EP1927692A1 - Tilting punching device and method - Google Patents

Abstract

The needle punching apparatus for making non-woven materials from a fiber lap, comprises a frame, a unit for guiding a product e.g. fiber lap according to a forward longitudinal direction in a plane and a width of the product, a support (42) intended to carry a needle plate (1), actuating and guiding unit to activate the support so that the needles carry out a successive striking movement in the product with a main component, which is transverse to the plane, and a unit for defining an inclination of the main component. The needle punching apparatus for making non-woven materials from a fiber lap, comprises a frame, a unit for guiding a product e.g. fiber lap according to a forward longitudinal direction in a plane and a width of the product, a support (42) intended to carry a needle plate (1), actuating and guiding unit to activate the support so that the needles carry out a successive striking movement in the product with a main component, which is transverse to the plane, a unit for defining an inclination of the main component around an axis significantly parallel to the width of the product with respect to a normal level, and a unit for adjusting the inclination of the main component. The striking movement is a movement in closed loop defining the main component combined with a secondary component substantially parallel to the longitudinal direction of the product, and a substantially straight movement. The actuating and guiding unit comprises a unit for guiding a positioning pivot (49) linked to support according to a predetermined path. The inclination defining unit allows to define an orientation of the predetermined path, which is straight. The unit for guiding the positioning pivot comprises a slide, and a deformable quadrilateral having an intermediary rod connected to the support by an articulation in the positioning pivot and two guiding rods articulated each of a part with a respective end of the intermediary rod and other part with the frame along an anchor axis. The deformable quadrilateral is constituted by Watt's and Tchebycheff's mechanisms. The inclination of the main component is adjusted by the orientation of predetermined path. The anchoring axis is moved with respect to the frame to adjust the inclination of predetermined path and the orientation of the main component. The anchoring axis moving unit defines a path for the anchoring axis into an arc form of a circle centered on an axis parallel to the width of the product. The anchoring pivot displacement path is substantially in an arc form, which is centered on the axis of positioning pivot when the needle tips are at middle in the product. The anchoring axis moving unit comprises a guiding slide, and a unit for blocking a position of anchoring axis in the slide. The unit for guiding the positioning pivot is mounted on a turning plate around an axis parallel to the width of the product. The actuating unit comprises two actuating rods of which one part is connected with a respective crankshaft and other to the support of needle board by the actuating axis, where the two crankshafts turn in opposite direction from each other. A mutual angular setting of both crankshafts is adjustable. An outlet shaft is connected to the first crankshaft, and an inlet shaft is connected to an outlet shaft of motor. An angular adjustable element is intended to adjust a phase difference of the first crankshaft with respect to the second crankshaft. An independent claim is included for a needle punching process.

Description

Technical area

The present invention relates to a device for needling a product such as a sheet of fibers. It also relates to a method implemented in this device.

The field of the invention is more particularly that of needling machines for manufacturing nonwoven materials from fiber webs.

State of the art

A web of fibers is typically composed of layers of parallel fibers superimposed so that the direction of the fibers is different from one layer to each adjacent layer. The tablecloth is fragile because the fibers are not linked together.

To consolidate a web, it can be passed in a needling device called needling. The sheet propagates inside the needling machine in a direction of longitudinal advance along a needling path defined between two generally horizontal plates, called respectively stripping plate (or stripper) generally placed in the upper position, and needling plate (or needling table) generally placed in the lower position. The needling machine further comprises on the side of the stripper a needle board carrying thousands of needles oriented vertically towards the needling table. The board is operated in a vertical back and forth movement through the needling path. The stripper and the needling plate have holes for passing the needles. In this way, the needles can penetrate the web and withdraw from the web many times as a given point of the web passes the needling path. At each penetration of needles into the web, barbs present on the needles cause and interlace fibers of the web. The sheet thus compacted and consolidated leaves the needling machine with good mechanical strength.

Such a needling device, however, has some defects. For example, each time the needles are engaged vertically in the sheet, they block the passage to the sheet despite the traction exerted by extractor rollers placed at the exit of the needling path. This subjects the web to discontinuous longitudinal stresses.

In addition, the needles having a vertical speed and the sheet having a horizontal speed, the fibers driven by the needles are subjected to a strong longitudinal stretching stress. The fiber web is never ideally uniform, it has resistant areas with relatively many fibers and mechanically weaker areas with less fiber. During stretching, the weaker zones deform further and the result is an increase in the lack of uniformity. In extreme cases where stretching is very important, the sheet can tear and fibers can break, depending on their fragility.

Elliptical needle needles are also known which give the tip of the needles an approximately elliptical oval trajectory. In these needling machines, the horizontal component of the elliptical movement partially accompanies the product. But it has been found according to the invention that, during the descent of the needles in the product, the capacity of the needles to drive the fibers in the direction of the thickness of the web is then sometimes decreased. This is thought to be due to insufficient interference between needles and fibers; The result would be that fewer fibers are captured by the barbs of the needles and driven transversely to the plane of the product. In other cases, the "elliptical" needling does not provide a significant advantage over a linear needling, especially when the horizontal component of the elliptical movement is small relative to the speed of advance of the product.

The object of the invention is to propose a device and a needling process that makes it possible in particular to better control the effectiveness of the needling, the barrier effects of the sheet by the needles and / or the stretching effects of the needle. tablecloth.

Presentation of the invention

This objective is achieved with a needling device comprising a frame, means for guiding a product in a direction of longitudinal advance in a plane defining a longitudinal direction and a width of the product, a support for carrying a needle board and actuating and guiding means for actuating the support so that the needles perform in the product a successive striking movement having a main component transverse to the plane, characterized in that it comprises means for defining, with respect to the normal to the plane, an inclination of the main component about an axis substantially parallel to the width of the product.

The device according to the invention may further comprise means for adjusting the inclination of the main component.

During a movement of the needles in the product, the ratio between the needle speed component which is parallel to the direction of advance of the product and the needle speed component which is perpendicular to the direction of advance of the product is a priori variable.

When the needles are in the product with a velocity component parallel to the direction of advance of the product which is not negligible compared to the speed of the product, the stretching of the product is limited, and the movement of the needles accompanies the movement of the product. product. The needles may possibly propel the product in its advance movement if their speed component parallel to the direction of advance of the product is greater than the speed of the product without needles inserted.

The speed of the needles perpendicular to the direction of advance of the product mainly depends, in general, on the one hand on the geometric data of the machine and on the other hand on the striking rate which is chosen for a particular production.

By defining (or adjusting) the inclination of the movement of the hands, it is possible to define (or respectively adjust) how, during the movement of the hands, the ratio between the component of the speed of the hands which is parallel to the direction of the needle changes. advance of the product and the component of the speed of the needles perpendicular to the direction of advance of the product. It is thus possible to define (or respectively adjust) the interactions and the stresses that are exerted between the needles and the product during the movement of the needles.

The device according to the invention makes it possible to optimize the movement of the needles to limit the drawing of the product and to increase the effectiveness of the action of the needles on the fibers of the product, preferably a sheet of fibers.

The striking movement may be a closed-loop movement defining for the tip of the needles said main component combined with a secondary component, for example a swinging or translational component substantially parallel to the longitudinal direction of the product. The ratio of the main and secondary components may vary along the loop. The movement of striking can also be a substantially linear movement, preferably substantially rectilinear.

The actuating and guiding means may comprise means for guiding a positioning pivot connected to the support in a predetermined path, and the means for defining and possibly adjusting the inclination may act by defining and possibly adjusting the orientation of said predetermined path. , preferably around an axis substantially parallel to the width of the product. The predetermined path may be substantially a linear back and forth, preferably substantially straight.

The axis of the positioning pin is preferably placed parallel to and at a distance from a general plane of symmetry perpendicular to the longitudinal direction of the product.

The means for guiding the positioning pin are preferably passive, that is to say devoid of motor means or even semi-active means such as springs.

In one embodiment, the means for guiding the positioning pin may comprise a slideway in which the positioning pin is free to move. If the device according to the invention comprises means for adjusting the inclination of the main component, these adjustment means may comprise means for adjusting the orientation of this slide preferably around an axis substantially parallel to the width of the product. , so as to adjust the orientation of the predetermined path.

In another embodiment, the means for guiding the positioning pin may comprise a deformable quadrilateral comprising an intermediate rod hinged to the board support by the positioning pin, and two guide links each hinged on the one hand at a respective end. the intermediate link, and secondly to the frame by an anchor pin. The quadrilateral can consist of a Watt mechanism, or a Chebyshef mechanism. To allow to adjust the orientation of the predetermined path, at least one of the anchoring pivots may be movable relative to the frame. A path of movement of the anchor pin may be substantially arcuate centered on the axis of the positioning pin when the tips of the needles are halfway through the product.

In one embodiment, the means for guiding the positioning pin can comprise a rod hinged to the frame according to an anchoring axis, and the adjusting means may comprise means for moving the anchor axis relative to the frame. Preferably, the anchor axis is substantially parallel to the width of the product. The means for moving the anchor axis may define for the anchoring axis a trajectory in the form of an arc of a circle centered preferably on an axis substantially parallel to the width of the product. In a variant, the means for guiding the axis connected to the support can be mounted on a turntable, which can preferably rotate about an axis substantially parallel to the width of the product. In another variant, the means for moving the anchor axis may comprise a guide rail of the anchor axis, and means for locking the position of the anchor axis in the slideway.

• des moyens pour appliquer au support un mouvement de va-et-vient sensiblement perpendiculaire à la direction d'avance du produit, et
• des moyens pour appliquer au support un mouvement de balancement sensiblement parallèle à la direction d'avance du produit.

To actuate the needles in a reciprocating movement transverse to the plane of advance of the product, the actuating means may comprise:

• means for applying to the carrier a reciprocating motion substantially perpendicular to the direction of advance of the product, and
• means for applying to the support a swinging movement substantially parallel to the direction of advance of the product.

The actuating means may comprise two crankshafts rotating in opposite directions from one another and two actuating rods extending transversely to the plane of the product and each connected on the one hand to a respective crankshaft and on the other hand to the needle board support by an actuating pin. During rotation of the crankshafts, the needle board support is driven by a main movement back and forth transverse to the plane of the product. If the actuating and guiding means comprise means for guiding a positioning pin connected to the support in a predetermined path, the axis of the positioning pivot is preferably close to a first of said actuation axes, or even coincidental. with this first axis, the second actuating axis being preferably free relative to the frame.

The crankshafts preferably rotate about axes parallel to the width of the product, with a mutual angular setting which is preferably adjustable, and the actuating axes are substantially parallel to the width of the product. Thus, when the mutual setting of the crankshaft is such that there is a non-zero phase shift between the crankshafts, the actuating means also apply to the support a secondary swing movement substantially parallel to the direction of advance of the product.

The possible means for adjusting the phase shift preferably comprise a differential having an output shaft connected to a first of the crankshafts, an input shaft connected to a motor shaft, and an element such as a planet carrier which is angularly adjustable to adjust the phase shift.

According to yet another aspect of the invention, there is provided a needling process implemented in a device according to the invention, comprising guiding a product in a direction of longitudinal advance in a plane defining a longitudinal direction. and a width of the product, an actuation and a guiding of a support for carrying a needle board so that the needles perform in the product a reciprocating movement having a main component transverse to the plane, characterized in that that is defined, relative to the normal plane, an inclination of the main component about an axis substantially parallel to the width of the product.

In the context of the actuation and guidance of the support, it is possible to guide a positioning pin connected to the support in a predetermined path.

The method according to the invention may further comprise an adjustment of the inclination of the main component.

It is possible to adjust said orientation of the predetermined path to adjust the inclination of said main component.

The striking movement may be a closed-loop movement, preferably substantially elliptical or ovoid. The striking movement can also be a substantially linear, preferably substantially rectilinear, back-and-forth movement.

The movement of the needles in the product may include insertion of the needles into the product with a speed substantially perpendicular to the longitudinal direction of the product, or may include insertion of the needles into the product with a speed having a component substantially parallel to the longitudinal direction of the product.

The movement of the needles in the product may comprise a withdrawal of the needles out of the product with a speed substantially perpendicular to the longitudinal direction of the product, or may comprise a withdrawal of the needles out of the product with a speed having a component substantially parallel to the longitudinal direction of the product.

Description of the Figures and Embodiments

• la figure 1 est une vue schématique de profil d'un premier mode de réalisation d'un dispositif selon l'invention, les vilebrequins du dispositif étant en phase ;
• la figure 2 est une vue du premier mode selon la figure 1, mais à plus petite échelle et avec un déphasage des vilebrequins,
• la figure 3 illustre quatre vues schématiques, de profil et successives du premier mode de réalisation en fonctionnement avec déphasage des vilebrequins,
• les figures 4 et 5 illustrent chacune une vue de profil de deux mouvements possibles de la pointe d'une aiguille,
• la figure 6 est une vue schématique de profil d'un détail de l'aiguilletage, illustrant un mouvement de la pointe des aiguilles,
• la figure 7 est une vue schématique de dessus d'une première variante de moyens pour régler le déphasage,
• la figure 8 est une vue schématique de dessus d'une deuxième variante de moyens pour régler le déphasage,
• la figure 9 est une vue analogue à la figure 1 mais relative à un deuxième mode de réalisation du dispositif selon l'invention,
• les figures 10 et 11 illustrent chacune de profil un mouvement de la pointe d'une aiguille dans une nappe de fibres,
• la figure 12 illustre de profil deux mouvements possibles de la pointe d'une aiguille associée à un dispositif selon l'invention dans une nappe de fibres,
• la figure 13 illustre la vitesse de la nappe de fibres de la figure 12, en fonction du temps, et pour les deux mouvements possibles, et
• les figures 14 et 15 sont des vues schématiques analogues à la figure 1, mais relatives à un troisième et respectivement un quatrième mode de réalisation du dispositif selon l'invention.

Other features and advantages of the invention will appear on reading the detailed description of embodiments and implementation in no way limiting, and the accompanying drawings, wherein:

• the figure 1 is a schematic side view of a first embodiment of a device according to the invention, the crankshafts of the device being in phase;
• the figure 2 is a view of the first mode according to the figure 1 , but on a smaller scale and with a phase shift of the crankshafts,
• the figure 3 illustrates four schematic, profile and successive views of the first embodiment in operation with phase shift of the crankshafts,
• the Figures 4 and 5 each illustrate a profile view of two possible movements of the tip of a needle,
• the figure 6 is a schematic side view of a detail of the needling, illustrating a movement of the needle points,
• the figure 7 is a schematic view from above of a first variant of means for adjusting the phase shift,
• the figure 8 is a schematic view from above of a second variant of means for adjusting the phase shift,
• the figure 9 is a view similar to the figure 1 but relating to a second embodiment of the device according to the invention,
• the Figures 10 and 11 each illustrate a movement of the tip of a needle in a sheet of fibers,
• the figure 12 illustrates in profile two possible movements of the tip of a needle associated with a device according to the invention in a sheet of fibers,
• the figure 13 illustrates the speed of the fiber web of the figure 12 , as a function of time, and for both possible motions, and
• the Figures 14 and 15 are schematic views analogous to the figure 1 , but relating to a third and fourth embodiments of the device according to the invention.

We will first describe with reference to Figures 1 to 8 a first embodiment of the needling device according to the invention, implementing the method according to the invention.

The device comprises a stripping plate 21 and a needling plate 23 approximately parallel to each other, carried by a not shown frame. Unrepresented cylinders allow, in known manner, to adjust the position of the plates relative to the frame. These plates are designed to guide between them a sheet of fibers 22 (partially shown) in a plane comprising a longitudinal direction 24 in which advance the web 22 under the action of not shown drive means, and a direction 48 parallel to the width of the tablecloth. The sheet is endless in its longitudinal direction 24. The plates are provided with holes for passing needles 50 (only five are shown) attached to a board 1 substantially parallel to the plane of the sheet. The needles are parallel to each other and substantially perpendicular to the needling and needling plates, and therefore to the guide plane of the sheet. The stripping plate 21 is located between the needling plate 23 on the one hand, and the needle board 1 on the other hand. On the opposite side to the needles 50, the board 1 is fixed to a support 42.

In the following, we consider non-limitatively that the guide plane of the web is horizontal, as is very often the case in practice. It is also considered that the needle board 1 and its guiding and actuating means are located above the sheet. But the invention is applicable on each side of the web, where even both sides at once.

Two identical and substantially vertical actuating rods 2, 3 are each connected to the support 42 by a respective actuating pivot 5, 6 having a respective geometric axis of actuation 51, 52, and are each connected by an eccentric pivot 16, 17 to a respective crankshaft 14, 15. The axes of these pivots are substantially parallel to the width of the product, as all axes of articulation, rotation and pivoting described so far and below. Each crankshaft 14, 15 is mounted in the frame by rotational bearings 18, 19 of which only the axes geometric are represented. The crankshafts are mounted one after the other relative to the longitudinal direction 24, in a common plane substantially parallel to that of the path of the ply 22.

Thanks to motor means not shown in the figure 1 , the crankshafts are rotated at equal speed and in opposite directions relative to one another about the axes of the bearings 18, 19 according to the arrows 91, 92. If the crankshaft pivots 16, 17 have, around the axes of the bearings 18 and 19, angular positions symmetrical with respect to a plane 25 substantially perpendicular to the longitudinal direction 24 of the web, it is said that the crankshafts are rotated in phase (as shown in FIG. figure 1 ); otherwise, crankshafts are said to be rotated with a phase shift relative to each other (as shown in FIGS. figures 2 and 3 ). The first embodiment of the device according to the invention comprises means for adjusting the phase shift between the crankshafts. Embodiments of these means are described later with reference to Figures 7 and 8 .

A point of the support 42, materialized by a positioning pin 49 integral with the support 42, is guided in a linear path which in this example is substantially rectilinear and transverse to the plane of the path of the web. This guidance is provided by a mechanism 53 which is passive, ie devoid of dynamic means such as motors. There are also no semi-active means such as springs. The position of the support 42, and therefore of the needle board 1 and the needles 50, is defined at each instant by the angular position of the crankshafts in combination with the guidance of the positioning pin 49 along its rectilinear trajectory, with respect to which the support 42 can rotate. The guide means of the positioning pivot 49 make it possible to define the orientation and the inclination of the path of the pivot 49 relative to the plane of the ply 22. It has been found that the orientation of the path of the pivot 49 makes it possible to define, relative to the normal plane of the web 22, an inclination of the movement of the needles 50. In addition, the particular embodiment shown comprises means 4 which will be described in detail later to adjust the inclination of the trajectory of the pivot of positioning 49.

The positioning pivot 49 is closer to a first 51 of the actuating axes than to the second actuating axis 52. In the example shown, the axis of the positioning pivot 49 coincides with the first actuation axis 51, which here is the one located forward relatively in the direction of progression 24 of the web. Thus, the positioning pin 49 and a first of the actuating axes 51 are guided along a path. The second of the actuating axes 52 is free relative to the frame.

The general operation is as follows: when the crankshafts are in phase as shown in the figure 1 , the tips of the needles perform a rectilinear back and forth movement forming with the guide plane of the sheet an angle substantially equal to the angle formed by the trajectory of the positioning pin 49 with the guide plane of the sheet. This movement back and forth is a movement of successive striking of the needles in the sheet. When there is a phase shift between the crankshafts, this results in a rocking motion of the support 42 and the board 1. More specifically, the support 42 oscillates angularly around the axis of the positioning pin 49 at the same time as the Pivot 49 moves back and forth along its substantially straight path. This results for the needles 50 a movement comprising in addition to the main component transverse to the plane of the web a secondary component substantially parallel to the direction of the longitudinal feed of the web 22. The trajectory of the tips of the needles becomes a closed curve substantially elliptical. The adjectives "principal" and "secondary" correspond to convenient vocabulary choices for respectively designating a component transverse to the plane of the web and a component substantially parallel to the direction of the longitudinal advance of the web. However, the phase shift of the crankshafts is in general sufficiently small so that the main component, transverse to the horizontal plane of advance of the web, is greater than the secondary component. The direction of the phase shift is chosen relative to the direction of rotation of the crankshafts so that the tips of the needles advance in the same direction as the web (direction 24) when these peaks are engaged in the web. When in the case of phase shift, the positioning pin 49 is guided along a line perpendicular to the plane of the sheet, the substantially elliptical curve has an axis perpendicular to the plane of the sheet, corresponding to the penetration component or principal component of the movement of the needles. in the tablecloth. When, as shown by figures 2 and 3 , a phase shift of the crankshafts is combined with an inclination of the trajectory of the pivot 49, the axis of the ellipse corresponding to the penetration component forms with the plane of the web an angle of inclination substantially equal to that of the trajectory of the pivot 49 relative to the plane of the web.

For guiding the positioning pivot 49 and the actuating axis 51 according to the aforementioned linear trajectory, the illustrated embodiment provides for connecting the pivot 49 to the frame not shown by means of a deformable quadrilateral which consists of this example in a Chebyshev mechanism. This quadrilateral comprises an intermediate rod 7 connected in its center to the support 42 of the plate 1 by the positioning pin 49; two guide rods 8, 9 each connected to a respective end of the rod 7 by an intermediate pivot 10, 11, each guide rod 8, 9 being further connected to the frame by an anchor pin 12, 13; and the frame considered as a fixed link connecting the anchoring pivots 12, 13. The intermediate link 7 oscillates in the vicinity of an orientation perpendicular to the guide plane of the ply 22. The distance between the anchor axis of the pivot anchor 12 or 13 and the axis of the intermediate pivot 10 or 11 is identical for each guide rod 8, 9. The axis of the positioning pin 49 is located midway between the axes of the intermediate pivots 10, 11 The anchoring pivots are located on the same side of the plane containing the axes of the positioning pivot 49 and the two intermediate pivots 10, 11. The two guide rods 8, 9 intersect each other. During the movement of the needles, the position of the anchoring pivots 12, 13 on the frame is constant. The Tchebychef mechanism guides the axis of the positioning pin 49 along a substantially straight back and forth path parallel to the line connecting the anchoring pivots 12, 13.

With respect to the first actuating axis 51 associated with the positioning pivot 49, the Tchebychef mechanism is entirely located on the opposite side to the second actuating axis 52. This allows the connecting rod-crank systems to be brought closer to one another .

In addition, the Tchebychef mechanism largely releases the space between the plane passing through the actuating axes 51, 52 and the needle board 1. This makes it possible to reduce the distance between the needles 50 and the plane passing through the axes 51, 52.

The device comprises means for adjusting the inclination of the movement of the needles back and forth through the web. In the example shown, these means operate by adjusting the inclination of the linear trajectory of the positioning pin 49. For this, more particularly, the position of the line connecting the pins 12, 13 is adjusted by relative to the frame. The orientation of the path of the positioning pin 49 substantially corresponds to the inclination of the penetration movement of the needles. A first slide 4 makes it possible to move the anchoring axis of a first one of the anchoring pivots 12. A displacement of the anchoring pivot 12 in the slideway 4 makes it possible to adjust the orientation (or inclination) of the path positioning pivot 49 and thus the inclination of the main component of the movement of the needles. The slide has a shape of a circular arc centered on an axis parallel to the width of the web, so that the inclination of the main component of the movement of the needles (and the inclination of the path of the pivot 5, 49) can be set around an axis parallel to the width of the web. A not shown cylinder makes it possible to modify and block the position of the anchoring pivot 12 in the slideway 4.

In the example shown in figure 1 , the phase shift is zero between the crankshafts 14, 15, and the anchoring pivots 12, 13 are aligned perpendicular to the plane of advance of the web. The trajectory of the positioning pin 49 is therefore rectilinear and perpendicular to the plane of the sheet. This trajectory is positioned so that the plane 25 of symmetry of the two crankshafts passes between the two axes of actuation 51, 52 being equidistant from them. The needles then have a rectilinear linear back-and-forth movement substantially perpendicular to the plane of the sheet.

The figure 2 illustrates a state of the device of the figure 1 when the phase angle of the crankshafts 14, 15 has been set to a non-zero value. The phase shift is such that the front actuating rod 2 is in advance of the rear actuating rod 3. In addition, the pivot has been adjusted. anchoring 12 in the slide 4 so that the anchoring pivots 12, 13 are aligned on a straight line 10 inclined in the direction said "forward" around an axis parallel to the width of the web. The upper anchoring pivot 12 is offset in the direction of longitudinal advance 24 with respect to the lower anchoring pivot 13.

The figure 3 illustrates four successive states of the first embodiment of the device according to the invention when the crankshafts 14, 15 are rotated about the axes of the rotational bearings 18, 19 with the same phase shift as at the figure 2 , while the straight line 20 connecting the anchoring pivots 12, 13 is this time tilted backwards thanks to a different setting of the anchoring pivot 12 in its slideway 4.

A not shown variant of this first embodiment further comprises a second slide to move the position of the anchor axis of the second anchor pin 13, and a jack for modifying and blocking the position of this anchor pin. 13 in this slide. A displacement of the anchor pin 13 in the second slide also makes it possible to adjust the orientation of the path of the axis of the positioning pin 49 and the inclination of the main component of the movement of the needles. Both slides can be used independently or simultaneously. It is thus possible to better optimize the geometry of the Tchebychef mechanism as well as the position of the path of the pivot 49.

This first embodiment is a preferred embodiment. It has many advantages. The size of the guide rods 8, 9 is limited because they are on the same side of the intermediate rod 7. The adjustment of the inclination of the movement of the needles can be done by means of a single slide 4. The first slide 4 (and possibly the second slide if it exists) has a circular arc shape centered on an axis parallel to the width of the web.

The choice of the center of the arc determines the overlap of the needle movement curves for different positions of the anchor pin in the slider. The figure 4 illustrates the case where the arc is centered at a point considered unfavorable. One passes from one path to the other substantially by a geometric rotation around a center 93 located near the vertex of these trajectories, out of the path of the web. The holes in the stripping plate 21 and the needling plate 23 should have a large width to allow the needles to pass for different inclinations of the penetration component (principal component) of the elliptical movement.

In the preferred example shown in figure 5 it has been arranged that the center of geometric rotation is situated in the guide plane of the sheet near the bottom of the trajectories. For this, the arc of the slide 4 is centered on the position occupied by the axis of the positioning pin 49 when the tips of the needles are substantially halfway in the fiber web 22. This is typically equivalent to a position of the needle board at one-sixth of its vertical stroke from its bottom dead center. The width 36 of the holes in the stripping and needling plates can thus be reduced for the same range of variation of the inclination of the elliptical curves. This arrangement makes it possible to increase mechanical strength of the plates 21, 23, and / or the density of holes in the plates 21, 23 and therefore the density of needles on the plate 1 and the productivity of the device.

• une largeur d, qui croît avec le déphasage entre les vilebrequins, le mouvement étant sensiblement rectiligne si la largeur est nulle;
• pour la composante principale du mouvement, une inclinaison α autour d'un axe parallèle à la largeur de la nappe (par exemple de l'ordre du degré); et
• un sens de parcours de la boucle, par exemple horaire ou contra-horaire, qui dépend notamment du sens du déphasage et du sens de rotation des vilebrequins.

An example of needlepoint movement is illustrated in figure 6 . In general, the movement of the needles is a closed loop 26 (preferably elliptical) of which different characteristics can be regulated:

• a width d, which increases with the phase shift between the crankshafts, the movement being substantially rectilinear if the width is zero;
• for the main component of the movement, an inclination α about an axis parallel to the width of the web (for example of the order of the degree); and
• a direction of travel of the loop, for example hourly or counter-hourly, which depends in particular on the direction of the phase shift and the direction of rotation of the crankshafts.

If the loop is an ellipse, the width d is the small diameter of the ellipse, and the main component is the large diameter of the ellipse. The means for adjusting the phase shift between the crankshafts make it possible to adjust the width d of the loop. The position of the first anchoring pivot 12 in the slideway 4 (and / or possibly the second anchoring pivot 13 in the second slide if it exists) makes it possible to adjust the inclination α.

• le déphasage entre les vilebrequins 14, 15 est sensiblement nul, et
• les positions des pivots d'ancrage 12, 13 sont telles que le mouvement du pivot de positionnement 49 est sensiblement vertical pendant le mouvement des aiguilles,

alors le mouvement des pointes des aiguilles est un mouvement rectiligne vertical.If as illustrated in figure 1 :

• the phase difference between the crankshafts 14, 15 is substantially zero, and
• the positions of the anchoring pivots 12, 13 are such that the movement of the positioning pin 49 is substantially vertical during the movement of the needles,

then the movement of the needle points is a vertical rectilinear motion.

• il existe un déphasage entre les vilebrequins 14, 15, et
• les positions des pivots d'ancrage 12, 13 sont telles que le mouvement du pivot de positionnement 49 est sensiblement vertical pendant le mouvement des aiguilles,

alors le mouvement des pointes des aiguilles est un mouvement en boucle, dont la plus grande dimension est verticale.Yes :

• there is a phase shift between the crankshafts 14, 15, and
• the positions of the anchoring pivots 12, 13 are such that the movement of the positioning pin 49 is substantially vertical during the movement of the needles,

then the movement of the points of the needles is a looping motion, the largest dimension of which is vertical.

• le déphasage entre les vilebrequins 14, 15 est sensiblement nul, et
• les positions des pivots d'ancrage 12, 13 sont telles que pendant le mouvement des aiguilles le mouvement du pivot de positionnement 49 est incliné vers l'avant,

alors le mouvement des pointes des aiguilles est un mouvement linéaire sensiblement rectiligne et incliné vers l'avant autour d'un axe parallèle à la largeur de la nappe.Yes :

• the phase difference between the crankshafts 14, 15 is substantially zero, and
• the positions of the anchoring pivots 12, 13 are such that during the movement of the needles the movement of the positioning pin 49 is inclined towards the front,

then the movement of the needle points is a substantially straight linear motion and inclined forwards about an axis parallel to the width of the web.

• il existe un déphasage entre les vilebrequins 14, 15, et
• les positions des pivots d'ancrage 12, 13 sont telles que pendant le mouvement des aiguilles le mouvement du pivot de positionnement 49 est incliné vers l'avant,

alors le mouvement des pointes des aiguilles est une boucle dont le grand diamètre est incliné vers l'avant autour d'un axe parallèle à la largeur de la nappe.If as illustrated in figure 2 :

• there is a phase shift between the crankshafts 14, 15, and
• the positions of the anchoring pivots 12, 13 are such that during the movement of the needles the movement of the positioning pin 49 is inclined towards the front,

then the movement of the needle points is a loop whose large diameter is inclined forward around an axis parallel to the width of the web.

• le déphasage entre les vilebrequins 14, 15 est sensiblement nul, et
• les positions des pivots d'ancrage 12, 13 sont telles que pendant le mouvement des aiguilles le mouvement du pivot de positionnement 49 est incliné vers l'arrière,

alors le mouvement des pointes des aiguilles est un mouvement linéaire sensiblement rectiligne et incliné vers l'arrière.Yes :

• the phase difference between the crankshafts 14, 15 is substantially zero, and
• the positions of the anchoring pivots 12, 13 are such that during the movement of the hands the movement of the positioning pin 49 is inclined towards the rear,

then the movement of the needle points is a linear movement substantially rectilinear and inclined to the rear.

• il existe un déphasage entre les vilebrequins 14, 15, et
• les positions des pivots d'ancrage 12, 13 sont telles que pendant le mouvement des aiguilles le mouvement du pivot de positionnement 49 est incliné vers l'arrière,

alors le mouvement des pointes des aiguilles est une boucle dont le grand diamètre est incliné vers l'arrière, comme illustré à la figure 6.If as illustrated in figure 3 :

• there is a phase shift between the crankshafts 14, 15, and
• the positions of the anchoring pivots 12, 13 are such that during the movement of the hands the movement of the positioning pin 49 is inclined towards the rear,

then the movement of the needle points is a loop whose large diameter is tilted backwards, as shown in FIG. figure 6 .

Means for adjusting the phase shift between the crankshafts are shown in Figures 7 and 8 . These means use an adjustable differential 87 to create from a motor shaft 54 a phase shift between a first and a second output shaft 55, 56, each integral with a respective one of the crankshafts 14, 15 and rotating in opposite directions.

A first preferred embodiment of means for adjusting the phase shift is shown in FIG. figure 7 . The drive shaft 54 drives a primary gear 66 which drives in the opposite direction to the drive shaft the second crankshaft 15 meshing with a secondary gear 67 connected to the second crankshaft 15 by the second output shaft 56. The dimensions of the gears 66 and 67 are such that the second crankshaft 15 rotates at a smaller angular velocity than that of the drive shaft 54. The drive shaft 54 further drives the first crankshaft 14 through a phase difference differential 87. . A stage 72 satellite of the differential 87 comprises a first gear stage 70 meshing with a first sun gear 68 integral with the drive shaft 54 and a second gear stage 71 meshing with a second sun gear 69 integral with the output shaft 55. satellite 72 is freely rotatable along its own axis in a differential cage 73. The dimensions of the teeth 68, 69, 70 and 71 of the differential 87 are such that when the axis of the satellite 72 is immobilized (cage 73 immobile), the first crankshaft 14 rotates at an angular speed smaller than that of the drive shaft 54 but equal to and opposite to that of the second crankshaft 15. The angular position of the cage 73 about the common axis 74 of the first and second planetary 68 and 69 determines the phase difference between the output shafts 55 and 56. A servo motor attached to the frame 65 controls the angular position of the cage 73 around the common axis 74 via a gearbox 75 comprising a worm 75v driven by the servo motor (not shown) meshing with a ring gear 75c formed on the periphery of the radially outer face of the cage 73.

A second variant of means for adjusting the phase shift, represented in FIG. figure 8 , will be described only for its differences from the previous one. The drive shaft 54 drives a primary gear 57 which drives in the same direction as it the second crankshaft 15 via a cascade of an intermediate gear 58 and a secondary gear 59 connected to the second crankshaft 15 by the second output shaft 56 The gears 57 and 59 have the same diameter so that the second crankshaft 15 rotates at an angular speed equal to that of the drive shaft 54. In the differential 87, the two planetary gears 60 and 61 are now conical and of the same diameter. , and both mesh with the same conical toothing a satellite 76 whose axis is radial relative to the axis 74 of the planetaries 60 and 61. When the cage 62 is stationary, the first differential gear 60 drives the second differential gear 61 and the first crankshaft 14 with a speed equal to and opposite to that of the motor shaft 54.

For both variants, the gear 75 is irreversible in that the moments of rotation undergone by the cage 73 about its axis 74 relative to the frame are unable to rotate the screw 75v. The cage 73 is immobilized in rotation about its axis 74 relative to the frame when the servomotor is inactive. The means described above for adjusting the phase shift make it possible to adjust the phase shift during a needling operation, without interrupting it. The auger mechanism and ring gear could be replaced by any linear actuator such as a hydraulic or mechanical cylinder.

We will now describe with reference to the figure 9 a second embodiment of the device according to the invention, which will be described only for its differences with respect to that of Figures 1 to 8 . The means 53 for guiding the positioning pin 49 along its substantially linear trajectory is a Watt mechanism, which differs from the Chebychef mechanism in that the guide rods 28, 29, instead of crossing each other, are located on either side. else of the plane defined by the axes of articulation of the intermediate rod 7. In the example, the link 29 located above the plane of the axes of actuation 5, 6 and associated with the guide pin 11 furthest the guide plane of the web extends rearwardly relative to the direction 24, and between the two connecting rods 2, 3. Each anchor pin 32, 33 can be moved by sliding inside a slide 34 respective, by means of a jack (not shown) also able to lock the pivot in a selected position in the slide. A displacement of the anchoring pivots 32, 33 in the slideway 34 makes it possible to adjust the orientation of the path of the axis of the positioning pivot and thus the inclination of the principal component of the movement of the needles around an axis parallel to the width of the web 22. The slides 34 are concentric circle segments with each other. Typically, the anchoring pins 32, 33 are adjusted in their slideway 34 so that the mechanism is capable of a configuration in which the intermediate rod 7 is perpendicular to the two anchor rods 28, 29.

• les fibres butent plus fortement contre l'aiguille ;
• les fibres sont plus entraînées par l'aiguille lors de l'insertion de l'aiguille dans la nappe ; et
• l'aiguille barre davantage l'avancement de la nappe, freine et étire davantage la nappe.

Each of the Figures 10, 11 and 12 where the direction of travel 24 of the web is shown inverted with respect to the previous views, illustrates a side view of a movement of the tip of a needle 50 of a needling machine equipped with a device according to the invention, in a fiber web 22 guided in a direction of horizontal longitudinal advance 24 between a breaking plate 21 and a needling plate 23. The direction of the secondary component of the speed of the needle 50 is little different from the direction of longitudinal advance 24 of the web. The needle includes barbs provided to hook fibers that interfere with the needle due to the product advance and insertion of the needle into the web. When increasing the difference between the speed of the web and the secondary component of the speed of the needle:

• the fibers abut more strongly against the needle;
• the fibers are more driven by the needle during insertion of the needle into the web; and
• the needle further slows the progress of the sheet, slows down and further stretches the sheet.

• une partie 38 d'insertion ou de pénétration de l'aiguille dans la nappe, et
• une partie 39 de retrait de l'aiguille hors de la nappe.

The movement shown in figure 10 is an ellipse inclined towards the rear, that is to say whose vertex remote from the sheet is shifted in the direction opposite to the longitudinal advance 24. The movement of the needle can be broken down into two parts in which the needle interacts in different ways with the fiber web:

• a part 38 of insertion or penetration of the needle into the sheet, and
• a portion 39 of withdrawal of the needle out of the web.

In the insertion portion 38, the horizontal speed of the needle is substantial relative to the horizontal advance of the web. The needle leads to fibers smoothly accompanying the advance of the sheet, which allows to draw the sheet and limit the longitudinal stretching of the sheet.

In the withdrawal portion 39, the speed of the needle is substantially vertical. The horizontal speed of the needle is negligible compared to the horizontal advance of the web, and the needle blocks the advance of the web. There is not much vertical work of the needles in the tablecloth because the barbs of the needles are oriented downwards.

• une partie 40 d'insertion de l'aiguille dans la nappe, et
• une partie 41 de retrait de l'aiguille hors de la nappe.

The movement shown in figure 11 is a forward inclined ellipse, that is to say whose vertex remote from the sheet is shifted in the direction of the longitudinal advance 24. The movement of the needle can be break down into two parts in which the needle interacts in different ways with the fiber web:

• a part 40 for inserting the needle into the sheet, and
• a portion 41 of withdrawal of the needle out of the web.

In the insertion portion 40, the speed of the needle is substantially vertical. The horizontal speed of the needle is negligible compared to the horizontal advance of the web. The needle drives and works the fibers efficiently, but blocks the advance of the web.

In the withdrawal portion 41, the horizontal speed of the needle is substantial relative to the horizontal advance of the web, and goes in the same direction as the advance of the web. The needle accompanies the movement of the sheet and can tow the sheet.

The figure 12 illustrates two possible movements of one of the needles of a device according to the invention: a substantially elliptical movement 77 transverse to the ply 22 and inclined in the direction of the longitudinal advance 24 of the ply, and a substantially elliptical movement 78 no inclined and substantially perpendicular to the plane of the web.

When the needle 50 is not in the ply 22, the ply advances substantially at the speed of extracting rollers located downstream of the needling device according to the invention. When the needle 50 is in the sheet, the speed of the sheet is substantially equal to the secondary component of the speed of the needle. The needle 50 enters and leaves the web with horizontal speeds different from the speed of the rollers, and the web is therefore subjected to shaking and stretching. This phenomenon is particularly marked when the sheet is thick, when the spacing between stripper and needling table is large or when the penetration depth of the needle in the sheet is large.

The thickness of the sheet is generally slightly less than the distance between the stripper and the needling plate. During the entry 80 of the needle into the sheet, the needle 50 plates the sheet against the needling plate 23. At the exit 81 of the needle out of the sheet, the needle 50 plates the sheet against the stripper 21. Thus, the vertical position of the needle between the stripper 21 and the needling table 23 is different at the time of entry 80 and the outlet 81 of the needle. The horizontal component of the speed of the needle 50 is therefore a priori different at the time of entry 80 and the exit 81 of the needle even if the ellipse is vertical.

As illustrated in figure 12 for the movement 78 perpendicular to the web, the horizontal component of the speed of the needle 50 is greater at the entry 80 of the needle than at the exit 81 of the needle. As a result, the web is less braked during the entry 80 of the needle than at the exit 81 of the needle. As illustrated in figure 13 the horizontal velocity 82 of the web during the entry 80 of the needle is therefore greater than the horizontal speed 83 of the web during the exit 81 of the needle, but lower than the horizontal speed 84 of the web when there is no needle in the web. At the exit of the needle, the speed of the web is minimum, and can even be negative, that is to say, opposite to the direction of longitudinal advance of the average speed of the web. During a time interval between the entry and exit of the needle, around the bottom dead center of the movement of the needle, the needle causes the web to a speed 90 greater than the horizontal speed 84 of the web when the needle is not in the tablecloth.

• de diminuer la vitesse horizontale de l'aiguille et donc de la nappe lors de l'entrée 80 et durant l'insertion 88 de l'aiguille dans la nappe, de sorte que l'aiguille capte mieux les fibres de la nappe et travaille mieux la nappe ;
• d'augmenter la vitesse horizontale de l'aiguille et donc de la nappe durant le retrait 89 et lors de la sortie 81 de l'aiguille hors de la nappe, de sorte que l'aiguille freine moins la nappe lorsque les barbes de l'aiguille ne peuvent pas travailler la nappe ;
• de diminuer la vitesse horizontale 85 de la nappe lors de l'entrée 80 de l'aiguille tout en augmentant la vitesse horizontale 86 de la nappe lors de la sortie 81 de l'aiguille, de manière à égaliser ces deux vitesses et à augmenter le minimum 86 de la vitesse de la nappe ;
• de diminuer la différence entre d'une part la vitesse horizontale 84 de la nappe lorsqu'il n'y a pas d'aiguille dans la nappe, et d'autre part la vitesse minimum parmi la vitesse de la nappe lors de l'entrée ou de la sortie de l'aiguille, de manière à diminuer les secousses et l'étirage de la nappe.

As illustrated in figure 12 by forwardly inclining the movement 77 of the needle with respect to the non-inclined movement 78, the horizontal speed of the needle during its entry 80 is decreased and the horizontal speed of the needle is increased when it is released. 81. Thus, as illustrated in figure 13 the braking of the ply is increased during the entry of the needle and the braking of the ply is reduced when the needle is released. The inclination of the movement 77 of the needle relative to the non-inclined movement 78 therefore allows:

• to reduce the horizontal speed of the needle and therefore of the web during entry 80 and during insertion 88 of the needle into the web, so that the needle better captures the fibers of the web and works better the tablecloth ;
• to increase the horizontal speed of the needle and thus of the web during the withdrawal 89 and during the exit 81 of the needle out of the web, so that the needle less brakes the web when the barbs of the needle can not work the tablecloth;
• to reduce the horizontal speed 85 of the web during the entry 80 of the needle while increasing the horizontal speed 86 of the web during the output 81 of the needle, so as to equalize these two speeds and to increase the minimum 86 of the velocity of the water table;
• to reduce the difference between, on the one hand, the horizontal speed 84 of the sheet when there is no needle in the sheet, and, on the other hand, the minimum speed among the speed of the sheet at the time of entry or the exit of the needle, so as to reduce shaking and stretching of the web.

In a third embodiment of the device according to the invention, illustrated in FIG. figure 14 the anchor pivot adjustment slide (s) are removed. The anchoring pivots 43, 44 of the deformable quadrilateral are located on a turntable 45 connected to the frame by a gear system. The turntable makes it possible to rotate simultaneously the positions of the two anchoring pivots about an axis substantially parallel to the width of the sheet, and to adjust the inclination of the main component of the movement of the needles.

In a fourth embodiment of the device according to the invention illustrated in FIG. figure 15 , the guide links are removed. The positioning pin 49 is free to slide in a straight slide 47. The inclination of the straight slide 47 is adjustable about an axis substantially parallel to the width of the web. The slide guides the movement of the board and needles. By adjusting the inclination of the slide, the inclination of the main component of the movement of the hands is adjusted.

Of course, the invention is not limited to the examples which have just been described and numerous adjustments can be made to these examples without departing from the scope of the invention.

In particular, one can imagine many ways to define or adjust the inclination of the main component of the movement of the needles.

It is also possible to perform a quasi-rectilinear guidance by connecting the positioning pin with the frame by means of a relatively long, approximately horizontal, oscillating arm, one end of which is articulated to the positioning pin 49 connected to the support and the other end is hinged to the frame. Adjusting the inclination by moving relative to the frame the hinge axis with the frame.

In all the embodiments, instead of guiding a positioning pin coaxial with the articulation between the support and an actuating rod, it is possible to guide a separate positioning pin, integral with the support and specially designed for this guidance.

Similarly, one can imagine many forms for the movement of needles, such as linear shapes or loops in the form of ellipses, D, O or 8.

Claims (32)

Needling device comprising a frame, means for guiding (21, 23) a product (22) in a direction of longitudinal advance (24) in a plane defining a longitudinal direction (24) and a width of the product, a support (42) for carrying a needle board (1), and actuating and guiding means (2, 3, 5-19) for actuating the holder so that the needles (50) effect in the product a movement successive striking device having a major component transverse to the plane, characterized in that it comprises means for defining, with respect to the normal to the plane, an inclination of the main component about an axis substantially parallel to the width of the product. Device according to claim 1, characterized in that the striking movement is a closed-loop movement (26) defining for the tip of the needles said main component combined with a secondary component substantially parallel to the longitudinal direction of the product. Device according to claim 1, characterized in that the striking movement is a substantially linear movement, preferably substantially rectilinear. Device according to one of claims 1 to 3, characterized in that the actuating and guiding means comprise means for guiding a positioning pin (49) connected to the support (42) in a predetermined path, and in that the means for defining the inclination make it possible to define the orientation of said predetermined path. Device according to claim 4, characterized in that the predetermined path is substantially a linear back-and-forth, preferably substantially rectilinear. Device according to claim 4 or 5, characterized in that the means for guiding the positioning pin (49) comprises a slide (47) preferably inclined or inclinable. Device according to claim 4 or 5, characterized in that the guide means of the positioning pin comprise a deformable quadrilateral (7, 8, 9, 10, 11, 12, 13) comprising an intermediate link (7) connected to the support ( 42) by a hinge according to said positioning pivot (49) and two guide rods (8, 9) articulated each on the one hand to a respective end of the intermediate link, and on the other hand to the frame along an axis of anchoring (12, 13). Device according to claim 7, characterized in that the quadrilateral consists of a Watt mechanism. Device according to claim 7, characterized in that the quadrilateral consists of a Tchebychef mechanism. Device according to one of claims 1 to 9, characterized in that it further comprises means for adjusting the inclination (4, 34) of the main component. Device according to claim 4 or 5, characterized in that it further comprises means for adjusting the inclination (4, 34) of the main component by adjusting the orientation of the predetermined path. Device according to claim 11, characterized in that the means for guiding the positioning pin (49) connected to the support comprise a link articulated to the frame according to an anchoring axis (12, 13), and in that the adjustment means comprise means (4, 34) for moving the anchor pin (12, 13) relative to the frame. Device according to one of claims 5 to 7, characterized by means for moving the anchor axis (12, 13) relative to the frame, so as to adjust the inclination of the predetermined path and also the orientation of the main component. Device according to claim 12 or 13, characterized in that the means for moving the anchor axis define for the anchoring axis a trajectory in the form of a circular arc centered on an axis substantially parallel to the width of the product . Device according to Claim 14, characterized in that the path of movement of the anchoring pivot is substantially in the form of a circular arc centered on the axis of the positioning pivot (49) when the points of the needles are halfway in the product. . Device according to one of claims 12 to 15, characterized in that the means for moving the anchor axis comprise a guide (4, 34) for guiding the anchoring pin, and means for locking the position of the anchor pin in the slide. Device according to one of claims 4 to 9 and 11 to 15, characterized in that the means for guiding the positioning pin are mounted on a turntable (45) about an axis substantially parallel to the width of the product. Device according to one of claims 1 to 17, characterized in that the actuating means comprise two actuating rods (2, 3), each actuating rod being connected on the one hand to a respective crankshaft (14, 15) and on the other hand to the support (42) of needle board (1) by an actuating axis (5, 6), the two crankshafts rotating in opposite directions from each other. Device according to Claim 18 when attached to one of Claims 4 to 9 and 11 to 17, characterized in that the axis of the positioning pin (49) coincides with one of the said actuating axes (5, 6). ). Device according to claim 18 or 19, characterized in that the two crankshafts are mutually out of phase. Device according to one of claims 18 to 20, characterized in that the mutual angular setting of the two crankshafts is adjustable. Device according to claim 21, characterized in that it comprises means for adjusting the phase difference comprising a differential (87) having an output shaft connected to a first (14) of the crankshafts, an input shaft connected to a motor output shaft (54) and an angularly adjustable element (72) for adjusting the phase shift of the first crankshaft relative to the second crankshaft (15). Needling process implemented in a device according to one of the preceding claims, comprising guiding a product in a direction of longitudinal advance in a plane defining a longitudinal direction and a width of the product, an actuation and guidance a carrier (42) for carrying a needle board (1) so that the needles (50) perform in the product (22) a successive striking movement having a main component transverse to the plane, characterized in that relative to the plane normal, an inclination of the main component about an axis substantially parallel to the width of the product is defined. Method according to Claim 23, characterized in that, in the context of the actuation and the guiding of the support (42), a positioning pin (49) connected to the support is guided in a predetermined path, and in that in order to define the inclination, the orientation of said predetermined path is defined. Method according to claim 23 or 24, characterized in that it further comprises adjusting the inclination of the main component. Method according to claim 24, characterized in that said path orientation is adjusted to adjust the inclination of said main component. Method according to one of claims 23 to 26, characterized in that the striking movement is a closed-loop movement, preferably substantially elliptical or ovoid. Method according to one of claims 23 to 26, characterized in that the striking movement is a substantially linear movement, preferably substantially rectilinear. Method according to one of claims 23 to 28, characterized in that the movement of the needles in the product comprises an insertion (40) of needles in the product with a speed substantially perpendicular to the longitudinal direction of the product. Method according to one of claims 23 to 28, characterized in that the movement of the needles in the product comprises an insertion (38) of the needles in the product with a speed having a component substantially parallel to the longitudinal direction of the product. Method according to one of claims 23 to 30, characterized in that the movement of the needles in the product comprises a withdrawal (39) of the needles out of the product with a speed substantially perpendicular to the longitudinal direction of the product. Method according to one of claims 23 to 30, characterized in that the movement of the needles in the product comprises a withdrawal (41) of the needles out of the product with a speed having a component substantially parallel to the longitudinal direction of the product.

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