Classifications

• • 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 is used for solidification and structuring of nonwovens.
• a nonwoven web is pierced with a large number of needles, which are guided in an oscillating up and down movement.
• the needles are thus guided with an oscillating vertical movement in order to solidify the fiber material in the nonwoven web.
• the nonwoven web is continuously advanced with a feed, which is preferably carried out by rolling. Since the needles are not smooth but are provided with barbs that are open in the puncture direction, filaments of the fleece are caught during insertion and reoriented in the fleece. This produces the desired felting and consolidation effect in the web.
• the needles are guided with a superimposed horizontal movement.
• the movement of the needles in the feed direction of the nonwoven web is aligned.
• two different drive variants are known in the prior art.
• a generic device for needling a nonwoven web in which a needle bar with a vertical drive for performing an up and down movement and with a horizontal drive for performing a reciprocating motion is connected.
• the horizontal drive is formed by two oppositely driven eccentric drives, which consist of two connecting rods arranged parallel to each other and with the connecting rods.
• gene coupled crankshafts are formed.
• the phase angles of the crankshafts are mutually adjustable, so that the transmitted by the connecting rods on a coupling member horizontal stroke is adjustable in size. From the coupling member, the horizontal movement is transmitted directly to a beam carrier or by an intermediate coupling gear.
• the horizontal drive is formed by an eccentric drive, which has a cooperating with a crankshaft connecting rod.
• the connecting rod acts with its connecting rod eye directly on a beam support on the underside of a needle bar is held.
• Such devices allow higher throughput speeds of the nonwoven web, but have the great disadvantage that the horizontal stroke is not variably adjustable.
• a further device for needling a nonwoven web in which the beam support is formed by a guided in a pivot tube bumper.
• the pivot tube 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 for driving the needle board or boards parallel to the nonwoven web.
• connecting rods are coupled with their connecting rods in an inclined position with the horizontal link, wherein the connecting rods form an angle with their central axes.
• the invention has the particular advantage that the power transmission of the two eccentric drives of the horizontal drive is limited spatially to a very narrow compact attack area and thus leads to a stable guidance of the drive movement of the two eccentric drives.
• the invention is achieved by the proviso that a horizontal drive, which generates a vertical movement component in addition to the horizontal movement component, is completely unsuitable for a horizontal drive of the beam support.
• the vertical movement of the needles guided on the needle bar is effected exclusively by the vertical drive, so that the horizontal drive can be moved to a purely horizontal movement. has witnessed to compensate for the advancing movement of the nonwoven web. In that regard, a triggered by the horizontal drive vertical motion component is to be avoided.
• the invention has recognized that the combination of the rods held in an inclined position with the horizontal link can be advantageously used to transmit only the horizontally directed forces on the beam support.
• the motion component generated via the eccentric drives in the vertical direction is intercepted via the horizontal link and not transmitted to the beam carrier.
• the high flexibility of the stroke settings caused by the two eccentric drives can advantageously be combined with a stability and rigidity of the force transmission.
• An improved stability of the horizontal drive can be achieved in particular by the development of the invention, in which the connecting rods of the connecting rods are coupled by a double swivel joint with the horizontal link.
• the force intervention can focus on a coupling point, which is performed together on the eccentric drives.
• the double swivel joint is always guided by the eccentric drives on an ellipse-like path whose width and height depends on the phase angle of the two eccentric drives. As an extreme case, this results in either approximately a vertical or exactly one horizontal straight line for maximum or minimum horizontal stroke.
• the double swivel joint for connecting the connecting rods can be formed either directly at one end of the horizontal link or advantageously on a coupling link of a coupling kinematics connected to the horizontal link.
• the hinges are preferably formed in close proximity or slightly offset from each other directly at one end of the horizontal link.
• the coupling kinematics is formed from a coupling member connected to the eccentric and a rocker arm held on a pivot bearing.
• the coupling element as a push rod and the horizontal link preferably engage each other offset from one another on the tilting lever, so that the eccentric movements are transmitted with a translation onto the needle bar.
• the oblique position of the connecting rods is chosen such that the angle between the center axes of the connecting rods is ⁇ 180 °. This arrangement can be realized, which represent a compromise between favorable motion and favorable power ratios at the connecting rods.
• crankshaft of the eccentric drives are driven in opposite directions, the phase angles of the two crankshafts are designed to adjust a stroke independently adjustable.
• the crankshafts are assigned separate servo motors, by which the phase angle of the crankshaft is adjustable.
• the servomotors can be controlled via a common control device according to the desired stroke settings.
• the horizontal link is arranged with its end in a central region of the beam support and connected by a hinge to the beam support.
• the position of the horizontal link is suitable for making a guide of the beam carrier in the longitudinal direction of the beam.
• the horizontal link is arranged essentially parallel to a transverse side of the beam carrier and designed with a shaping of this kind, 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 carrier would only be driven by the vertical drive to move up and down.
• the needles are driven in the vertical direction preferably according to the embodiment of the invention with a vertical drive, which is formed by two eccentric drives, each having a crankshaft and a connected via a connecting rod to the crankshaft connecting rod.
• the connecting rods are connected with their connecting rod eyes via swivel joints with the beam support.
• FIG. 1 shows schematically a side view of a first embodiment of the device according to the invention
• FIG. 2 shows schematically a side view of a further embodiment of the device according to the invention
• 3 shows schematically a side view of a further embodiment of the device according to the invention
• Fig. 4 and Fig. 5 schematically further embodiments of a horizontal drive for the embodiments of Figures 1, 2 and 3.
• FIG. 6 shows schematically a side view of a further embodiment of the device according to the invention.
• FIG. 1 a first embodiment of the inventive device for needling a nonwoven web is shown.
• the embodiment of the device according to the invention according to FIG. 1 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 23 and a wiper 28, wherein between the tray 23 and the wiper 28, a nonwoven web 24 with substantially constant Feed rate is performed.
• the direction of movement of the nonwoven web 24 is characterized by an arrow.
• a vertical drive 12 and a horizontal drive 5 engages.
• the vertical drive 12 is formed by two parallel eccentric drives 12.1 and 12.2.
• the eccentric 12.1 and 12.2 have two parallel juxtaposed crankshafts 25.1 and 25.2, which are arranged above the beam carrier 2.
• the crankshafts 25.1 and 25.2 each have at least one eccentric section for receiving at least one connecting rod.
• connecting rods 13.1 and 13.2 are shown, which are held with their Pleuelköpfen to the crankshafts 25.1 and 25.2.
• the connecting rods 13.1 and 13.2 are connected with their free ends by the pivot hinges 14.1 and 14.2 with the beam support 2.
• the crankshaft 25.1 forms with the connecting rod 13.1 and the crankshaft 25.2 with the connecting rod 13.2 each have an eccentric drive to guide the beam support 2 in an up and down movement.
• the crankshafts 25.1 and 25.2 are driven synchronously or in opposite directions synchronously so that the beam support 2 is guided at least approximately parallel.
• the horizontal drive 5 engages with two eccentric drives 5.1 and 5.2 on the beam support 2.
• the horizontal drive 5 is connected via a horizontal link 15 with the beam support 2.
• a free end of the horizontal link 15 is arranged via a rotary joint 16 in the middle region of the beam support 2.
• the opposite end of the horizontal link 15 is connected via a double pivot 10 with the eccentric 5.1 and 5.2.
• the eccentric drives 5.1 and 5.2 are formed by two mutually parallel crankshafts 6.1 and 6.2.
• the crankshafts 6.1 and 6.2 each have at least one eccentric section in order to drive at least one connecting rod in each case.
• the connecting rod 7.1 is coupled with its connecting rod 8.1 on the crankshaft 6.1.
• the connecting rod 7.2 is connected with its connecting rod 8.2 at the crankshaft 6.2 arranged at a distance.
• the connecting rods 7.1 and 7.2 are directed in an inclined position to each other, so that the connecting rod 9.1 of the Connecting rod 7.1 and the connecting rod eye 9.2 of the connecting rod 7.2 are connected together by the double pivot 10 with the horizontal link 15.
• the double pivot joint 10 thus forms a common coupling point for transmitting power to the two eccentric drives 5.1 and 5.2.
• the rotary joint 10 is located at the intersection of the center axes of the connecting rods 7.1 and 7.2, so that an angle is established between the center axes of the connecting rods 7.1 and 7.2.
• the angle between the connecting rods 7.1 and 7.2 is indicated in Fig.
• the angle ⁇ is essentially dependent on the position of the crankshafts 6.1 and 6.2 and is preferably carried out in a value ⁇ 180 ° in order to obtain a sufficient horizontal deflection at the common coupling point with maximum stroke adjustment of the eccentric drives 5.1 and 5.2.
• the angle ⁇ and thus the arrangement of the connecting rods to each other chosen so that a compromise between favorable motion and favorable power ratios is achieved at the connecting rods.
• the eccentric drives 5.1 and 5.2 are driven synchronously in opposite directions.
• the double swivel joint 10 is guided as a common coupling point of the two connecting rods 7.1 and 7.2 on an elliptical path.
• the horizontal component of the movement is transmitted via the horizontal link 15 and the pivot 16 directly to the beam support 2.
• the vertical component of the movement generated by the eccentric drives 5.1 and 5.2 leads to the horizontal link 15 only to a rotational movement about the pivot 16.
• the vertical movements generated by the horizontal drive 5 remain in the double pivot 10 substantially without effect on the beam support 2 through
• the horizontal link 15 can be transmitted via the pivot 16 only horizontally directed forces that lead to a corresponding horizontal movement of the beam support 2.
• the crankshafts 6.1 and 6.2 can be driven together by a drive or separately via separate drives. To increase the lift of the horizontal To adjust len movement of the beam carrier, the phase angles of the crankshafts 6.1 and 6.2 are adjusted to each other. The phase position and thus the desired horizontal stroke of the crankshaft take place in this embodiment by two servo motors 26.1 and 26.2, which are shown schematically in Fig. 1.
• the servomotors 26.1 and 26.2 are associated with the crankshafts 6.1 and 6.2 and connected in a common control device 27. By means of the control device 27, it is therefore possible to set any desired combinations of phase positions between the crankshafts 6.1 and 6.2.
• the double pivot 10 is guided as a common coupling point while on an elliptical-like guideway whose width and height depends on the phase angle of the two crankshafts. As an extreme case, this results in either approximately a vertical or exactly one horizontal guideway for maximum or minimum horizontal stroke.
• the beam support 2 is located in the horizontal position to the left of the neutral position and in the vertical direction in an upper intermediate position.
• the beam support 2 is reciprocated horizontally with the beam support 1 with a predefined stroke.
• the horizontal movement takes place in the nonwoven web 24 in the feed direction of the nonwoven web 24, so that essentially no deformations and no relative movements occur between the needles 4 and the nonwoven web 24.
• the horizontal link 15 causes at the same time a relation to the vertical drive 12 effective guidance of the beam support 2, in particular in the beam longitudinal direction.
• the horizontal link 15 is formed in a stiffening shape, which is represented by a stiffening rib 17 in this embodiment.
• the beam support 2 is guided by the arranged on the transverse sides of the beam support 2 horizontal link 15, so that the beam support 2 could be operated safely even without activation of the horizontal drive 5.
• the vertical drive 12 and the horizontal drive 5 are synchronously driven for needling of the nonwoven web 24, whereby the downward movement of the beam carrier 2 is controlled by a feed movement. movement is combined, so that the needles 4 within the nonwoven web 24 can perform a directed in the direction of the nonwoven web 24 movement.
• a needle bar 1 is held on the beam support 2.
• a beam support 2 is guided by at least one vertical drive 12.
• a majority of these units usually occurs, although not every beam support must also be guided by at least one horizontal drive.
• several beam carriers could be connected to a needle bar, so that only a horizontal drive unit would lead from a needle bar and several Balkenträgren in a machine.
• FIG. 2 a further embodiment of the inventive device is shown schematically in a side view.
• the embodiment of FIG. 2 is substantially identical to the embodiment of FIG. 1, so that at this point only the differences will be explained and otherwise reference is made to the above description.
• two needle bars 1.1 and 1.2 are held on the beam support 2, each carrying a needle board 3 and a plurality of needles 4 on their undersides.
• the beam carrier 2 is coupled to a vertical drive 12, which is identical to the aforementioned embodiment.
• For horizontal movement of the beam support 2 of the beam support 2 is coupled via a central pivot 16 with a horizontal link 15.
• the swivel joint 16 is arranged substantially with the Pleuelgelenken 14.1 and 14.2 at a common height on the beam support 2, so that the arranged to the transverse sides of the beam support 2 horizontal link 15 allow aligned to the power instructions on the beam support 2 leadership.
• a horizontal drive 5 is provided, which are formed by the eccentric drives 5.1 and 5.2.
• the eccentric drives 5.1 and 5.2 each have a crankshaft 6.1 and 6.2 which, contrary to the previous exemplary embodiment, are arranged above the beam support 2.
• the crankshaft drives of the vertical drive 12 and the horizontal drive 5 can be arranged in a common machine plane.
• the coupling mechanism 18 consists in this embodiment of a rocker arm 20 which is pivotally mounted on a pivot bearing 21.
• the rocker arm 20 has at a free end below the pivot bearing 21, a rotary joint 22.2, with which the horizontal link 15 is connected to the tilt lever 20.
• the rocker arm 20 is L-shaped and has at a second free end a second pivot 22.1 on which a coupling member in the form of a push rod 19 engages.
• the push rod 19 is coupled to an opposite end by the double pivot 10 with the connecting rods 9.1 and 9.2 of the connecting rods 7.1 and 7.2.
• the connecting rods 7.1 and 7.2 are arranged in an inclined position and connected via their connecting rod 8.1 and 8.2 with the parallel juxtaposed crankshafts 6.1 and 6.2.
• the center axes of the connecting rods 7.1 and 7.2 form the angle ⁇ , which also in this case has a size of less than 180 °.
• crankshafts 6.1 and 6.2 are driven in opposite directions at the same speed, wherein the phase angles of the crankshafts 6.1 and 6.2 are set as a function of a desired horizontal stroke to each other.
• the adjustment of the phase positions in the crankshaft 6.1 and 6.2 can be carried out as previously described in the embodiment of FIG.
• the connecting rods 7.1 and 7.2 When driving the crankshafts 6.1 and 6.2, the connecting rods 7.1 and 7.2 are deflected so that they move in the common coupling point, the double swivel joint on a guideway.
• This directly on the push rod 19 transmitted movement is transmitted from the push rod 19 via the rocker arm 20 to the horizontal link 15.
• the stroke movement generated by the eccentric drives 5.1 and 5.2 is transmitted to the beam support 2 with a translation.
• the beam carrier 2 In relation to the double swivel joint 10, the beam carrier 2 thus carries out a stroke movement changed by a gear ratio, in this case smaller.
• the exemplary embodiment of the device according to the invention shown in FIG. 2 represents only one further possibility for connecting the two eccentric drives 5.1 and 5.2 of the horizontal drive 5 to the horizontal link 15 via a coupling mechanism 18.
• both the power transmission of the horizontal link 15 on the beam support 2 and the lifting movement of the horizontal link 15 on the beam support 2 can be influenced.
• the eccentric drives 5.1 and 5.2 of the horizontal drive 5 and the eccentric 12.1 and 12.2 of the vertical drive 12 can be arranged in a common upper machine level.
• a coupling mechanism 18 is arranged between the horizontal drive 5 and the horizontal link 15.
• a coupling mechanism 18 is arranged between the horizontal drive 5 and the horizontal link 15.
• FIG. 3 is largely identical to the embodiment of FIG. 1 and differs only by the interposition of a linkage 18.
• the coupling mechanism 18 is formed by a rocker arm 20 and a coupling member 19, wherein the coupling member in here also as a push rod 19 is executed.
• the rocker arm 20 is held on a pivot bearing 21 and has at a lower end below the pivot bearing 21, a rotary joint 22 for connecting the horizontal link 15.
• the push rod 19 is coupled via the double swivel joint 10 with the connecting rods 7.1 and 7.2 of the eccentric drives 5.1 and 5.2.
• the eccentric drives 5.1 and 5.2 of the horizontal drive 5 are identical to the exemplary embodiment of FIG. 1, so that no further explanation for this is done.
• the linkage 18 between the eccentric drives 5.1 and 5.2 and the horizontal link 15 can, depending on
• Gear ratios are set.
• the horizontal stroke and the force guide in the beam support 2 for guiding the needle bar 1.1 and 1.2 influence.
• two needle bars 1.1 and 1.2 are held on the beam support 2.
• Each of the needle bars has a needle board 3 with a plurality of needles 4.
• the needle bars 1.1 and 1.2 are associated with a tray, not shown here, in which a nonwoven web is guided.
• the acting on the beam support 2 vertical drive 12 is identical to the aforementioned embodiments, so that there is no further explanation.
• the size of the offset is chosen here by way of example.
• the connecting rods 7.1 and 7.2 of the eccentric drives 5.1 and 5.2 also form here with their central axes an angle ⁇ , wherein the axes of rotation of the hinges 11.1 and 11.2 need not necessarily be at the apex of the angle.
• the crankshafts 6.1 and 6.2 offset from each other, so that the connecting rods 7.1 and 7.2 are formed with the same length.
• a further variant for the formation of the horizontal drive 5 is shown.
• the hinges 11.1 and 11.2 for connecting the connecting rods 7.1 and 7.2 offset in the vertical direction to each other.
• the connecting rods 9.1 and 9.2 are coupled to the horizontal link 15.
• the connecting rods 7.1 and 7.2 associated crankshafts 6.1 and 6.2 are connected via the connecting rod ends 8.1 and 8.2 with the connecting rods 7.1 and 7.2.
• the pivots 11.1 and 11.2 are each formed on the horizontal link 15.
• the hinges 11.1 and 11.2 are formed on a coupling member of a linkage, for example on the push rod 19 of the coupling gear 18 shown in Fig. 2 and 3.
• the horizontal drive 5 is formed by the eccentric drives 5.1 and 5.2.
• the crankshafts 6.1 and 6.2 of the eccentric drives 5.1 and 5.2 are arranged above the beam support 2 together with the crankshafts 25.1 and 25.2 of the vertical drive 12 in a machine plane.
• the eccentric drives 5.1 and 5.2 of the horizontal drive associated connecting rods 7.1 and 7.2 are connected via a coupling gear 18 with the horizontal link 15.
• the coupling mechanism 18 is formed by a rocker arm 20 and a push rod 19.
• the connecting rods 7.1 and 7.2 engage via a double pivot 10 at a free end of the push rod 19.
• the rocker arm 20 is connected via a rotary joint 22.1.
• the rocker arm 20, which has an elongated shape, is pivotally mounted in the middle region on a pivot bearing 21.
• the rocker arm 20 is connected by a further rotary joint 22.2 with the horizontal link 15.
• the connecting rods 7.1 and 7.2 form with their central axes an angle ⁇ , which is ⁇ 180 °.
• the horizontal drive 5 is associated with a Phasenverstell worn in the embodiment of FIG. 6.
• a first servomotor 26.1 engages on the crankshaft 6.1 and a second servomotor 26.2 on the crankshaft 6.2.
• the servomotors 26.1 and 26.2 are independently controllable via a control device 27. By activating the servomotors 26.1 and 26.2 or only one of the motors, the phase positions of the crankshafts 6.1 and 6.2 can be adjusted relative to each other so that the trajectory of the double pivot 10 is changeable.
• the double swivel joint 10 which forms the coupling point of the connecting rods 7.1 and 7.2, always moves on an ellipsis-like path whose width and height depends on the phase angle of the two crankshafts. As an extreme case, this results in either approximately a horizontal or exact vertical straight line for maximum or minimum horizontal stroke.
• the phase positions of the crank Shafts 6.1 and 6.2 advantageously each set a desired length of the horizontal stroke.
• the movement of the connecting rods can be particularly advantageous over the push rod 19 and the horizontal link 15 and the tilt lever 20 transmitted to the beam support 2, so that reverses the direction of movement. This can be compensated for at least part of the horizontal inertia.
• the influence of the horizontal link 15 on the bar movement can be compensated by the push rod 19, so that a straight guide path results with a zero stroke with a very good approximation.
• the crankshafts 6.1 and 6.2 of the horizontal drive 5 are driven in opposite directions. The direction of movement of the crankshafts 6.1 and 6.2 is indicated in Fig. 6 by an arrow.
• 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 with variable horizontal stroke.
• a high uniform needling quality can be achieved in the structuring of nonwovens even at maximum production speeds.
• a very compact design with low space requirement is created.
• the simple gearbox kinematics for controlling the horizontal link as well as the stiffening shape of the horizontal link for axial guidance of the beam support enable a constructive design with few parts and low masses.
• very high movement frequencies of the beam support can be achieved, since the compact design allows a rigid structure of the machine frame.
• the vertical drive and the horizontal drive can be operated both synchronously and asynchronously to move the beam carrier.
• This can be the Drive eccentric drives with any phase settings, so that a high flexibility in the motion control of the beam carrier is given.

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

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• 2008
  • 2008-06-02 JP JP2010511578A patent/JP2010530034A/ja not_active Ceased
  • 2008-06-02 WO PCT/EP2008/056783 patent/WO2008151961A1/fr active Application Filing
  • 2008-06-02 US US12/664,581 patent/US8069541B2/en not_active Expired - Fee Related
  • 2008-06-02 CN CN2008800204552A patent/CN101680145B/zh not_active Expired - Fee Related
  • 2008-06-02 CA CA 2689142 patent/CA2689142A1/fr not_active Abandoned
  • 2008-06-02 AT AT08760369T patent/ATE490360T1/de active
  • 2008-06-02 DE DE200850001954 patent/DE502008001954D1/de active Active
  • 2008-06-02 EP EP20080760369 patent/EP2158348B1/fr not_active Not-in-force

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