks 11 are mounted, which have the same width as the levers I themselves and are each guided in the same slot as the associated lever.

These levers 1 engage with said Sliders blocks 11 from below into a recess of the individual slides 7.

The sets of cam discs 3, 4 are so constructed that, upon synchronous rotation of the two shafts 9 and 90, they are permanently in contact without any play with the rollers 2, and move the slides 7 by means of the levers 1 in an identical manner but with a phase offset in accordance with a predetermined law defining the slope of the travelling shed, toand-fro from a rear end position to a forward beat-up position. A dovetailshaped slot 13 extending transversely of the slots 8 over the full extent of the casing 32 serves for accommodating a ledge 12, which in turn holds all the slides 7 in the slots 8.

The slides 7 carry, as shown in FIGURE 1, at their left hand side ends a forked projection 14 having a recess 15. An arcuate shuttle 16 engages with its likewise arcuate lower rib 2i] and its two flanks 21 and 31 (FIGURE 3) into a sickle-shaped guide formed by the recesses of the forked projections of a plurality of slides 7, which guides represents a wave trough as viewed from the fell 26 Within the wave shape of the mutually offset recesses 15.

A convenient shape of the travelling wave is illustrated in FIGURE 3. The shape shown repeats itself any time after an angular offset of 360 of the cam discs so that permanently five to eight of such waves are formed. The travelling waves thus formed by the projections 14 proceed in one or the other direction transversely of the warp threads depending on the sense of rotation, and thus carry along the shuttle l6 lying in the wave trough facing the fell 26. Each shuttle 16 is in engagement only with a predetermined number of slides 7, namely with those, which actually form the trough of the wave, and has for this purpose a concave formation of the driving and guiding surfaces.

In addition to the projection 14 group 27 of reed teeth 22 is mounted on each slide which group is held together by means of a connecting member 23. Each of the slides 7 together with its group 27 of reed teeth is exchangeable, for which purpose however firstly the ledge 12 and the cover 38 are to be removed. The warp threads 25 enclosing the shuttle run between the individual reed teeth 22 to the fell 26 and thus form the weaving shed, in which the shuttle is held by the slides 7 and their projections 14, respectively. The individual reed teeth 22 are moreover connected at their upper ends by outer connecting members 24. The reed teeth 22 serve to beating-up the weft thread into the fell 26 in the forward beating-up position of the slides 7, in which the projections 14 have emerged from the weaving shed.

As will be seen in FIGURE 3, owing to the favourable shape of the shuttle 16 and to the compact shape of the travelling wave it is possible, to let the slides stand still in the forward beating-up position for a short while, in order to attain in this manner a favourable binding in of the freshly inserted weft thread.

The weft thread 28 is stored in a cavity in the shuttle to be delivered therefrom to the fell of the fabric during operation. In order to keep the shuttle small, preferably only a storage of weft thread corresponding to one pick is accommodated therein.

As shown in FIGURE 7 the entire length of the side 21 of the shuttle 16 contacts the rear edge 19 of the recess in the projection 14 and also the forward edge 18 of the recess of the projection contacts the flank 31 of the shuttle. Since the two edges 18 and 1% converge upwardly, the recesses 15 diverge downwardly. Since the rib 20 has a profile corresponding to the recesses 15, the shuttle, which rests with its underside on the upper edges of the projections 14, is firmly guided in these projections, so that it can move only laterally in accordance with the movement of the slides 7.

In FIGURE 3 the slide 7:: is at the rear dead centre position and is accordingly for a moment at a standstill.

All the sldes located to the left in FIGURE 3 move towards the left in the direction of the arrow, some of the forward edges 18 of the recesses of projections 14 cooperating with the mounting member of driving surface 51, which is inclined relative to the driving direction, and shift the shuttle 16 in FIGURE 3 downwardly. Similarly, all the slides, which in FIGURE 3 lie to the right of the slide 7a and which are not yet in the forward beating-up position, move in the opposite direction or forward, some of their rear edges cooperate with the driving surface 52 of shuttle 16 to push it downwardly in FIGURE 3. The straight line guidance of the shuttle on a track parallel to the fill 26 is taken care of only by the slides, which are in motion, thereby that the rear edges 19 of these projections lying below the slide 7a cooperate with the guide surface 53, and the forward edges 18 of these slides lying above the slide 752 cooperate with a second guide surface 54.

All the groups of reed teeth 27 of all the slides 7 taken together form, as it were, a reed extending over the whole width of the warp and moving in a wave-shape, the dents between the reed teeth 22 being identical across the width of the beat-up assembly. Also the slides carrying the groups of reed teeth 27 have predominantly a constant width or pitch. The number of warp threads 25 drawn in between any two adjacent reed teeth may differ depending on the spacing of the warp or for other reasons.

Hereinafter the relations applicable in general between the values mentioned will be explained with reference to FIGURE 4:

The characters used hereinafter have the following meaning:

S pitch, or mean pitch, respectively, of the slides in inches.

Z:dent size or the spacing between the reed teeth in inches.

K number of warp threads per inch of the width of the weave.

E number of warp threads between any two adjacent reed teeth.

T number of reed teeth per group of reed teeth mounted on a slide.

S'=pitch of a formation in inches.

T total number of teeth per formation.

A number of reed teeth groups per formation.

It will be readily seen that under the assumption of a uniform pitch of slides:

Considering the number of warp threads per group of reed teeth, there exists the relation:

Hence:

wherein T as the number of teeth must be a whole number.

In an ordinary wave or progressive shed weaving machine for cotton, the number of warp threads per 0.3937 inch amounts to about 20 to 60, while the number of warp threads between any two adjacent reed teeth varies between 1 and 3. Assuming for example E 2 and S:0.l968 inch. From this it follows that Since T must be a whole number, the assumption of a constant number of warp threads between any two adjacent reed teeth implies necessarily the use of warps having a number of warps per inch K which is a whole number multiple of four, ie for example warps having a figure of K 20 in conjunction with a number of reed teeth per group T:5 as according to FIGURE 4.

5, If for the same figure of E=2 the pitch of the slides S is four times larger, namely 0.7874 inch, it follows that so that with such a pitch of the slides all warps having whole numbers of warp threads per inch are permissible for a uniform number of warp threads between any two adjacent reed teeth. A pitch of the slides 5:0.7874 inch is, however, undesirable in view of its detrimental effect on the shape of the travelling waves and. on the size of the shuttles.

In FIGURE 5 any two consecutive groups of reed teeth 27 constitute a formation repeating itself all over the width of the weave, the individual groups of reed teeth having numbers of reed teeth differing from one another. For example one of the two groups of reed teeth of a formation has six, and the other has seven reed teeth.

With a mean slide pitch of S=0.1968 inch there results a pitch of formation S'=2 S=0.3937 inch. For the total number of teeth of one formation and a number of warps per interstice between consecutive reed teeth E=2 there results accordingly the following relation:

For a number of warps per 0.3937 inch of K=26 for example there results 13 for a formation, or as stated, 'six teeth for one group of reed teeth, and seven for the other group of the formation. Accordingly, with a beatup device according to FIGURE 5 all the warps having an even number per 0.3937 inch may be used with a uniform number of warp threads in the said interstices of the reed teeth, i.e. twice as many different warps as with devices according to the prior art.

FIGURE 5 shows that the individual groups of reed teeth must have different lateral positions relative to their associated driving members i.e. to their slides in order to permit a regular pitch of the slides.

In FIGURE 6, which shows a modified embodiment by way of example, any four consecutive groups of reed teeth 27 form an analogous formation, three groups of each formation having five, and any fourth group having six reed teeth. Per formation there results, with a mean pitch of the slides of S=0.1968 inch, a pitch of formations of S'=4S=0.7874 inch. For the total number of teeth T of one formation there results, with a figure of E=2, the relation:

i.e. with an arrangement according to FIGURE 6 any warp having a whole number of warp threads per 0.3937 inch may be used. For example with a number of warp threads K:21 per 0.3937 inch the total number of reed teeth T' of a formation is likewise 21, i.e. as illustrated in FIGURE 6, any three groups of reed teeth of a formation have five, and the fourth has six reed teeth. With a uniform number of warp threads per interstice and a pitch of the slides corresponding to practical requirements it sufiices accordingly, if a number of consecutive groups of reed teeth of a number of teeth differing from one another forms re-current formation of identical kind over the whole width of the weave and it is sufficient, if the numbers of teeth of the various groups of reed teeth differ not more than one tooth for the same number of warps per 0.3937 inch. For a figure of E=2 and a pitch of the slides of S =0.1968 inch the permissible number of groups of reed teeth constituting a formation amounts to a maximum of four.

It should be emphasized that even more formations suitable for practical purposes may be formed in which for narrow pitches of the slides any warps having a whole number of warp threads per 0.3937 inch is permissible with a uniform number of warp threads per interstice. When it is required that L K A then necessarily S/E=1, and S'=E. Since the pitch of the formations S is equal to the product of the number A of groups of reed teeth groups per formation by the mean pitch of the slides, there results:

For E=2, e.g., A=3 and S=2/3 of 0.3937 inch, or A=6 and S=1/3 of 0.3937 inch, while for E=3, A=5 and S=.2362 inch is permissible, or A =6 and S=0.1968 inch.

Moreover it is obviously possible to make arrangements which permit an even finer sub-division of the warps per inch. In such a case for example T=2K or =3K, etc., i.e.

respectively, such as for E=2, A=6 and 8:2/3 inches, or A=9 and S=2/3 inches.

1 claim:

1. A beat-up device for the weft thread in progressive shedding looms with a short wave length comprising in combination a fixed casing, a plurality of shuttle drive members lying side by side distributed over the whole width of said beat-up device, means guiding said members on saidv casing, reed teeth uniformly spaced over the whole width of the warp, a group of reed teeth mounted on each of said drive members for beating-up the weft thread, said groups of reed teeth differing from one another in their lateral position relative to their associated drive member, said groups of reed teeth differing from one another in their number of reed teeth whereby formations of consecutive groups of reed teeth of different numbers of reed teeth will recur identically over the whole width of the warp, and driving means mounted on said casing reciprocating said members with a mutual offset corresponding to the Wave shape.

2. A beat-up device as claimed in claim 1, wherein the maximum number of said consecutive groups of reed teeth constituting a formation amounts to four.

3. A beat-up device as claimed in claim 1, wherein the maximum difference in the number of teeth of said groups of reed teeth amounts to one for the same number of warp threads per unit length.

References Cited by the Examiner UNITED STATES PATENTS 720,181 2/1903 Salisbury 139-12 FOREIGN PATENTS 1,237,034 6/ 1960 France. 1,072,569 12/1959 Germany.

522,814 4/1955 Italy.

DONALD W. PARKER, Primary Examiner.

Claims (1)

1. A BEAT-UP DEVICE FOR THE WEFT THREAD IN PROGRESSIVE SHEDDING LOOMS WITH A SHORT WAVE LENGTH COMPRISING IN COMBINATION A FIXED CASING, A PLURALITY OF SHUTTLE DRIVE MEMBERS LAYING SIDE BY SIDE DISTRIBUTED OVER THE WHOLE WIDTH OF SAID BEAT-UP DEVICE, MEANS GUIDING SAID MEMBERS ON SAID CASING, REED TEETH UNIFORMLY SPACED OVER THE WHOLE WIDTH OF THE WARP, A GROUP OF REED TEETH MOUNTED ON EACH OF SAID DRIVE MEMBERS FOR BEATING-UP THE WEFT THREAD, SAID GROUPS OF REED TEETH DIFFERING FROM ONE ANOTHER IN THEIR LATERAL POSITION RELATIVE TO THEIR ASSOCIATED DRIVE MEMBER, SAID GROUPS OF REED TEETH DIFFERING FROM ONE ANOTHER IN THEIR NUMBER OF REED TEETH WHEREBY FORMATIONS OF CONSECUTIVE GROUPS OF REED TEETH OF DIFFERENT

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