FR3005304A1 - BOOT MACHINE MODULE AND MACHINE EQUIPPED WITH SUCH A MODULE - Google Patents

Abstract

The linkage attachment module 2 for a bunching machine comprises a retaining assembly 100, a tying assembly 200 and a gearbox 11. The gearbox 11 has an input adapted to receive a motor shaft and outputs formed of a plurality of driven shafts 23, 31, 33, 35, 37. It is configured to sequentially rotate each of the driven shafts 23, 31, 33, 35, 37 under the effect of a rotation of the drive shaft. 'engine shaft. The retaining assembly 100 and the tying assembly 200 comprise elements configured to be animated under the effect of the rotation of one of the driven shafts 23, 31, 33, 35, 37.

Description

BOW. BACKGROUND OF THE INVENTION The invention relates to the field of tying an object or a set of objects by means of a link with formation of a node. .

Tying to surround, tighten and tie together different kinds of objects can be done manually. For example, tying is used to tie bouquets of flowers, vegetable boots, cardboard boxes, electrical wires, newspapers, etc. Manual tying is long, tedious and expensive. In general, the term "bundling" is used to designate a string of a bundle of objects.

In the field of meat production, for example for the production of meatballs, these operations are generally carried out at low temperature. Manual operations are all the more difficult and unpleasant. Tying devices are known to partially automate these tasks. It is already known, in particular according to the publication WO 8503272, tying devices by means of a link forming a node of the type comprising a movable arm to bring the link. The knot made by means of this device comprises two long link ends which not only lead to a waste of thread, but may further hamper the subsequent handling of the tied object. The applicant has proposed tying devices with a linkage movable arm in which the different sets of the machine work close to each other. This reduces thread consumption by shortening the link ends beyond the node. The French patent application FR 2,736,618 filed July 13, 1995 describes such devices. Although more efficient than previous devices, these mobile arm devices have limited operating rates. In addition, the use of lubricant in the form of oil or grease is necessary to ensure a reasonable service life of the parts. These lubricants tend to cause soiling both of the machine equipped with such devices, operators and objects to be tied. In industrial use, regular monitoring of proper lubrication and grease or oil applications at many locations of the device is required. It is also necessary to clean the projections and flows of lubricant. These operations generally require the device to be shut down, which limits productivity. Sanitary standards, especially for tying food items, are all the more restrictive.

Waste and dirt can also come from the objects treated, creep into the mechanisms of the machine and reduce its effectiveness. Typically, flowers and bunches of onions carry dust and dirt that quickly foul the bunching machine mechanisms. Machine maintenance significantly reduces their uptime.

The invention improves the situation. The Applicant proposes a link fixing module for a bunching machine. The module comprises: - a link retainer, - a link knotting set, and - a gearbox. The gearbox has an input adapted to receive a motor shaft and outputs formed of a plurality of driven shafts. The gearbox is configured to sequentially rotate each of the driven shafts under rotation of the drive shaft. The restraint assembly and the tying assembly include elements configured to be animated by rotation of one of the driven shafts. The module may furthermore have the following characteristics, whether they are combined with one another or not: the module comprises a link guiding assembly comprising elements configured so as to be animated under the effect of the rotation of one of the driven shafts; . In this case, the positions of the strands of the link during the operations of fixing the link are better controlled. The link is less sensitive to the external environment such as drafts, temperature, humidity, etc. The risks of malfunction are reduced. The link is less likely to get tangled up and stop the machine. The control of these risks is all the more important as the operating rates are high. - The module comprises a chamber arranged to be traversed by the motor shaft and the driven shafts. The enclosure is configured so that the inside and the outside of the transmission box are isolated from each other in a substantially sealed manner during operation. The presence of the enclosure structurally delimits the gearbox. The interior may contain products, especially lubricants, that it is not desirable to see in contact with the objects to be treated. These products are also contained and protected from the external environment. The losses are reduced. Maintenance operations such as emptying the gearbox are easy and fast. - The knotting assembly comprises an interior space housing means for transmitting the driving force. The inner space and the outside of the knotting assembly are isolated from each other substantially tightly. The knotting assembly forms an enclosure isolating the interior and exterior of the knotting assembly. The interior may contain products, especially lubricants, that it is not desirable to see in contact with the objects to be treated. These products are also contained and protected from the external environment. Losses are reduced. Maintenance operations such as emptying the knotting set are easy and fast. The gearbox is configured so that the sequential rotation of the driven shafts defines an operating cycle. The elements of the restraint assembly and the tying assembly have similar positions at the beginning and at the end of the operating cycle. This organization in repetitive cycle exempts from an initialization phase between each cycle. Productivity is improved. In addition, the indexing of the different parts of the module is automatic. Apart from a few optional settings and calibrations during installation, the machine's setting operations in use can be deleted. - The module has an operating cycle at the end of which a portion of wire is held by the retaining assembly. The operator is dispensed with a tedious and time-consuming operation such as priming the machine by introducing a wire end into the module for each new link. Productivity is improved. The safety of people is also improved because it is not necessary to intervene near mechanical organs capable of operating at high speed. - The module has a configuration in which the gearbox is adapted to receive a motor shaft whose rotational speed gives the operating cycle a duration of less than 0.7 seconds. Such a cycle time allows significant productivity. In addition, such a module can be associated and integrated with industrial chains, which until now have been too fast for known tying devices. - The gearbox houses at least one anti-rotation mechanism arranged to sequentially prevent the rotation of one of the driven shafts. This mechanism compensates for the effects of inertia. The risks of accidental deindexation of the various parts of the machine are reduced. Shocks and breaks in mechanical parts are reduced. - The link fixing module is in the form of a mounting kit comprising a set of parts capable of being assembled to form the module. Such a presentation makes it easier to transport and to reduce the risks of deterioration during transport. In addition, several interchangeable parts can be proposed to make the module more adaptable, for example to be able to treat objects of various shapes and sizes.

In another aspect, the invention relates to a bundling machine provided with a housing arranged to receive a bunching article and a wire reel arranged to unwind the wire around the article and form a link. The machine is equipped with a module according to the first aspect and a motor shaft received in the module. The machine may furthermore have the following characteristics, whether combined or not: - The machine is arranged to have a thread unwinding cycle around the article of less than 0.5 second duration. Such a cycle time allows significant productivity. In addition, such a module can be associated and integrated with industrial chains, which until now have been too fast for known tying devices. - The wire reel is arranged to unwind the wire around the article over at least two turns before the module is activated. Depending on the type of link desired, the machine can be parameterized to form links with a single node and as many loops as desired without the configuration of the module or machine need to be mechanically modified. - The machine is configured to successively rotate the reel and the motor shaft. The operations are then largely automated. A single action of an operator or a computer instruction of a control box is enough to form a loop (or more) and then to fix the link.

Other features, details and advantages of the invention will appear on reading the detailed description below, and the attached drawings, in which: FIG. 1 is a general perspective view of a machine according to the invention; FIG. 2 is a schematic perspective view of a part of a machine according to the invention; FIG. 3 is a view from the rear of the part shown in FIG. 2; FIGS. 4 and 5 are perspective views of a link fixing module according to the invention, - Figure 6 is a view from the rear of the module of Figures 4 and 5, - Figure 7 is a view from the rear of the module of the 4 and 5 on which parts have been removed, FIG. 8 is an exploded view of the module of FIG. 7 on which parts have been removed, FIGS. 9 and 10 are partial and exploded views of the module of FIGS. 4 25 and 5, - Figures 11 and 12 are views of some elements of the m FIGS. 13 is a perspective view of a restraint assembly and a cutting assembly of the module of FIGS. 4 and 5; FIG. 14 is an exploded view of the assembly of FIGS. FIG. 15 is a detail view of a part of FIG. 13, FIGS. 16 and 17 are partial and exploded views of the module of FIGS. Fig. 18 is an exploded view of some elements of the module of Figs. 4 and 5 including a tying assembly; Figs. 19 and 20 are partial and exploded views of details of the tying assembly of Fig. 18; FIGS. 21 to 26 are perspective views of the module of FIGS. 4 and 5 at different stages of an operating cycle, FIG. 27 is a detailed view of FIG. 26, FIGS. and 31 are schematic views from one side of a portion of the module of Figures 4 and 5 at different stages of a function cycle. Figure 29 is a sectional view of a detail of Figure 28. The attached drawings include features of a certain character. They can therefore not only serve to complete the invention, but also contribute to its definition, if any. It is noted that teachings such as the shape and configuration of mechanical parts are difficult to define completely, other than by drawing. In the following, the terms forward, back, up, down, right and left are used in accordance with the intended position of an operator using the machine. In each of the figures, a three-dimensional mark is shown. The arrow referenced x represents the direction of depth oriented from front to back. The arrow referenced y 25 represents the vertical direction oriented from bottom to top. The arrow referenced z, represents the lateral direction oriented from left to right. Reference is made to Figure 1 which shows the general organization of a bunching machine. In Figure 1, the protective housings as well as the control means, timing and power of the motors were not shown.

The bunching machine has the reference 1. The machine 1 may be referred to as the stringer or baler. The machine 1 comprises a link fixing module 2, a support 6 defining at least partly a housing 7, a motor 8 and a reel 9 supporting a supply of wire 10.

An armature supports all the components of the machine 1. The frame may have other shapes and dimensions adapted. In use, a housing is arranged around the frame so as to protect the mechanical members without hindering their operation and to protect the operator using the machine. Such a protective casing can also act as a work table and complete the support 6 to support an article 3 to be tied. By article, we mean both a single object and a set of objects. The term link 5 denotes a length of wire 10 manipulated by the machine 1 to surround, tighten and tie around the article 3. In the configuration shown in Figure 1, the support 6 is fixed relative to to the frame of the machine 1. The support 6 has a generally cylindrical shape open at its ends. The support 6 surrounds a free space. The free space forms a housing 7 to accommodate the article 3 before and during the bunching. The section of the openings of the support 6 delimits the maximum dimensions of the housing 7 and the article 3 which can be tied by the machine 1. The dimensions of the support 6 allow for example to have a small flower boot or a large shrub such as a Christmas tree. The opening at both the front and rear ends of the support 6 facilitates the sliding in the direction of the depth (the x direction) of objects of great length. This facilitates the implementation of several successive tying cycles on the same item 3. For example a set of cables of several meters can be bundled by arranging and fixing several similar links spaced apart from each other. The reel 9 comprises a ring supporting a supply of wire 10. The ring is arranged around the support 6. The ring has an axis of revolution extending substantially in the x direction. The reserve of wire here takes the form of a coil mounted mad on a shaft secured to the ring. The ring is rotatably mounted around its axis of revolution and around the support 6. The reel 9 comprises driving means able to rotate the ring in a controlled manner. In the example shown in Figure 1, the drive means comprise a motor coupled to a belt, itself mounted around the ring. In the example described here, the reel 9 comprises a dedicated motor, separate from the motor 8 of the module 2. In variants, the housing 6 and the reel 9 are of dimensions chosen 5 according to the objects to be treated. In general, the smaller the section of the support 6, the smaller the ring of the reel 9 and the higher operating rates can be achieved. However, the larger the section of the support 6, the more the articles 3 that can be processed by the machine 1 are diversified. In other embodiments, the support 6 is removable and interchangeable with other supports of different shapes and sizes. The module 2 for fastening links is fixed to the frame of the machine 1. The module 2 is disposed near a front edge of the support 6. The module 2 is connected to the motor 8 via a shaft The embodiment shown here is intended to be used by an operator placing article 3 to bunch, triggering the operating cycle for example by activating a switch or pedal and then moving to new article 3. The organs of the machine 1 visible in Figure 1 may take any other suitable arrangement, in particular depending on the destination of the machine 1. For example, the machine 1 can be integrated within a chain of Automated or semi-automated manufacturing / processing / packaging. In FIG. 1, the arrow F9 indicates the direction of rotation of the reel ring 9. This anticlockwise rotation direction seen from the front of the machine 1 is adapted to the configuration of the module 2 described hereinafter. The operation of the reel 9 is simplified with respect to a machine of the type comprising a movable arm for bringing a link. A moving arm generally has a direction of advance and a direction of recoil during a tying cycle. The rotation in a single direction of the reel 9 during a cycle dispenses with the reversal of direction during the operating cycle. The operating rates can be increased and the jolts reduced. Reference is now made to FIGS. 2 and 3. FIG. 2 schematically represents the mutual organization of the link fixation module 2, the reel 9, 30 of the support 6 and an article 3 to be bunched. Article 3 here takes the form of an elongated room. Article 3 is disposed through the housing 7 and placed on a substantially flat and horizontal surface of the support 6. During the bunching sequences, the article 3 can be placed or maintained, for example by an operator. The arrow F8 represents the direction of rotation of the motor shaft 19 driven by the motor 8. Reference is now made to FIGS. 4 to 6. The motor 8 is arranged in such a way as to rotate the motor shaft 19 in the direction represented by the arrow F8. The motor shaft 19 is arranged to achieve rotational speeds of between 50 and 150 revolutions per minute. The motor shaft 19 extends vertically in the direction y. Its axis of rotation is represented by a broken line Y19. One end (top of the figures) of the motor shaft 19 is housed in the module 2 while the opposite end is connected to the motor 8. The module 2 comprises a gearbox 11 on which is fixed a table of The transmission box 11 comprises a bearing support 15, which can be seen as a skeleton of the module 2, to which the other parts are connected directly or indirectly. The gearbox 11 comprises a housing 13 mounted on the bearing support 15 to the left of the module 2. The bearing support 15 and the housing 13 protect the inside of the gearbox 11 of the external medium and vice versa. The bearing support 15 and the casing 13 together form an enclosure of the gearbox 11. In FIGS. 4 to 6, the module 2 is shown in a state at rest, that is to say between two operating cycles. . Reference is now made to FIGS. 7 and 8. In FIG. 7, the bearing support 15 and the housing 13 are not shown to reveal the inside of the transmission box 11. In FIGS. 7 and 8, some parts such as screws, nuts, seals and bearings are not shown. In the following, the similar parts bear identical reference numerals, in particular the bearings 26, the 25 pins 27, the pins 28 and the keys 29. The gearbox 11 comprises a primary shaft 23, a first secondary shaft 31, a second secondary shaft 33, a third secondary shaft 35 and a fourth secondary shaft 37. Each of the primary shaft 23 and secondary shafts 31, 33, 35 and 37 is rotatably mounted relative to the bearing support 15. In the configuration shown here, the primary shaft 23 and the secondary shafts 31, 33 and 37 extend parallel to each other and in the direction z. The third secondary shaft 35 extends vertically in the direction y. When this does not affect the clarity of the figures, the axis of rotation of each of the shafts is shown in dashed lines and referenced respectively by the reference Y19, Z23, Z31, Z33, Y35 and Z37. The primary shaft 23 is arranged to cooperate with the motor shaft 19. The cooperation of the motor shaft 19 and the primary shaft 23 is provided here by means of a gear. The motor shaft 19 supports a toothed wheel 21 and the primary shaft 23 supports a corresponding gear wheel 25 of the toothed wheel 21. The rotation of the motor shaft 19 in the direction indicated by the arrow F8 causes the rotation of the primary shaft 23 in the direction indicated by the arrow F23 by meshing of the gears 21 and 25.

Reference is now made to FIGS. 8 to 10. The primary shaft 23 is supported by a bearing formed in the bearing support 15 and provided with a bearing 26. A portion of the primary shaft 23 projects from the bearing support 15 to the casing 13. The corresponding end of the primary shaft 23 is supported by a bearing fixed inside the casing 13 and provided with a bearing 26. The primary shaft 23 carries, between the bearing support 15 on the right and the casing 13 on the left, in this order: a first member 401, a second member 403, a third member 405, a fourth member 407, a fifth member 409 and a sixth member 411. Each of the members 401 to 411 carried by the primary shaft 23 takes a general form of revolution hollowed in its center. Each of these members 401 to 411 is threaded around the primary shaft 23. The members 401 to 411 are fixed and indexed in rotation with respect to the primary shaft 23. The members 401 to 411 are fixed axially, that is, that is to say in the direction z, relative to the primary shaft 23. The members 401 and 405 to 411 are fixed and indexed in rotation relative to the primary shaft 23 by means of keys 29 and corresponding housing. The second member 403 is fixed and indexed in rotation with respect to the primary shaft 23 by means of a pin 28 arranged in corresponding housings of the first member 401 and the second member 403. The rotation of the primary shaft 23 causes the rotation of each of the members 401 to 411 and vice versa. The rotation of the primary shaft 23 and each of the members 401 to 411 is synchronous. In the ready state, the members 401 to 411 are in contact or near-contact with their immediate neighbor as shown in FIG. 7. In variants, several of the members 401 to 411 form a single piece. For example, the third member 405, the fourth member 407 and the fifth member 409 can be made in one piece.

In the embodiment presented here, the rotation on a turn exactly of the primary shaft 23 corresponds to an operating cycle of the module 2. Therefore, it is possible to deduce at least in part the operation of each of the members 401 to 411 according to their shape, like a time dial representing the course of a cycle. The first secondary shaft 31 is supported by a bearing provided with a bearing 26 formed in the bearing support 15. The first secondary shaft 31 protrudes from the bearing support 15 to the housing 13. The first secondary shaft 31 carries, between the support-bearings 15 on the right and the casing 13 on the left, in this order: a first member 421, a second member 423 and a third member 425. Each of the members 421, 423 and 425 carried by the first secondary shaft 31 takes a general form of revolution hollowed out in its center. Each of the members 421, 423 and 425 carried by the first secondary shaft 31 carries a peripheral surface forming a repeating pattern in the direction of the circumference and the tooth / hollow or male / female type. The first member 421 and the third member 425 here take the form of gear wheels. Each of the members 421, 423 and 425 is threaded around the first secondary shaft 31. The members 421, 423 and 425 are fixed and indexed in rotation with respect to the first secondary shaft 31 by means of a key 29 and corresponding housings. The rotation of the first secondary shaft 31 causes the rotation of each of the members 421, 423 and 425 and vice versa. The rotation of the first secondary shaft 31 and each of the members 421, 423 and 425 is synchronous. In the ready state, the members 421, 423 and 425 are in contact or near-contact with their immediate neighbor as shown in FIG. 7. The first member 421, respectively the second member 423, of the first secondary shaft 31 is arranged to cooperate with the first member 401, respectively the second member 403, of the primary shaft 23. The first member 401 and the second member 403 comprise two common meshing peripheral sectors. In other words, by indexing in rotation, the two peripheral meshing sectors of the first member 401 on the one hand and the second member 403 on the other hand are aligned two by two in the direction z.

The two meshing peripheral sectors correspond to two sequences of the operating cycle of the module 2 and to the operation of a retaining assembly 100 which will be detailed hereinafter. The two peripheral meshing sectors of the first member 401 are provided with shapes arranged to engage the first member 421 of the first secondary shaft 31 and here take the form of toothed sectors. The two meshing peripheral sectors of the second member 403 are provided with shapes arranged to allow rotation of the second member 423 of the first secondary shaft 31 and here take the form of recesses in the radial direction.

During each of these two cycle sequences, one of the tooth sectors of the first member 401 engages with the first member 421. The rotation of the primary shaft 23 then causes the rotation of the first secondary shaft 31 by meshing corresponding shapes. first members 401, 421. The two peripheral meshing sectors are mutually spaced by two smooth circular edges. The two smooth circular edges of the first member 401 are devoid of an intermingling shape. The two smooth circular edges of the second member 403 are not only devoid of intermeshing shape but also form two peripheral anti-rotation sectors. The peripheral surfaces of the second members 403 and 423 are mutually arranged so that during the sequences without meshing, not only the rotation of the second member 403 does not cause the rotation of the second member 423, but the rotation of the second member 423, and therefore that of the first secondary shaft 31, are prevented. To do this, the second member 423 comprises a periphery having a particular male / female type pattern. The female shapes are adjusted so that, when they are opposite a smooth circular border of the second member 403, that is to say out of the meshing sequences, the second member 403 can rotate without being impeded by the second member 423. The male shapes are shaped to come opposite the second member 403 by engaging in the recesses of the second member 403 only when the latter are vis-à-vis , that is during the meshing sequences. During the sequences without meshing, the second member 423 is held in a stable equilibrium angular position and the rotation of the first secondary shaft 31 is prevented. During the meshing sequences, the second member 423 rotates by engaging its male shapes in the recesses of the second member 403 and the rotation of the first secondary shaft 31 is permitted. This anti-rotation mechanism allows for example to stop the rotation due to the inertia of the elements. The effect of inertia is all the more important and annoying that the movements are fast. The anti-rotation effect of the second members 403 and 423 is all the more advantageous when the module 2 is used at high rates. The two non-intermingling peripheral sectors thus formed correspond to sequences of the operating cycle during which the rotation of the primary shaft 23 is rotated and the first secondary shaft 31 is stopped. The holding assembly 100 is stationary in rotation. The rotation of the primary shaft 23 in the direction indicated by the arrow F23 sequentially causes the rotation of the first secondary shaft 31 in the direction indicated by the arrow F31 by meshing of the first members 401 and 421 during two sequences of the cycle. operation. The second secondary shaft 33 is supported by two bearings provided with bearings 26 formed in the bearing support 15. The second secondary shaft 33 protrudes from the bearing support 15 towards the housing 13. The second secondary shaft 33 carries, between the bearing support 15 on the right and the casing 13 on the left, a member 431. The member 431 carried by the second secondary shaft 33 takes the form of a toothed wheel 20 hollowed at its center. The member 431 is threaded around the second secondary shaft 33. The member 431 is fixed and indexed in rotation relative to the second secondary shaft 33, here by means of a key 29 and corresponding housing. The rotation of the second secondary shaft 33 causes the rotation of the member 431 and vice versa. The rotation of the second secondary shaft 33 and the member 431 is synchronous. The member 431 is arranged to cooperate with the third member 425 of the first secondary shaft 31. The member 431 and the third member 425 each carry a peripheral surface provided with a pattern repeating throughout the circumference. The patterns here take the form of teeth arranged to mesh with each other. During operation, the rotation of the first secondary shaft 31 causes the second secondary shaft 33 to rotate by meshing the corresponding shapes of the member 431 and the third member 425.

The rotation of the first secondary shaft 31 in the direction indicated by the arrow F31 continuously drives the rotation of the second secondary shaft 33 in the direction indicated by the arrow F33 by meshing of the member 431 and the third member 425. In both sequences of the operating cycle in which the first secondary shaft 31 is rotated, the second secondary shaft 33 is also rotated. Reference is now made to FIGS. 8 to 10 and to FIG. 18. The fourth secondary shaft 37 is supported by two bearings provided with bearings 26 formed in the bearing support 15. In FIG. 9, the axis Z37 is not represented to avoid a risk of confusion with the Z23 axis. The fourth secondary shaft 37 protrudes from the bearing support 15 towards the housing 13. The fourth secondary shaft 37 carries, between the bearing support 15 on the right and the housing 13 on the left, in this order, a first member 441 and a second member 443. The first member 441 and the second member 443 carried by the fourth secondary shaft 37 each have a general form of recessed revolution in its center. The first member 441 and the second member 443 are threaded around the fourth secondary shaft 37. The first member 441 and the second member 443 are fixed and indexed in rotation relative to the fourth secondary shaft 37, each by means of a pin 27 through the first member 441, respectively the second member 443, and the fourth secondary shaft 37 in a radial direction. The rotation of the fourth secondary shaft 37 causes the rotation of the first member 441 and the second member 443 and vice versa. The rotation of the fourth secondary shaft 37, the first member 441 and the second member 443 is synchronous. The second member 443 comprises a first portion of the support-bearing side 15 and a second portion of the housing side 13 integral with one another. The first portion carries a peripheral surface bearing a repeating pattern in the circumferential and tooth / hollow direction. The pattern repeats itself around the circumference and is formed here of ten teeth. The second portion carries a peripheral surface bearing only two diametrically opposed teeth aligned with two of the ten teeth of the first portion in the z direction. The first member 441 of the fourth secondary shaft 37 is arranged to co-operate with the third member 405 of the primary shaft 23.

The first portion of the second member 443 of the fourth secondary shaft 37 is arranged to cooperate with the fourth member 407 of the primary shaft 23. The second portion of the second member 443 of the fourth secondary shaft 37 is arranged to cooperate with the fifth member 409 of the primary shaft 23.

The third member 405, the fourth member 407 and the fifth member 409 each comprise two meshing peripheral sectors. The peripheral meshing sectors of the fourth member 407 have an angular offset with those of the fifth member 409. In the example shown here, the peripheral meshing sectors of the third member 405 each comprise a radial recess. The peripheral meshing areas of the fourth member 407 each comprise four teeth while the peripheral meshing regions of the fifth member 409 each comprise a single tooth. Each of the two peripheral meshing sectors of the fourth member 407 has an angular offset with that of the fifth member 409. The two meshing peripheral sectors of the third member 405 are located in angular portions corresponding to those of the fourth member 407 and the fifth member 407. organ 409 united. In other words, by rotating indexing, the two peripheral meshing sectors of the third member 405 on the one hand and the peripheral meshing sectors of the fourth member 407 and the fifth member 409 joined on the other hand are aligned two to one another. two according to the direction z. These meshing peripheral sectors correspond to sequences of an operating cycle of the module 2 and the movements of a set of knotting 200 which will be detailed in the following. During these two cycle sequences, one of the toothed sectors of the fifth member 409 engages with the second portion of the second member 443. During these two cycle sequences, one of the toothed sectors of the fourth member 407 engages with the first portion of the second member 443. Each tooth of the fifth member 409 forms with the corresponding tooth of the second portion of the second member 443 an engagement gear for the gear formed by the teeth of the fourth member 407 and the first portion. second member 443 of the same sequence. Friction and stress on the teeth are limited and mechanical life is improved.

The two peripheral meshing sectors of each of the members 405, 407 and 409 are mutually spaced by two non-intermeshing smooth circular edges. The two smooth circular edges of the third member 405 are not only devoid of intermeshing shape but also form two peripheral anti-rotation sectors. The peripheral surfaces of the third member 405 and the first member 441 are mutually arranged so that, during sequences without meshing, not only the rotation of the third member 405 does not cause the first member 441 to rotate, but the rotation of the first member 441, and therefore that of the third secondary shaft 37, are prevented. The conjugate operation of the third member 405 and the first member 441 is similar to that of the second members 403 and 423 described above and forms an anti-rotation mechanism. The first member 441 includes a periphery having a particular male / female type pattern. The female shapes of the first member 441 are adjusted so that, when they are opposite a smooth circular edge of the third member 405, that is to say out of the meshing sequences, the third member 405 can be rotated without being impeded by the first member 441. The male shapes of the first member 441 are shaped to face the third member 405 by engaging in the recesses of the third member 405 only when the last are vis-à-vis, that is to say during the sequences of meshing. During the sequences without meshing, the first member 441 is held in a stable equilibrium angular position and the rotation of the third secondary shaft 37 is prevented. During sequences with meshing, the first member 441 rotates by engaging its male shapes in the recesses of the third member 405 and the rotation of the third secondary shaft 37 is permitted. This anti-rotation mechanism allows for example to stop the rotation due to the inertia of the elements. The effect of inertia is all the more important and annoying that the movements are fast. The anti-rotation effect of the first member 441 and the third member 405 is all the more advantageous as the module 2 is used at high rates. The non-intermeshing peripheral sectors thus formed correspond to sequences of the operating cycle during which the primary shaft 23 is rotated and the third secondary shaft 37 is stopped. The knotting assembly 200 is in a stationary position relative to the primary shaft 23.

The rotation of the primary shaft 23 in the direction indicated by the arrow F23 sequentially causes the rotation of the third secondary shaft 37 in the direction indicated by the arrow F37 by meshing of the fourth member 407, respectively of the fifth member 409, with the first portion, respectively the second portion, of the second member 443 of the fourth secondary shaft 37. The elements operating downstream of the sixth member 411 of the primary shaft 23 are shown isolated from the rest of the gearbox 11 in Figures 11 and 12. The sixth member 411 carried by the primary shaft 23 has a thickness substantially greater than that of the other members of the primary shaft 23. A groove is formed in the peripheral surface of the sixth member 411. The groove extends substantially along the circumference of the sixth member 411. The groove has a depth in the radial direction and a thickness in the z direction sensiblem constant along the circumference. In contrast, the groove is distinguished from a strictly annular groove by having a position in the sixth member 411 which varies substantially continuously in the z direction along the circumference. The variations in direction of the groove along the circumference of the sixth member 411 each correspond to sequences of the operating cycle of the module 2. The transmission box 11 further comprises a sliding arm 451. The sliding arm 451 comprises, here, two branches. The two branches extend substantially parallel to each other and extend substantially in the direction z. The two branches are arranged free in translation in the z direction in corresponding housings of the bearing support 15. The two branches are connected integrally with each other by a spacer. The spacer carries a finger 453. The finger 453 extends substantially from the spacer in the direction of the axis Z23. The finger 453 is arranged to be housed in the groove of the sixth member 411. When the sixth member 411 rotates about the axis Z23, the finger 453 follows the path formed by the groove. The sixth member 411 forms a cam while the arm 451 forms a cam follower. The cooperation between the sixth member 411 and the arm 451 makes it possible to transform the rotational movement of the primary shaft 23 into a translation movement along the z direction of the arm 451. The rotation of the primary shaft 23 in the direction indicated by the arrow F23 causes a reciprocating movement of the arm 451. The arm 451 slides in the bearing support 15 in the direction indicated by the arrows F451 and F'451. One of the branches of the arm 451 comprises an end portion 455 configured rack and provided with teeth. The end portion 455 is located opposite the finger 453, within the bearing support 15. The third secondary shaft 35 is supported by two bearings each provided with a bearing 26 disposed in the bearing support 15. The third secondary shaft 35 comprises a lower end portion housed within the bearing support 15 and extending (in the y direction) near the arm 451. The lower end portion of the third secondary shaft 35 bears on at least a portion of its circumference of the teeth corresponding to that of the rack of the arm 451. The arm 451 and the third secondary shaft 35 are arranged to cooperate within the bearing support 15. In operation, the rack of the portion of end 455 of the arm 451 meshes with the teeth carried by the third secondary shaft 35. The movement of the arm 451 comes and slides in the bearing support 15 in the direction indicated by the arrow F451, r respectively F'451, causes the rotation of the third secondary shaft 35 in the direction indicated by the arrow F35, respectively F'35. Depending on the cycle sequences defined by the shape of the groove of the sixth member 411, the third secondary shaft 35 is rotated in the F35 direction, in the opposite direction F'35 or is held stationary. The third secondary shaft 35 includes an upper end portion opposite the lower end portion. The upper end portion protrudes from the bearing support 15 and the gearbox 11, upwards. A guide arm 501 is integrally attached to the upper end portion. The guide arm 501 has a general shape reminiscent of a hook or a quarter of a ring. The guide arm 501 is fixed by one of its ends to the upper end portion of the third secondary shaft 35 so that the rotation of the third secondary shaft 35 causes a movement of the guide arm 501 in a substantially horizontal plane ( perpendicular to the direction y). The guide arm 501 is part of a guide assembly 500. The function of the guide arm 501 will be described in the following.

Although each of the members 401 to 411 carried by the primary shaft 23 has a general shape of revolution, the peripheral portions have distinct shapes depending on the circumferential position. In other words and unlike the most widespread homogeneous gear wheels, the circumferential patterns are heterogeneous along their periphery. A complete rotation, that is to say 360 °, of the primary shaft 23 corresponds to an operating cycle of the module 2. The different circumferential parts of each of the members 401 to 411 correspond to various sequences of the operating cycle . Sets 100, 200 and 500 of module 2 which will be described hereinafter have activity sequences which depend on these circumferential portions. The intermeshing or otherwise non-interfering shape of each of the members 401 to 411 makes it possible to cause, not to cause or to stop the activity of the assemblies 100, 200 and 500 located mechanically downstream. The observation of the members 401 to 411 and their arrangements relative to other parts of the module 2 makes it possible to determine, at least in part, the sequences of the cycle. The particular configuration shown in the figures is an exemplary embodiment. Other mechanical parts and other configurations are able to ensure equivalent movements or equivalent functions of the assemblies 100, 200 and 500. The gearbox 11 has an input adapted to receive the motor shaft 19 to put in rotation the primary shaft 23. The gearbox 11 receives as input the driving force of the drive shaft 19. The gearbox 11 has outputs formed of a plurality of driven shafts. In the example described here, the driven shafts correspond to the primary shaft 23, the second secondary shaft 33, the third secondary shaft 35 and the fourth secondary shaft 37. The first secondary shaft 31 does not constitute an output of the box. transmission 11 but transmits the motive power between the primary shaft 23 and the second secondary shaft 33. The gearbox 11 transmits and distributes the driving force to the outside of the assembly of the bearing support 15 and the housing 13 at the output of the gearbox 11. Each of the assemblies 100, 200 and 500 is here driven directly or indirectly by the rotation of the primary shaft 23.

Reference is now made to FIGS. 13, 14 and 15. The retaining assembly 100 is disposed between the tying assembly 200 and the bearing support 15, beneath the ejection table 17 and in the immediate vicinity of the assembly. The small distance between the retainer assembly 100 and the tying assembly 200 limits the yarn consumption. The retaining assembly 100 comprises a driving shaft 101. The driving shaft 101 forms an extension of the second secondary shaft 33 projecting from the bearing support 15 to the right, on the opposite side to the casing 13. The second secondary shaft 33 and the driving shaft 101 can be made of a single piece or be indexed in rotation by any suitable means. The driving shaft 101 is adapted to be rotated about the Z33 axis. Around the end opposite to the bearing support 15 of the driving shaft 101 is threaded a drive wheel 103 not shown in Figure 14 and shown isolated in Figure 15. The drive wheel 103 is formed here of a piece piece. The drive wheel 103 comprises a sleeve 102 of generally cylindrical shape arranged to be threaded around the driving shaft 101. The sleeve 102 of the drive wheel 103 is fixed and indexed in rotation on the driving shaft 101, here by means of a pin 27 passing through the drive wheel 103 and the driving shaft 101 in a substantially radial direction. The drive wheel 103 is adapted to be rotated by the rotation of the driving shaft 101. The drive wheel 103 receives the pin 27 in an elongated housing in the z direction. Thus, the drive wheel 103 can slide along the driving shaft 101 during operation. This configuration makes it possible to index in rotation while preserving freedom in sliding in the direction z. This forms part of the mechanism for damping the traction of the yarn described hereinafter. The sleeve is provided with peripheral lugs 105, 106 extending radially towards the outside of the sleeve 102. The lugs 105, 106 are organized in three planes of rotating lugs 103a, 103b, 103c ("plane (s) of rotation "in the continuation) perpendicular to the axis of rotation Z33 and on an end portion of the sleeve 102, on the right. From the right to the left there is a first plane of rotation 103a, a second plane of rotation 103b and a third plane of rotation 103c. The rotation planes 103a, 103b and 103c are arranged substantially perpendicular to the driving shaft 101 and are spaced apart from each other. In variants, the rotation planes 103a, 103b and 103c may be embodied by separate parts mounted on the sleeve 102 and whose periphery bears the lugs 105, 106.

The first plane of rotation 103a comprises six lugs 105, 106 in the form of curved teeth, arranged at 60 ° from each other. The lugs 105, 106 are bent in the direction of rotation of the drive wheel 103 (arrow F33) so as to facilitate the setting of the wire during rotation, in the image of a hook. In other words, each lug 105, 106 has a profile in the direction of the axis of rotation Z33 delimited by a rounded concave edge and a convex edge joining in point opposite to the sleeve 102. The rounded concave edge forms a seat to accommodate a link portion 5. Alternatively, the lugs 105, 106 may have any suitable shape forming a seat for a link portion 5. The lugs 105, 106 are here of a first type 105 ("ergot (s) 105 "in the following) or a second type 106 (" pins 106 "in the following). In the example described here, three lugs 105 mutually disposed at 120 ° from each other are similar to each other, while the other three lugs 106 similar to each other are longer, less curved and extend radially further than the lugs. 105. The lugs 105, respectively 106, of the second plane of rotation 103b are of identical shape to the lugs 105, respectively 106, of the first plane of rotation 103a. The lugs 106 of the third plane of rotation 103c are arranged at 120 ° from each other. The lugs 106 of the third plane of rotation 103c are similar to those of the first and second planes of rotation 103a and 103b. Each lug 106 of the third plane of rotation 103c is aligned with a lug 106 of the second plane of rotation 103b and a lug 106 of the first plane of rotation 103a.

The third plane of rotation 103c is devoid of lug 105. The lugs 105 have the function of maintaining and moving and releasing one of the portions of the link 5. The lugs 106 have the function of hanging, moving and pushing another portion from the same link 5 to split it. In the example described here, the radial distance separating the axis of rotation Z33 from the seat of the lugs 105 is smaller than the radial distance separating the axis of rotation Z33 from the seat of the lugs 106. Thus, the cooperation of the lugs 106 with the lug cutting assembly 300 is improved. The ability of the pins 105 to catch a portion of wire to pinch it into the retainer assembly 100 is improved. These operations and the distinct functions of the lugs 105 and 106 will be described in more detail below, in particular with reference to FIGS. 28 to 31. The retaining assembly 100 further comprises two fixed rotating plates 111a and 111b and a plate 111c. . The plate 111c is fixed to the bearing support 15, on the right side. The plates 111a and 111b and the plate 111c are arranged in planes substantially perpendicular to the direction z, parallel to each other and parallel to the rotational planes 103a, 103b and 103c. The plates 111a and 111b and the plate 111c each have a generally rectangular shape having a cutout having substantially the shape of a semicircle centered on the axis Z33 and having a diameter greater than the outer diameter of the driving shaft 101. Each cutouts continue with an entrance edge and an exit edge that flare out from this cut. The plates 111a and 111b and the plate 111c are arranged alternately with the planes of rotation 103a, 103b and 103c, as appears in FIG. 13. Thus, successively, from the right to the left of the module 2: the plate 111a, the first plane of rotation 103a, the plate 111b, the second plane of rotation 103b, a free space, the third plane of rotation 103c, a cutting assembly 300 fixed to the plate 111c, the plate 111c fixed against the bearing support 15 Figures 28 to 31 show the configuration of the retainer 100 at different stages of its operation. The plate 111c and the plates 111a and 111b each comprise two through openings. The through openings are aligned in the z direction between the plates 111a and 111b and the plate 111c. The plate 111c and the plates 111a and 111b are mounted threaded around two arms 113a, 113b by said openings. The two arms 113a, 113b are mounted integral with the plates 111a and 111b and extend in the z direction. The opposite end portion (left) of each of the two arms 113a and 113b are slidably mounted in the bearing support 15, for example by means of ball bushings housed in the support-bearing 15. The plates 111a and 11 lbs are thus locked in rotation relative to the bearing support 15 but movable in translation in the z direction.

In variants, the gap between the plates 111a and 111b can be fixed, for example by interposing wedges or spacers fixed and permanent. On the contrary, in the example shown here, the interspace between the plates 111a and 111b may vary during operation. Wedges, here taking the form of washers 115, are threaded around the arms 113a and 113b between the plates 111a and 111b. The thickness of the washers 115 in the z direction determines the minimum distance between the plates 111a and 111b. The washers 115 then form stops for the second plate 111b. The second plate 111b can undergo a slight translation to the plate lllc, to the left. This movement is limited by springs 117 working in compression between the second plate 111b and the plate lllc. In operation and as shown in Figure 29, the tightening of the wire, by clamping between the plates 111a and 111b and the lugs 105, 106 of the plane of rotation 103a and 103b, is dependent on the gap between the plates 111a and 111b. The freedom of translation of the second plate 111b with respect to the first plate 111a gives the retaining assembly 100 a capacity to adapt to variations in thickness of the wire during operation. The retaining assembly 100 is thus provided with a mechanism for fine adaptation of the necking of the wire. This fine mechanism compensates for irregularities of the wire. By replacing the washers 115 with other washers of different thickness, it is also possible to adjust the minimum distance between the plates 111a and 111b. It is thus possible to adapt the retaining assembly 100 to son of very varied thicknesses and flexibilities. The retaining assembly 100 may for example be adapted for the passage of a wire of less than one millimeter in diameter or a wire of more than one millimeter. The retaining assembly 100 is thus provided with a coarse adaptation mechanism of the necking of the wire.

The fine adaptation mechanism and the coarse adaptation mechanism are optional and can be implemented independently of one another. Nevertheless, the combination of these two mechanisms provides a complementary effect: an operator can manually adjust the clamping of the wire with the interchangeable shims 115, and then the fine mechanism automatically adjusts the clamping more finely during operation.

In addition, the retainer 100 allows sliding during z-direction operation of a group of sliding parts relative to a group of stationary parts. The group of sliding parts comprises the arms 113a and 113b, the plates 111a and 111b and the drive wheel 103. The group of fixed parts 5 comprises the plate 111c and the support-bearings 15. The plates 111a and 111b and the wheel With the drive 103 sliding together, the clamping of the wire is substantially independent of the sliding. The sliding is limited by abutment means and elastic return means. The elastic return means comprise, here, a helical spring 119 working so as to urge a closer approximation of the sliding group parts 10 and parts of the fixed group. In operation, sliding during an operating cycle gives flexibility to the retaining assembly 100 of module 2: it can be "given slack" during knotting, which avoids breaking the thread, in particular during fast operations and / or when the wire used has zero or negligible elasticity. During operation, the yarn can undergo sudden pulls. Sliding can limit the stresses collected by the wire and dampen sudden movements. The retaining assembly 100 is thus provided with a mechanism for damping the traction of the wire. In the example described here, the traction of the wire, especially during the knotting, pulls on the group of sliding parts which generates the sliding. In a variant, the sliding is forced during the cycle by mechanical means provided for this purpose. This variant is particularly advantageous to avoid the sudden pulling of the wire when the latter is fragile. In a variant that can be combined with the preceding one, the stiffness of the damping is manually adjustable according to the type and the thickness of the wire used for bundling, for example by means of a nut to be moved to modify the spring stroke. . The damping mechanism is optional and independent of the pinch adjustment mechanisms. In the embodiment presented here and combining the three mechanisms, the first plate 111a is damped in the direction of the plate 111c by the work of the spring 119 while the second plate 111b is urged towards the first plate 111a by the work of the springs 117.

Of course, each of the three mechanisms described above can take different configurations while remaining functionally similar to those presented here. The embodiment of the retainer assembly 100 shown here is adapted to cooperate with the rest of the module 2 and the machine 1 described so far. The retainer 100 may nevertheless be adapted to cooperate with other modules and other tying machines. The cutting assembly 300 visible in Figures 13 and 14, here takes the form of a knife attached to the plate 111c. The knife has a beveled blade capable of severing a wire. The knife is disposed between the plate 111c and the third plane of rotation 103c of the drive wheel 103. The knife is oriented so as to cooperate with a pin 106 of the third plane of rotation 103c acting against blade, like that will be described later. During an operating cycle, the second secondary shaft 33 is rotated sequentially by meshing with the first member 401, which gives the drive wheel 103 a sequential rotation. The drive wheel 103 is rotated twice 60 °, as shown in FIGS. 28, 30 and 31. The identity of the lugs (105, 106) gives the drive wheel 103 three sectors. identical angles in a central symmetry with a pitch of 120 °. Although rotated 120 °, the drive wheel 103 has a similar configuration at the beginning and end of the cycle. The knotting assembly 200 is shown in its immediate environment in FIGS. 16 and 17, and connected to the elements that allow it to move in FIG. 18. The knotting assembly 200 comprises a tilting support 201, a spout support 202 , a crank 203, a connecting rod 205, a spout 207 and a spur stop 209. The tilting support 201 has a generally hollow cup shape at its center. The tilting support 201 is threaded around the primary shaft 23. The primary shaft 23 supports the tilting support 201 via a bearing 26 housed in the recess of the tilting support 201. The tilting support 201 can thus be The rotation of the primary shaft 23 and the tilting of the tilting support 201 around the axis Z23 are asynchronous.

The fourth secondary shaft 37 protrudes from the gearbox 11 from the bearing support 15 away from the housing 13 to the tying assembly 200. In an end portion, on the side of the tying assembly 200, the fourth secondary shaft 37 supports the crank 203. The crank 203 takes the form of a disc in which is formed a through opening, along its axis of revolution. The crank 203 is fixed and indexed in rotation to the fourth secondary shaft 37, here by means of a key 29 and corresponding housings in the fourth secondary shaft 37 and the crank 203. A first end of the connecting rod 205 is fixed to a part the crank 203 eccentric with respect to the Z37 axis. A second end of the rod 205, opposite the first, is fixed to a portion of the tilting support 201 eccentric with respect to the axis Z23. The ends of the rod 205 are fixed to the crank 203, respectively to the rocking support 201, freely rotated about an axis oriented in the direction z. The rotation of the fourth secondary shaft 37 about the axis Z37, causes the rotation of the crank 203, which causes the movement of the rod 205 in a plane substantially perpendicular to the direction z. The displacement of the connecting rod 205 in turn causes the partial rotation, tilting, of the tilting support 201 with respect to the axis Z23. During an operating cycle, the fourth secondary shaft 37 is rotated by a half-turn on itself during a first sequence by meshing with the first peripheral meshing sector of the fourth member 407, which which gives the tilting support 201 a tilting movement about the axis Z23 in the opposite direction to that indicated by the arrow F23. In a subsequent sequence of the same operating cycle, the fourth secondary shaft 37 is rotated an additional half-turn on itself by meshing with the second meshing peripheral sector of the fourth member 407, which gives the tilting support 201 a tilting movement about the Z23 axis in the opposite direction to that of the first sequence (this time in the direction of F23) and the same angle. The tilting support 201 supports in the upper part the spout support 202. The spout support 202 houses the spout 207. The rotations of the tilting support 201 drive the spout support 202 successively between a so-called rest or withdrawal position and a so-called work position. The tying assembly 200 further comprises a drive plate 211. The drive tray 211, hollowed out at its center, is threaded around the primary shaft 23. The drive plate 211 is fixed and indexed in turn. rotation to the primary shaft 23, here by means of a key 29 and corresponding housings in the primary shaft 23 and the drive plate 211. The tilting support 201 surrounds the drive plate 211 by its cup shape on the right side of the module 2. The drive plate 211 carries a toothed sector 213 extending over a limited angular interval (for example of the order of 55 °). The upper part of the spout support 202 carries a cam 223 formed as a non-circular outer cylindrical surface. The spout support 202 carries, in the upper part, the spout 207 rotatably mounted about an axis Y207 perpendicular to the axis Z23. In the working position of the tying assembly, the Y207 axis is substantially oriented in the vertical y direction. The spout 207 is wedged at the upper end of a shaft whose lower end carries a toothed pinion 217 adapted to mesh with the toothed sector 213. The spout 207 carries a tongue 219 hinged about an axis Z219 oriented in a substantially horizontal direction. The tongue 219 carries a wheel 221 adapted to cooperate with the cam track 223. When the toothed sector 213 meshes with the pinion 217, the spout 207 is rotated about the axis Y207 and the tongue 219 can be brought together or away from the bill to form a clip for holding one or more strands of wire for the formation of a node. Thus, the spout 207 can be rotated on itself (along the axis Y207), in combination with a tilting movement about the axis Z23 while the tongue 219, or against-beak , articulates around a pivot defining the Z219 axis according to the angular position of the spout 207 relative to the spout support 202 (around Y207). The shim 209 attached to the spout support 202 acts as a mechanical return to press the spool 221 against the cam track 223. The wedge 209 is not shown in FIG.

Referring now to Figures 16 and 17. In the example shown here, the guide assembly 500 comprises the guide arm 501 whose operation has been described above, a guide pin 503, a stripper finger 505, an arm lower guide 507 and a retaining finger 509.

The guide pin 503 is attached to the bearing support 15 via a support 504 and fastening systems such as screws. The free end of the guide pin 503, against which the link 5 is supported during operation, is disposed near the spout 207 in the working position, on the right side, opposite the bearing support 15. The finger 503 guide remains stationary during a cycle of operation.

The stripping finger 505 is attached to the tilting support 201 of the knotting assembly 200. The free end of the stripping finger 505 intended to come into contact with the link 5 during operation is disposed near the spout 207. The free end the stripper finger 505 is interposed between the spout 207 and the guide finger 503 when the knotting assembly 200 is moved to its working position. The stripping finger 505 is moved simultaneously to the tilting of the tilting support 201. The lower guide arm 507 is attached to the support 504 by a freely rotatable connection along an axis of rotation Z507 parallel to the direction z. The lower guide arm 507 is connected to the tilting support 201 via a connecting rod 508. The support 504, the guide arm 507, the connecting rod 508 and the tilting support 201 are mutually arranged so that, simultaneously the rotation of the tilting support 201 about the axis Z23 to bring the spout 207 into the working position, the portion of the lower guide arm 507 intended to come into contact with the link 5 goes from a low withdrawal position to a position The retaining finger 509 here is formed of a protuberance of the plate 111c of the retaining assembly 100. The protrusion takes a rounded shape and extends from the plate 111c towards the front of the module 2 substantially in the direction x. The retaining finger 509 remains stationary during an operating cycle. The operation of the link fixing module 2 is now described with reference to FIGS. 21 to 26 showing respectively a state 0, a, b, c, d and e of the module 2 during one operating cycle and making references to Figures 28, 30 and 31 respectively representing the states b / c, d and e of the retaining assembly 100.

The rest position 0 of the link fixing module 2 corresponds to the position of the module 2 between two operating cycles. The relative positions of the various elements of the module 2 substantially correspond to those shown in the previously described figures.

In the starting phase of the operating cycle, in position 0, the link 5 has a first end A wedged in the retaining assembly 100. The link 5 extends to the reel 9 shown schematically. FIG. 29 represents, in section, the first end A wedged and held in the retaining assembly 100. In the figures, reference numeral 900 indicates the position of the end of an arm of the reel 9 as represented in FIG. 1. The first end A of the link 5 extends under the retaining assembly 100, around the retaining finger 509 and between the plates 111a and 111b and lugs 105, 106 rotation planes 103a, 103b which hold it tight. The link 5 is held taut between the retaining assembly 100 and the end 900 of the reel 9.

The guide arm 501 is in the retracted position, i.e. retracted towards the rear of the module 2 and recessed with respect to the front edge of the ejection table 17. The tying assembly 200 and the 505 stripper finger are also recessed, that is to say in the rest position, tilted backwards. In the state, the retaining finger 509 and the guide pin 503 protrude from the front edge of the ejection table 17 relative to a reeling plane substantially perpendicular to the direction x. Before triggering the reel 9, an article 3 to bunch is disposed above the module 2, here on the ejection table 17. In Figures 22 to 26, the article 3 is shown disposed in a position to the left of the ejection table 17 to facilitate viewing of the organs located under the ejection table 17. The placement of Article 3 in this location is possible. However, it is generally preferable to have it as close to the spout 207 in the working position. This makes it possible to make links 5 which are tighter and whose yarn consumption is reduced. The rotation of the ring and the arm of the reel 9 along the axis of revolution makes it possible to unwind the link 5 from the end 900 of the reel feeder arm 9. The path of the end 900 of the feeder arm of the reel 9 corresponds substantially to a circle in the unwinding plane (perpendicular to the x direction), centered on the axis of revolution of the ring of the reel 9 and in the direction indicated by the arrows F9. Reference is now made to Figure 22 showing the position a. The position a of the module 2 corresponds to the position 0 after the end 900 of the arm of the reel 9 has made a complete rotation. Figures 28 and 29 show the rotation assembly 100 in step a. When rotating on a turn of the reel 9, the wire is unrolled, in this order, around the guide pin 503, the article 3 and the retaining finger 509. The first end A of the link 5 remains locked in the retaining assembly 100. The second end of the link 5 near the end 900 of the feed arm of the reel 9 is referenced B. The second end B remains connected to the supply of wire 10 of the reel 9. The reel 9 is arranged to generate a traction force on the link 5 so that it is tensioned during operation. The applied traction force prevents portions of the link 5 from being displaced by the effect of gravity and / or air flow. The pulling force of the reel 9 is adapted, in particular according to the type of wire used. Although advantageous, this return force of the reel 9 is optional, especially when the wire used has a high elasticity. The portion of the link 5 extending between the article 3 and the retaining finger 509 is referenced I. The link portion 5 surrounding the guide pin 503 is referenced II. During the operation of the reel 9, between step 0 and step a, the module 2 remains inert and the relative positions of the elements of the module 2 remain unchanged. In the position a, a loop is formed around the article 3. The actuation of the link fixing module 2 will make it possible to fix the loop around the article 3 and to separate it from the rest of the wire from the side of the reel 9 In the following steps, the reel 9 remains substantially stationary but keeps the link 5 taut. Reference is now made to Fig. 23 showing the position b. Between the position a and the position b, the portion I of the link 5 is moved to the right of the module 2, that is to say substantially in the z direction. To do this, the guide arm 501 is rotated relative to the axis Z35 and in the direction indicated by the arrow F35. The free end 30 of the guide arm 501 pushes the portion I of the link 5 to a substantially vertical position and to the right of the spout 207 (left in Figure 23). The portion of the link 5 now extending between the portion I and the retaining finger 509 is referenced III. During the passage from the position a to the position b, the tilting support 201 of the tying assembly 200 tilts forwards about the axis Z23 so as to move the spout 207 to its working position. In this working position, the spout 207 comes close to and to the left of the portion I of the link 5. The guide arm 501 and the spout 207 are mutually arranged so that their respective movements are not impeded. In the example described and shown in FIG. 23, the spout 207 at the end of the tilting stroke passes partly through a corresponding cut at the end of the guide arm 501. On the other hand, the sequences are organized from so that the guide arm 501 pushes the portion I of the link 5 to the right of the spout 207 before the spout 207 reaches its working position. Tilting the tilting support 201 of the retaining assembly 200 also causes the stripper pin 505 to tilt toward a substantially vertical position. During this tilting, the stripping finger 505 pushes the portion II of the link 5 surrounding the guide pin 503 towards the rear of the module 2. The loop of the link 5 being stretched, the release of the link portion II 5 since the guide finger 503 by the movement of the stripping finger 505 causes the tightening of the loop. The portion II of the link 5 is tightened and bears against the spout 207 as can be seen in FIG. 23. Simultaneously with the tilting support 201 swinging from the tying assembly 200, the lower guide arm 507 undergoes a movement. The lower guide arm 507 and its movement are used to better guide the portion II released from the guide pin 503 to bear against the spout 207 in the working position. The arrangement and arrangement of the stripper finger sequences 505, the lower guide arm 507 and the tilt support 201 are mutually adapted so that the portion II is released from the guide finger 503 only after the spout 207 has reached its working position and can receive link portion II 5. Reference is now made to FIG. 24 representing position c. When passing from position b to position c, the guide arm 501 is returned to its retracted position by a rotation in the direction indicated by the arrow F'35 along its axis of rotation Z35. During this movement, the portion I of the link 5 is deposited against the right part of the spout 207, next to, in contact with or superimposed on the portion II of the link 5.

Reference is now made to Fig. 30 showing position d and Fig. 25 showing an intermediate position between positions d and e. After the deposition of the portion I of the link 5 against the spout 207 by the removal of the guide arm 501, the retaining assembly 100 is activated. Between the position c and the position d, the drive wheel 103 of the retaining assembly 100 is rotated about its axis Z33 in the direction indicated by the arrow F33 of FIGS. 24 and 28. Thus, a pair of lugs 105, one of which belongs to the first plan of rotation 103a and the other to the second plane of rotation 103b, drives the end portion A of the link 5 while keeping it wedged between the lugs 105 of the rotation planes 103a and 103b and the plates 111a and 111b.

Simultaneously, the three lugs 106 located at 60 ° behind and below the two first lugs 105 catch the III portion of the link 5. The advanced lugs 106 catching the III portion of the link 5 causes this portion III upwards. In step d, the portion III is not yet wedged between the plates 111a and 111b and the pins of the rotational planes 103a and 103b and is not yet maintained tight. The rotation of the drive wheel 103 is here about 60 °. The displacement of the portion A and the portion III of the link 5 places the latter substantially in a horizontal plane. This arrangement of the portions A and III of the link 5 facilitates the knotting operation by the spout 207 as described below. When the two portions A and III of the link 5 are arranged substantially horizontally, the position d is reached. The spout 207 is then rotated to perform the knotting. The spout 207 is rotated along its own axis Z207 in the direction indicated by the arrow F207 of Figure 25. In Figure 25, the spout 207 is being rotated. A rotation of about 270 ° has already been made. The rotation of the spout 207 on itself causes the winding portions I and II of the link 5 and the formation of a double loop. During its rotation and before crossing the portions A and III of the link 5, the clamp formed by the spout 207 and the tongue 219 opens. Following the rotation of the spout 207 passes the spout 207 over the portion A and the portion III of the link 5 and below the portions of the link 5 stretched between the spout 207 and the article 3, while the tab 219, or counter-clamp, in the open position passes under the portions A and III of the link 5.

When turning, the spout 207 pulls the link 5. The faster the rotation, the more the pull is brutal. The operation of the wire pull damping mechanism of the retainer assembly 100 is particularly advantageous during this sequence. At the end of rotation of the spout 207, the tongue 219 is closed by trapping the portions A and III of the link 5 against the spout 207. Almost simultaneously with the closing of the spout 207 and the tongue 219, the drive wheel 103 of the 100 retaining assembly is again rotated according to its own axis of rotation Z33 in the direction indicated by the arrow F33. The drive wheel 103 then rotates again about 60 °. This second rotation fulfills two distinct functions: the end portion A of the link 5, previously cut at the end of the cycle preceding the step 0, is released from the retaining assembly 100, and the portion III of the link 5 is driven by the lugs 106 against the cutting assembly 300 and in particular against the sharp edge of the knife so as to cut the portion III of the portion B still connected to the reel 9. Slightly before the section of the link 5 by the assembly 300, the portion of wire still connected to the reel 9 and passing under the retaining finger 509, referenced IV in Figure 25, is driven between the plates 111a and 111b and wedged tight between the lugs 105 of the rotation planes 103a and 103b and plates 111a and 111b. The portion IV is then held by the retaining assembly 100. The portion IV become an end still connected to the reel 9 of the present cycle is then ready for a next cycle in which the portion IV will become the end portion A. Referring now to Figs. 26, 27 and 3, there is shown the position e, after cutting the yarn and blocking portion IV for the next cycle. In Fig. 27, only spout 207, article 3 and link 5 are shown. The different portions of the link 5 and their provisions are shown apart from each other in an exaggerated manner to facilitate the visualization of the path taken by the link 5. In practice, the different strands of the link 5 are difficult to identify visually. After the position e shown in FIGS. 26 and 27, the various elements of the module 2 are returned to a final position f identical to their initial position 0. In particular, the tilting support 201 of the tying assembly 200 undergoes a tilting around the Z23 axis in a direction opposite to that indicated by the arrow F201 of Figure 22. This tilting movement back of the spout 207 finalizes the knotting. The two portions A and III of the link 5, become the free end portions of the link 5, are drawn by the spout 207 through the double loop formed by the link 5 around the spout 207. The knot is knotted. By the reaction force exerted by the article 3 on the link 5, and possibly the elastic effect of the link 5, the double loop around the spout 207 slides around and escapes the spout 207. In the embodiment presented here , the free ends of the portions A and III of the link 5 do not cross the double loop and remain on the front side of the double loop. In other words, two loops are formed with each of the portions A and III of the link 5. A knitted node is obtained. By pulling on both free ends, the knot can be undone because the loops are flowing. The link 5 formed around article 3 can thus be loosened more easily. This characteristic is advantageous but nevertheless optional. Alternatively, the portions A and III and the corresponding free ends 15 are pulled entirely through the double loop by the spout 207. The knot obtained is then un-wired. When the tilting support 201 tilts backwards, the stripper finger 505 and the guide arm 507 are also tilted back to their retracted initial position, corresponding to the position 0. The module 2 for attaching link is then ready to begin a new cycle, similar to that described so far. Before starting a new cycle, Article 3 may be moved longitudinally (in the fore-and-aft direction x) to form a link 5 at another location in Article 3. Article 3 may also be held in position to form a second link 5 substantially in the same place as the first. The article 3 can be further extracted from the housing 7 of the machine 1 in order to make room for a new article 3. This provides a link 5 fixed by a tightly knotted node around the article 3 and in which the free ends have a very short length. The production of wire waste or drop of link is reduced. The gearbox 11 includes the members for distributing the motive power from the upstream drive shaft 19 to the driven shafts 23, 31, 33, 35 and 37 downstream. These different moving parts generally have better durability when they are coated with a lubricating substance or bathe in a lubricating bath such as grease or oil. In the embodiment described above, the space defined in the chamber formed by the bearing support 15 and the housing 13 can be substantially hermetically isolated from the external environment. An elastomeric seal may for example be inserted between the bearing support 15 and the casing 13 in order to improve the seal. The lubricating substances are confined inside the bearing support 15 and the casing 13. In addition, this fluidic isolation makes it possible to limit the pollution of the gearbox 11 by debris, dust and foreign elements coming from the outside. Only the drive shaft 19 and the driven shafts 23, 33, 35 and 37 pass through the casing formed by the bearing support 15 and the casing 13. Now, these shafts being mobile only in rotation around their respective axes , the fluidic insulation of the gearbox 11 is ensured. Elastomeric seals or rings are arranged around said shafts 19, 23, 33, 35 and 37 at the inputs / outputs of the gearbox 11 to further improve the seal. Similarly, the tilting support 201 and the spout support 202 may be arranged so that the interior space, including housing the pinion 217 and the serrated section 213, is substantially sealingly insulated from the external environment.

The gear can also be lubricated without the lubricating substances being likely to contaminate the outside or to be polluted by the external environment. Lubricant inputs / outputs are provided for the gearbox 11 and for the tilting support 201 and the spout support 202. These inputs / outputs are here equipped with nozzles facilitating the connection of one or more lubricant reserves.

Such nozzles are referenced 600 in the figures. In a variant, the module 2 does not include a lubricant inlet / outlet. In this case, disassembly can renew the lubricant. This renewal is nevertheless rarefied by the sealing. Unlike the transmission box 11 and the tilting support assembly 201 and nozzle support 202, the parts of the module 2 in contact with or in the immediate vicinity of the link 5 and the article 3 operate without the use of lubricant is needed. Therefore, during operation of the machine 1 provided with the module 2, the articles 3 and the link 5 are protected from dirt or contaminations by the lubricant. This advantage is particularly interesting in the field of meat production and generally the production and bunching of products with high health constraints.

In addition, the cleaning of the module 2 is made easier and faster than for existing devices. The number and complexity of the parts of the module 2 in contact with or in the immediate vicinity of the articles 3 are reduced. Maintenance and maintenance of such modules or machines equipped with such modules is reduced and availability is improved.

Apart from the operation of the reel 9, the module 2 is supplied with motive power by a single drive shaft 19. In the embodiment presented here, the sequences of the operating cycle are entirely defined by mechanical parts. Module 2 has a high compactness (a small footprint). The amounts of movement of the different parts compared to existing devices are reduced. The magnitude of the movements of the different parts is limited compared to known devices. Thus, the energies involved are reduced and the wear constraints reduced. This in particular makes it possible to reduce the duration of each sequence of the operating cycle while increasing the service life of the installations. The reel 9 can here achieve operating rates with rewinding cycle times less than 0.5 seconds. The embodiment described above makes it possible, for example, to obtain operating rates with cycle times of module 2 alone (unwinding cycle not included) less than 0.7 seconds and even less than 0.5 second. . As a result, the total operating cycle has a reduced duration. The embodiment described above makes it possible, for example, to obtain operating rates of the machine 1 with cycle times of less than 1.1 seconds and even less than 0.9 seconds. In other words, 54 and even more than 66 links can be made per minute. The module according to the invention can be used to bunch objects of very different natures with elastic or non-elastic links that can have various thicknesses and characteristics.

In the example described so far, the total bundling cycle comprises a rewinding sequence involving the reel 9 followed by a series of link fixation sequences with formation of a node involving the module 2. In variants, two or more rewind sequences may be implemented further before activating module 2 to secure the multi-loop link. Thus, articles 3 can be bundled by means of one (or more) link 5 formed of several turns of wire, several turns of wire being fixed by a single node. In this case, the machine 1 is of similar configuration to that described above but the unwinding cycle is repeated successively as many times as desired loops. A new strand of wire is superimposed on the preceding one with each rotation of the reel 9. Next, the fixation cycle is similar to that described above, except that each portion of the link 5 comprises a number of equal strands. The invention also relates to a mounting kit comprising parts adapted to be assembled and forming a link fixing module for a bunching machine. The attachment module of the link in the state of spare parts can thus be transported more easily. Of course, the invention is not limited to the embodiment described above by way of example. Thus, it is possible to design a link fixing module and / or a machine adapted to operate within a largely automated assembly / manufacturing / packaging line. The invention is not limited to the embodiments described above, only by way of example, but encompasses all variants that may be considered by those skilled in the art within the scope of the claims below.

Claims (13)

REVENDICATIONS1. Linkage attachment module (2) (5) for a bunching machine (1) comprising: - a tie retainer assembly (100) (5), and - a linkage tie assembly (5) (5), characterized in that it further comprises - a gearbox (11) having an input adapted to receive a drive shaft (19) and outputs formed of a plurality of driven shafts (23, 31, 33, 35, 37), the gearbox (11) being configured to sequentially rotate each of the driven shafts (23, 31, 33, 35, 37) by rotation of the drive shaft (19). the retaining assembly (100) and the tying assembly (200) comprising elements configured to be animated by the rotation of one of the driven shafts (23, 31, 33, 35). , 37). The module (2) of claim 1, further comprising a link guide assembly (500) (5), the guide assembly (500) comprising elements configured to be animated under the effect of the rotation of one of the driven shafts (23, 31, 33, 35, 37). 3. Module (2) according to one of claims 1 and 2, comprising an enclosure (13; 15) arranged to be traversed by the drive shaft (19) and the driven shafts (23, 31, 33, 35). , 37), said enclosure (13; 15) being configured so that the inside and the outside of the transmission box (11) are isolated from each other in a substantially watertight manner during operation. 4. Module (2) according to one of the preceding claims, wherein the knotting assembly (200) comprises an interior space accommodating transmission means (213; 217) of driving force, said interior space and the outside of the knotting assembly (200) being insulated from each other substantially sealingly. 5. Module (2) according to one of the preceding claims, wherein the gearbox (11) is configured so that the sequential rotation of the driven shafts (23, 31, 33, 35, 37) defines a cycle the elements of the retainer assembly (100) and the knot assembly (200) having similar positions at the beginning and at the end of the operating cycle. 6. Module (2) according to claim 5, having an operating cycle at the end of which a portion of wire is held by the retaining assembly (100). 7. Module (2) according to one of claims 5 and 6, having a configuration in which the gearbox (11) is adapted to receive a motor shaft (19) whose rotational speed gives the operating cycle a duration less than 0.7 seconds. 8. Module (2) according to one of the preceding claims, wherein the gearbox (11) houses at least one anti-rotation mechanism (403; 423) arranged to sequentially prevent the rotation of one of the driven shafts (31). ). 9. Mounting kit comprising a set of parts capable of being assembled to form a module (2) according to one of the preceding claims. 10. Bunching machine (1) provided with a housing (7) arranged to receive an article (3) to bale and a wire reel (9) arranged to unwind the wire around the article (3) and forming a link (5), the machine (1) being equipped with a module (2) according to one of the preceding claims for fixing the link (5) and a motor shaft (19) received in the module (2). ). 11. Machine according to claim 10 arranged to present a thread unwinding cycle around the article (3) with a duration less than 0.5 seconds. 12. Machine according to one of claims 10 and 11, wherein the wire reel (9) is arranged to unwind the wire around the article (3) on at least two turns before the module (2) is activated. 13. Machine according to one of claims 10 to 12, configured to successively rotate the reel (9) and the motor shaft (19).