EP2021539B1 - Dispositif pour aiguilleter une bande d'étoffe non tissée - Google Patents

Dispositif pour aiguilleter une bande d'étoffe non tissée Download PDF

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Publication number
EP2021539B1
EP2021539B1 EP07725103A EP07725103A EP2021539B1 EP 2021539 B1 EP2021539 B1 EP 2021539B1 EP 07725103 A EP07725103 A EP 07725103A EP 07725103 A EP07725103 A EP 07725103A EP 2021539 B1 EP2021539 B1 EP 2021539B1
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EP
European Patent Office
Prior art keywords
drive
horizontal
rocker
eccentric
bar carrier
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Expired - Fee Related
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EP07725103A
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German (de)
English (en)
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EP2021539A1 (fr
Inventor
Robert Strasser
Andreas Plump
Tilman Reutter
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Hi Tech Textile Holding GmbH
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Hi Tech Textile Holding GmbH
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Publication of EP2021539A1 publication Critical patent/EP2021539A1/fr
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    • D—TEXTILES; PAPER
    • D04—BRAIDING; LACE-MAKING; KNITTING; TRIMMINGS; NON-WOVEN FABRICS
    • D04H—MAKING TEXTILE FABRICS, e.g. FROM FIBRES OR FILAMENTARY MATERIAL; FABRICS MADE BY SUCH PROCESSES OR APPARATUS, e.g. FELTS, NON-WOVEN FABRICS; COTTON-WOOL; WADDING ; NON-WOVEN FABRICS FROM STAPLE FIBRES, FILAMENTS OR YARNS, BONDED WITH AT LEAST ONE WEB-LIKE MATERIAL DURING THEIR CONSOLIDATION
    • D04H18/00—Needling machines
    • D04H18/02—Needling machines with needles

Definitions

  • the invention relates to a device for needling a nonwoven web according to the preamble of claim 1.
  • the known device has a beam support, on the underside of which two adjacently arranged needle beams are held for receiving a multiplicity of needles.
  • the beam support is movably supported, with a vertical drive for oscillating movement of the beam support in an up and down motion and a horizontal drive for oscillating movement of the beam support in a rectilinear reciprocation.
  • the vertical drive has a plurality of eccentric shafts and a plurality of connecting rods guided by the eccentric shafts, which engage with their free ends on the beam carrier.
  • the horizontal drive has at least one horizontal link, which is connected at one end to the beam support and associated with an opposite end of an eccentric drive.
  • the known device has various possibilities to couple the horizontal link with the eccentric drive.
  • the horizontal link is coupled via a Kipphebelkinematik with a guided on an eccentric connecting rod.
  • the free end of the connecting rod is detachably connected to the Kipphebelkinematik, so that a vibration displacement is adjustable depending on the position of the point of the connecting rod on the rocker arm.
  • this allows an adjustment of the horizontal stroke to perform the beam support only with stationary eccentric drive.
  • the oscillating horizontal movement is introduced via two parallel eccentric drives on the horizontal link.
  • the parallel guided connecting rods are connected via a coupling member and a transmission kinematics with the horizontal lever, whereby a resulting depending on the phase angles of the eccentric shafts of the eccentric motion amplitude is generated.
  • This can indeed be an adjustment of the horizontal stroke change during operation, but only with a considerable expenditure on equipment, which leads to a large amount of space in the entire device in large systems.
  • at least two separate eccentric drives are required to perform only a horizontal reciprocating motion on the beam support.
  • the known device is thus based on mechanically very complex and partially in operation not adjustable drive means to perform superimposed to a vertical movement of the beam support in a straight-line back and forth movement.
  • the beam support is formed by a pivot tube which is pivoted back and forth relative to a pivot axis.
  • the beam carrier is pivoted about a pivot gear relative to the pivot axis.
  • the device and the swivel gear are therefore not suitable to perform a rectilinear back and forth movement of the beam support in the horizontal direction.
  • the US 3,830,174 relates to a machine for needling a fleece.
  • the needles are moved vertically in this machine by an eccentric drive via a special kinematics.
  • the transmission kinematics of the horizontal drive is formed by a rocker, which is held at one end by a frame pivot on a machine frame and at the opposite end has a double pivot, and that the rocker in the double swivel joint with the horizontal link and the eccentric drive is coupled.
  • the invention has the particular advantage that the horizontal link is coupled directly via a rotary joint with the eccentric drive, so that initially no further gear members are required for power transmission.
  • the caused by the eccentric deflection of the double pivot is determined by the rocker, which is fixed at its opposite end via a frame pivot in a position on the machine frame.
  • the horizontal stroke of the horizontal link which is established when the double pivot joint of the rocker is deflected is essentially determined by an angular position of the rocker relative to the horizontal link.
  • the frame pivot of the rocker is detachable and held so adjustable on the machine frame, that can be changed in a neutral position of the beam support between the rocker and the horizontal link set swing angle.
  • the relative position of the rocker to the horizontal link can thus be changed without interrupting the drive train.
  • the release and adjustment of the frame pivot of the rocker leads directly to a change in the horizontal link caused horizontal stroke, the rectilinear reciprocation of the beam support is continued by the constant connection of the eccentric drive to the hinge. Fine adjustments of the horizontal drive can thus be advantageously carried out during operation in particular at the beginning of the process in a simple manner.
  • the frame pivot of the rocker is held for adjustment to a guide device with a circular arc-shaped adjustment according to an advantageous embodiment of the invention.
  • the adjustment path represents the guideway of the frame pivot of the rocker in the event that the double pivot of the rocker held in the neutral position and the rocker is moved.
  • the articulation point of the horizontal link remains essentially unchanged at each stroke adjustment.
  • the design of the guide device as an adjusting lever which forms the frame pivot of the rocker at one end and is held with the opposite end pivotally and fixably on a pivot axis, has proven particularly useful.
  • To adjust the swing motion only the position of the adjustment lever is changed by pivoting about the pivot axis.
  • the change in position of the frame pivot of the rocker can be quickly and safely perform, and by marking the machine frame reproducible and very fine gradations of the swing adjustment are possible.
  • the horizontal link is arranged with its end in a central region of the beam support and connected by a hinge with the beam support.
  • the position of the horizontal link is suitable for perceiving a guide of the beam carrier in the longitudinal direction.
  • the horizontal link is arranged substantially parallel to a transverse side of the beam carrier and designed with such a stiffening shape, so that the beam carrier is guided in the longitudinal direction.
  • the device can be operated safely even with non-activated horizontal drive.
  • the beam support is driven only by the vertical drive to an up and down movement.
  • the development of the invention is preferably formed, in which the eccentric so engages the double pivot, that acting on the double pivot joint movement vector between the pivot on the beam support and the Frame pivot on the machine frame is directed.
  • eccentric shaft by a crankshaft in order, for example, to generate greater translatory movements by the eccentric drive.
  • a preferred embodiment of the invention provides that the horizontal link is connected via a coupling kinematics with the double pivot of the rocker. This gives the possibility to reduce the force acting on the horizontal drive force.
  • the axial guidance of the needle bar can be advantageously stabilized.
  • the coupling kinematics is formed of a connecting rod connected to the rocker and a rocker arm held on a rocker arm.
  • the push rod and the horizontal link preferably engage offset to one another on the rocker arm, so that the swinging motion is transmitted with a translation to the needle bar.
  • the rocker arm has a counterbalancing the needle bar at a free end balancing mass, characterized in that only a small force is required to move the needle bar horizontally.
  • the power reduction allows a lightweight construction of the horizontal drive, in which the hinges are designed for a corresponding low introduction of force.
  • the horizontal drive has a plurality of spaced apart horizontal link, which are distributed over the length of the beam support connected to the beam support and each synchronized by an associated rocker and an associated eccentric drive are driven, have the particular advantage that the beam support can be uniformly guided and moved over a greater length.
  • larger working widths for the treatment of nonwoven webs can be realized on the device.
  • the beam carrier is formed by a plurality of carrier modules and in which the carrier modules are guided by a plurality of drive modules of the horizontal drive.
  • Each of the drive modules has at least one of a plurality of horizontal links, one of a plurality of rockers and one of a plurality of eccentric drives.
  • the eccentric drives are driven synchronously by one or more eccentric shafts or crankshafts.
  • the formation of several carrier modules has the particular advantage that long and therefore bend-sensitive beam carriers can be avoided.
  • Fig. 1 and Fig. 2 a first embodiment of the inventive apparatus for needling a nonwoven web is shown.
  • the embodiment is in a side view and in Fig. 2 shown in a plan view.
  • Fig. 1 the embodiment is in a side view and in Fig. 2 shown in a plan view.
  • the embodiment of the device according to the invention Fig. 1 and Fig. 2 has a beam support 2, which holds a needle bar 1 on its underside.
  • the needle bar 1 holds on its underside a needle board 3 with a plurality of needles 4.
  • the needle board 3 with the needles 4 is associated with a tray 24, between the needle board 3 and the tray 24, a nonwoven web 25 is guided.
  • a vertical drive 6 and a horizontal drive 5 engages on the beam support 2, a vertical drive 6 and a horizontal drive 5 engages.
  • the vertical drive 6 the beam support 2 is oscillated in the vertical direction, so that the needle bar 1 with the needle board 3 performs an up and down movement.
  • the stroke of the vertical movement of the beam support 2 is selected such that the needles 4 held on the underside of the beam support 2 completely penetrate the nonwoven web 25 guided on the support 24.
  • the vertical drive 6 has a plurality of drive units 27.1 and 27.2, which act distributed over the length of the beam support 2 on the beam support 2.
  • the vertical drive 6 is formed by two drive units 27.1 and 27.2, wherein each drive unit is constructed identically.
  • Each drive unit 27.1 and 27.2 of the vertical drive 6 has two parallel adjacent connecting rods 7.1 and 7.2, which are connected at one end by a connecting pivot 9.1 and 9.2 with the beam support 2. With the opposite end of the connecting rods 7.1 and 7.2 are each held on a driven eccentric shaft 8.1 and 8.2.
  • the Eccentric shaft 8.1 forms with the connecting rod 7.1 and the eccentric shaft 8.2 with the connecting rod 7.2 each have an eccentric drive to guide the beam support 2 in an up and down movement.
  • the eccentric shafts 8.1 and 8.2 are driven synchronously, so that the beam support 2 is guided in parallel.
  • the horizontal drive 5 engages with two drive modules 23.1 and 23.2 synchronously to the beam support 2.
  • the drive modules 23.1 and 23.2 are each assigned to the transverse sides of the beam carrier 2.
  • each of the drive modules 23.1 and 23.2 is constructed identically, so that below the structure of the drive module 23.1 will be explained.
  • the horizontal drive 5 is connected via a horizontal link 10 with the beam support 2.
  • a free end of the horizontal link 10 via a hinge 15 in the central region of the beam support 2 is arranged.
  • the opposite end of the horizontal link 10 is coupled via a transmission kinematics 11 with an eccentric 12.
  • the horizontal link 10 is oriented horizontally, wherein the rotary joint 15 is guided on the beam support 2 on a horizontal straight line.
  • the articulation of the beam carrier 2 therefore always takes place from the same point.
  • the transmission kinematics 11 has a rocker 13 which is connected via a double pivot 14 with the horizontal link 10 and the eccentric 12.
  • the eccentric drive 12 has a connecting rod 17, which is arranged with one end on the double swivel joint 14 and is guided on an eccentric shaft 18 at the opposite end.
  • the eccentric shaft 18 is driven by a drive, not shown here.
  • the rocker 13 is held with its opposite end via a frame pivot 16 on a machine frame 21.
  • the frame pivot 16 is held in a guide device 20 which has a circular arc-shaped adjustment path 19 in which the frame pivot 16 of the rocker 13 is guided and fixable.
  • the guide device 20 has for this purpose a locking means on, through which the frame pivot 16 can be held in any position within the adjustment path 19.
  • the beam support 2 is in a neutral, undeflected position.
  • a swing angle ⁇ is formed between the horizontal link 10 and the rocker 13. Due to the relative position in the rocker 13, the deflection movement introduced by the connecting rod 17 and the eccentric shaft 18 on the double swivel joint 14 is converted into a specific amplitude of movement of the horizontal link 10.
  • the horizontal link 10 guides the beam carrier 2 horizontally back and forth within a predefined stroke.
  • the motion vector of the eccentric 12 in the Fig. 1 indicated by an arrow directed between the pivot 15 on the beam support 2 and the frame pivot 16 on the machine frame 21, so that a thrust force is introduced via the connecting rod 17 for the deflection of the horizontal link 10 and thus of the beam support 2.
  • the frame pivot 16 of the rocker 13 is dissolved in the guide device 20 and adjusted within the adjustment path 19.
  • the swing angle ⁇ forming in the neutral position can both be reduced or increased in order to obtain a corresponding stroke change.
  • a smaller swing angle ⁇ on the rocker 13 would be set.
  • For a smaller stroke in the horizontal direction of the swing angle ⁇ would be increased.
  • the adjustment of the relative position of the frame pivot 16 can be performed individually for each drive model 23.1 and 23.2. Depending on the constructive design of the guide device 20, however, common adjustments of the two frame joints are possible.
  • the adjustment path 19 of the guide device 20 is formed in this embodiment as a circular arc-shaped path that adjusts to guide the rocker arm 13 about the held in the neutral position double pivot 14. This maintains a substantially horizontal orientation of the horizontal link 10 over the entire adjustment range of the rocker 13.
  • the horizontal link 10 is thus particularly suitable for carrying out the guidance of the beam carrier 2 in the longitudinal direction.
  • the horizontal link 10 has a stiffening shape, which is represented by a stiffening rib 22 in this embodiment.
  • the beam support 2 is axially guided by the respective arranged on the transverse sides of the beam support 2 horizontal beam 10 of the drive modules 23.1 and 23.2, so that in extreme cases, the beam support 2 could be safely operated even without activation of the horizontal drive 5.
  • the vertical drive 6 and the horizontal drive 5 are synchronously driven for needling the nonwoven web 25, wherein the downward movement of the beam support 2 is combined with a feed motion, so that the needles 4 can perform within the nonwoven web 25 directed in the direction of the nonwoven web 25 movement.
  • a needle bar 1 is held on the beam support 2.
  • the vertical drive 6 and the horizontal drive 5 may comprise a plurality of drive units and drive modules to guide the beam support.
  • Fig. 3 an embodiment is shown in which the beam support 2 is formed by a plurality of juxtaposed support modules.
  • four support modules 26.1 to 26.4 are shown in a plan view to guide one or more needle bars.
  • For oscillating up and down movement and for oscillating reciprocating motion of the vertical drive 6 and the horizontal drive 7 are formed by a plurality of drive units and drive modules.
  • two drive units of the vertical drive 6 and two drive modules of the horizontal drive 5 are assigned as an example to the carrier module 26.1 and 26.2.
  • the carrier modules 26.3 and 26.4 are assigned a total of three drive units of the vertical drive 6 and the drive modules 23.5, 23.6 and 23.7 of the horizontal drive 5.
  • the drive units 27.1 to 27.7 and drive modules 23.1 to 23.7 are controlled so as to be able to drive the carrier modules 26.1 to 26.4 synchronously.
  • the number of carrier modules and the number of drive units as well as the drive modules can be varied according to bar length, weight, stroke and speed in order to obtain optimized usage.
  • the drive units 27.1 to 27.7 of the vertical drive 6 are identical according to the embodiment according to Fig. 1 built up. Likewise, the drive modules 23.1 to 23.7 have an identical structure as previously to the embodiment according to Fig. 1 was explained.
  • Fig. 4 is a further embodiment of the device according to the invention shown schematically in a side view.
  • all components and assemblies have the same function identical reference numerals.
  • two needle bars 1.1 and 1.2 are held next to one another on an underside of a beam carrier 2.
  • Each of the needle bars 1.1 and 1.2 has in each case a needle board 3 with the needles 4.
  • the needle bars 1.1 and 1.2 are associated with a tray, not shown here, on which a nonwoven web is guided.
  • a vertical drive 6 and a horizontal drive 5 engages on the beam support 2.
  • the horizontal drive 5 is connected via a coupling kinematics 35 with the beam support 2.
  • the transmission kinematics 11 is thus supplemented by the coupling kinematics 35 in order to form the connection between an eccentric drive 12 and a horizontal trailing arm 10.
  • the vertical drive 6 is designed substantially identical to the aforementioned embodiment, so that only the differences will be explained at this point.
  • the vertical drive 6 is formed by two drive units 27.1 and 27.2, each having a connecting rod 7.1 and 7.2 and a crankshaft 36.1 and 36.2.
  • the crankshafts 36.1 and 36.2 are shown schematically as a rotatable crank.
  • the crankshafts 36.1 and 36.2 are each connected to one of the connecting rods 7.1 and 7.2.
  • the connecting rods 7.1 and 7.2 are connected via the pivot hinges 9.1 and 9.2 with the beam support 2.
  • a horizontal link 10 engages via a rotary joint 15 on the beam support 2.
  • a coupling kinematics 35 is provided to connect the horizontal drive 5 with the horizontal link 10.
  • the coupling kinematics 35 consists in this embodiment a rocker arm 30 which is pivotally mounted on a pivot bearing 32.
  • the rocker arm 30 has a balancing mass 34 at a free end below the pivot bearing 32.
  • the horizontal link 10 and a push rod 31 are each connected via the pivot joints 33.1 and 33.2 with the tilt lever 30.
  • the rotary joint 33.1 which connects the rocker arm 30 with the push rod 31, is in this case formed at the free end of the rocker arm 30 above the pivot bearing 32.
  • the horizontal link 10 engages offset to the push rod 31 in a region of the rocker arm 30 between the pivot 33.1 and the pivot bearing 32.
  • the push rod 31 is connected at its opposite end on the double pivot 14 with the rocker 13 of the lifting drive 5.
  • the linear actuator 5 is constructed substantially identical to the previous embodiment, so that only the differences will be explained at this point.
  • the rocker 13 is arranged with the frame pivot 16 at a free end of an adjusting lever 28.
  • the adjusting lever 28 in this case forms the guide device 20 in order to fix the position of the frame pivot 16 on the machine frame.
  • the adjusting lever 28 is held for this purpose with the opposite end to a pivot axis 29, in which the adjusting lever 28 is pivotable and fixable. By adjusting the adjusting lever 28 thus the frame pivot 16 can be adjusted on a circular adjustment path 19.
  • the rocker 13 is connected in the double pivot 14 with the connecting rod 17, which is connected at its free end by a crankshaft 36.3.
  • the crankshaft 36.3 in this case forms the eccentric drive 12 in order to drive the connecting rod 17 to move the rocker 13.
  • the crankshaft 36.3 is in Fig. 4 shown schematically as a rotatably mounted crank.
  • the swinging motion of the rocker 13 is generated by the crankshaft 36.3 and the connecting rod 17.
  • the amplitude of the rocker movement of the rocker 13 is determined by the Location of the frame pivot 14 on the machine frame determined.
  • the movement of the rocker 13 is transmitted via the push rod 31 to the rocker arm 30.
  • the rocker arm 30 is pivoted about the pivot bearing 32, so that the engaging in the central region of the rocker arm 30 horizontal link 10 of the tilting movement of the rocker arm 30 follows. Due to the staggered arrangement of the hinges 33.1 and 33.2 of the push rod 31 and the horizontal link 10, the stroke generated by the horizontal drive 5 is transmitted with a translation to the beam support 2 out. In relation to the lifting drive 5, the beam carrier 2 thus performs a changed by a gear ratio - in this case - smaller stroke movement.
  • the compensating mass 34 formed at the free lower end of the rocker arm 30 counteracts the mass of the beam support 2 during pivoting of the rocker arm 30, so that weight compensation in the horizontal direction is achieved.
  • the weight compensation causes a relatively small force on the push rod 31 at the free end of the rocker arm 30 must be introduced to move the beam support 2 back and forth.
  • the force introduced into the horizontal drive 5 force can be reduced to a minimum, so that corresponding lightweight construction and compact arrangements are possible.
  • FIG. 4 illustrated embodiment of the device according to the invention represents only another possible variant to connect the horizontal drive 5 via a coupling kinematics 35 with the horizontal link 10.
  • the hinges 33.1 and 33.2 are merged, so that the push rod 31 is coupled directly to the horizontal link 10.
  • the oscillatory movement of the push rod 31 would be transmitted without translation directly to the horizontal link 10.
  • a mass balance in the horizontal direction is realized by the balancing mass 34 on the rocker arm 30 substantially.
  • it is particularly advantageous training with translated stroke transmission so that due to the power reduction several beam support can be driven by a linear actuator.
  • a further embodiment of a device according to the invention is shown schematically in a side view.
  • the vertical drive 6, the horizontal drive 5 and the coupling kinematics 35 for moving the beam support 2 are substantially identical to the aforementioned embodiment according to Fig. 4 executed. In that regard, reference is made to the above description and explained below only the differences.
  • the horizontal drive 5 is shown in an arrangement in which the push rod 31 of the coupling kinematics 35 is moved opposite to the horizontal link 10.
  • the horizontal drive in Fig. 5 designed mirror-symmetrical, so that the swinging motion is executed facing away from the beam support 9. This makes it possible to achieve a very compact design, since the rocker 13 and the connecting rod 17 are inwardly and thus can be set as close as possible to the vertical drive 6.
  • the coupling kinematics 35 is arranged on the right side of the machine and allows a very long formation of the horizontal link 10.
  • the horizontal link 10 is in this case connected at one end via the pivot 33.2 with a free end of the rocker arm 30 below the pivot bearing 32.
  • the rocker arm 30 is held on the pivot bearing 32, wherein the rocker arm 30 has a relatively short lower lever arm and a much larger lever arm above the pivot bearing 32.
  • the push rod 31 is connected by the pivot 33.1 with the rocker arm 30.
  • the rocker arm 30 carries at the free end of the balancing mass 34. By this configuration acts the Push rod 31 in addition mass balancing the horizontal movement of the beam support. 2
  • the transmission kinematics 11 can be arranged in a particularly compact design next to the beam support 2.
  • the device according to the invention is particularly suitable for carrying out mechanical needling of nonwoven webs with high production output and high production speeds.
  • a high uniform Vemadelungs23 is achieved in the structuring of nonwovens.
  • a very compact design with low space requirements is created.
  • the simple gear kinematics for controlling the horizontal link and the stiffening shape of the horizontal link for axial guidance of the beam support allow a structural design with few parts and low weights.
  • very high frequencies of movement to be performed on the beam support 2 since the compact design allows a rigid structure of the machine frame.
  • the vertical drive and the horizontal drive can be operated synchronously or asynchronously to move the beam carrier.
  • the eccentric drive can be driven with any phase tests, so that a flexibility in the motion control of the beam carrier is given.
  • To initiate the drive movement both eccentric shafts and crankshafts can be used.

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  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Nonwoven Fabrics (AREA)
  • Transmission Devices (AREA)

Abstract

L'invention concerne un dispositif pour aiguilleter une bande d'étoffe non tissée comprenant au moins une barre d'aiguilles. La barre d'aiguilles, qui présente sur son côté inférieur un lit d'aiguilles avec une pluralité d'aiguilles, est maintenue par un support de barre qui est guidé au moyen d'un entraînement vertical de manière à être animé d'un mouvement d'oscillation au cours de son déplacement de haut en bas, et de manière à être animé d'un mouvement d'oscillation par un entrainement horizontal au cours de son déplacement de va et vient. On utilise comme entraînement vertical au moins deux arbres excentrés entraînés et plusieurs tiges de bielles associées aux arbres excentrés, qui sont accouplés au support de barre par leurs extrémités libres. L'entraînement horizontal présente au moins un bras oscillant horizontal, qui est connecté au support de barre par l'une de ses extrémités et qui est accouplé par une extrémité opposée à une cinématique de transmission qui présente un entraînement excentré. Afin de réaliser une construction aussi simple et économique que possible de l'entraînement horizontal, la cinématique de transmission est formée, selon l'invention, par une bielle oscillante qui est maintenue sur un bâti de la machine par une extrémité par une articulation pivotante du bâti, qui présente à l'extrémité opposée une double articulation pivotante et qui est accouplée au niveau de la double articulation pivotante au bras oscillant horizontal et à l'entraînement excentré.

Claims (17)

  1. Dispositif pour aiguilleter une bande d'étoffe non tissée (25), comprenant au moins une barre d'aiguilles (1) qui présente sur son côté inférieur une plaque à aiguilles (3) avec une pluralité d'aiguilles (4), un support de barre (2) maintenu mobile pour retenir la barre d'aiguilles (1), un entraînement vertical (6) raccordé au support de barre (2) pour produire un mouvement oscillant du support de barre (2) dans un mouvement de haut en bas, et un entraînement horizontal (5) raccordé au support de barre (2) pour produire un mouvement oscillant du support de barre (2) dans un mouvement d'avant en arrière, l'entraînement vertical (6) présentant au moins deux arbres excentriques entraînés (8.1, 8.2) et plusieurs bielles motrices (7.1, 7.2) associées aux arbres excentriques (8.1, 8.2), dont les extrémités libres sont raccordées au support de barre (2), et l'entraînement horizontal (5) présentant au moins un bras horizontal (10), qui est raccordé par une extrémité au support de barre (2) et par une extrémité opposée à une cinématique de transmission (11), et un entraînement excentrique (12) accouplé à la cinématique de transmission (11), caractérisé en ce que la cinématique de transmission (11) est formée par une bielle oscillante (13) qui est maintenue par une extrémité par une articulation tournante de bâti (16) sur un bâti de machine (21) et qui présente à l'extrémité opposée une articulation tournante double (14), et en ce que la bielle oscillante (13) est accouplée dans l'articulation tournante double (14) au bras horizontal (10) et à l'entraînement excentrique (12).
  2. Dispositif selon la revendication 1, caractérisé en ce que l'articulation tournante de bâti (16) de la bielle oscillante (13) est maintenue de manière amovible et réglable sur le bâti de machine (21) de telle sorte que dans une position neutre du support de barre (2), un angle de bielle oscillante (α) formé entre la bielle oscillante (13) et le bras horizontal (10) puisse être modifié.
  3. Dispositif selon la revendication 2, caractérisé en ce que l'articulation tournante de bâti (16) de la bielle oscillante (13) est maintenue en vue du réglage au niveau d'un dispositif de guidage (20) avec une trajectoire de réglage (19) en forme d'arc de cercle, qui s'ajuste lors d'une rotation de la bielle oscillante (13) autour de l'articulation tournante double (14) maintenue dans la position neutre à l'extrémité de la bielle oscillante (13).
  4. Dispositif selon la revendication 3, caractérisé en ce que le dispositif de guidage (20) est formé par un levier de réglage (28) qui porte à une extrémité l'articulation tournante de bâti (16) de la bielle oscillante (13) et qui peut être fixé en position et est maintenu à rotation à son autre extrémité sur un axe de pivotement (29).
  5. Dispositif selon l'une quelconque des revendications 1 à 4, caractérisé en ce que le bras horizontal (10) est connecté avec son extrémité au support de barre (2) dans une région centrale du support de barre (2) par une articulation tournante (15).
  6. Dispositif selon la revendication 5, caractérisé en ce que le bras horizontal (10) s'étend essentiellement parallèlement à un côté transversal du support de barre (2) et présente une forme rigidifiante (22) pour le guidage du support de barre (2) dans la direction longitudinale.
  7. Dispositif selon l'une quelconque des revendications 1 à 6, caractérisé en ce que l'entraînement excentrique (12) vient en prise avec l'articulation tournante double (14) de telle sorte qu'un vecteur de déplacement agissant sur l'articulation tournante double (14) soit orienté entre l'articulation tournante (15) sur le support de barre (2) et l'articulation tournante de bâti (16) sur le bâti de machine (21).
  8. Dispositif selon la revendication 7, caractérisé en ce que l'entraînement excentrique (12) est formé par un arbre excentrique (18) entraîné et une bielle motrice (17) connectée à l'arbre excentrique (18), l'extrémité libre de la bielle motrice (17) étant maintenue sur l'articulation tournante double (14).
  9. Dispositif selon la revendication 8, caractérisé en ce que l'arbre excentrique (18) est réalisé sous forme de manivelle (36.3).
  10. Dispositif selon l'une quelconque des revendications 1 à 9, caractérisé en ce que le bras horizontal (10) est raccordé par le biais d'une cinématique de couplage (35) à l'articulation tournante double (14) de la bielle oscillante (13).
  11. Dispositif selon la revendication 10, caractérisé en ce que la cinématique de couplage (35) est formée par un levier oscillant (30) maintenu par le biais d'un palier pivotant (32) sur le bâti de machine (21) et par une tringle de poussée (31), la tringle de poussée (31) étant accouplée par une extrémité à l'articulation tournante double (14) de la bielle oscillante (13) et par l'autre extrémité au levier oscillant (30), et le bras horizontal (10) étant accouplé au levier oscillant (30).
  12. Dispositif selon la revendication 11, caractérisé en ce que la tringle de poussée (31) et le bras horizontal (10) sont raccordés de manière décalée l'un de l'autre au levier oscillant (30) par le biais d'articulations tournantes (33.1, 33.2).
  13. Dispositif selon la revendication 11 ou 12, caractérisé en ce que le levier oscillant (30) présente, à une extrémité libre, une masse d'équilibrage (34) agissant en face de la barre d'aiguilles (1).
  14. Dispositif selon l'une quelconque des revendications 1 à 13, caractérisé en ce que l'entraînement horizontal (5) présente plusieurs bras horizontaux (10) disposés à distance les uns des autres qui sont raccordés au support de barre (2) de manière répartie sur la longueur du support de barre (2), et qui sont entraînés à chaque fois de manière synchrone par une bielle oscillante (13) associée et un entraînement excentrique (12).
  15. Dispositif selon l'une quelconque des revendications 1 à 13, caractérisé en ce que le support de barre (2) est formé par plusieurs modules de support (26.1 - 26.4), lesquels modules de support (26.1 26.4) sont guidés ensemble par plusieurs modules d'entraînement (23.1 - 23.7) de l'entraînement horizontal (5), chaque module d'entraînement (23.1 - 23.7) comprenant au moins un parmi plusieurs bras horizontaux (10), une parmi plusieurs bielles oscillantes (13) et un parmi plusieurs entraînements excentriques (12).
  16. Dispositif selon la revendication 15, caractérisé en ce que les modules d'entraînement (23.1 - 23.2) sont réalisés de manière à pouvoir être entraînés de manière synchrone.
  17. Dispositif selon l'une quelconque des revendications 1 à 16, caractérisé en ce que les arbres excentriques (8.1, 8.2) de l'entraînement vertical (6) sont réalisés à chaque fois sous forme de manivelles (36.1, 36.2).
EP07725103A 2006-05-20 2007-05-11 Dispositif pour aiguilleter une bande d'étoffe non tissée Expired - Fee Related EP2021539B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006023762 2006-05-20
PCT/EP2007/004183 WO2007134731A1 (fr) 2006-05-20 2007-05-11 Dispositif pour aiguilleter une bande d'étoffe non tissée

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EP2021539A1 EP2021539A1 (fr) 2009-02-11
EP2021539B1 true EP2021539B1 (fr) 2012-06-13

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EP (1) EP2021539B1 (fr)
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WO (1) WO2007134731A1 (fr)

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EP2158348B1 (fr) * 2007-06-15 2010-12-01 Oerlikon Textile GmbH & Co. KG Dispositif d'aiguilletage d'une bande de non-tissé
US8156618B2 (en) * 2007-08-04 2012-04-17 Tilman Reutter Device for needling a fibrous web
DE102007041040B4 (de) * 2007-08-29 2009-07-09 ERKO Trützschler GmbH Nadelmaschine mit Nadelbalkenführung
EP2201164B1 (fr) * 2007-10-18 2012-04-18 Hi Tech Textile Holding GmbH Dispositif d'aiguilletage d'une nappe de fibres
CN101960065B (zh) * 2008-03-03 2012-03-14 欧瑞康纺织有限及两合公司 用于对纤维网进行针刺的设备
CN101981243A (zh) * 2008-04-17 2011-02-23 欧瑞康纺织有限及两合公司 用于对纤维网进行针刺的设备
EP2287377B1 (fr) * 2009-08-14 2011-10-26 Oskar Dilo Maschinenfabrik KG Dispositif d'entraînement et de guidage dans une machine à tricoter
CN102597351B (zh) * 2009-09-09 2015-04-29 恒天(奥地利)控股有限公司 用于针刺纤维幅的装置
IT1403176B1 (it) 2010-12-01 2013-10-04 Texnology S R L Dispositivo di cucitura.
EP2886694B1 (fr) * 2013-12-17 2016-09-07 Oskar Dilo Maschinenfabrik KG Procédé d'entraînement d'une planche à aiguilles dans une aiguilleteuse
CN104164755A (zh) * 2014-09-26 2014-11-26 绍兴励达无纺布有限公司 一种异步针刺机
EP3372716B1 (fr) * 2017-03-09 2019-09-04 Oskar Dilo Maschinenfabrik KG Aiguilleteuse
CN106958080B (zh) * 2017-06-02 2019-04-19 威海市和谐汽车内饰有限公司 针刺机
CN106988024B (zh) * 2017-06-02 2019-03-12 上海盈兹无纺布有限公司 针刺机
EP3412819B1 (fr) * 2017-06-08 2019-12-25 Oskar Dilo Maschinenfabrik KG Aiguilleteuse
CN107090665B (zh) * 2017-07-10 2019-05-31 上海名冠净化材料股份有限公司 用于制备针刺无纺布的装置
FR3109587B1 (fr) 2020-04-23 2022-05-20 Andritz Asselin Thibeau Dispositif de commande du mouvement des aiguilles d’une aiguilleteuse, notamment elliptique, et aiguilleteuse comportant un tel dispositif
CN115717298B (zh) * 2022-10-26 2023-11-14 扬州荣恒机械制造有限公司 一种针刺机

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Publication number Publication date
US7614127B2 (en) 2009-11-10
US20090119894A1 (en) 2009-05-14
EP2021539A1 (fr) 2009-02-11
TW200806839A (en) 2008-02-01
WO2007134731A1 (fr) 2007-11-29

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