EP2250308A1

EP2250308A1 - Device for needling a web of fiber

Info

Publication number: EP2250308A1
Application number: EP09718088A
Authority: EP
Inventors: Tilman Reutter; Andreas Plump; Andreas Mayer; Daniel Bu
Original assignee: Oerlikon Textile GmbH and Co KG
Current assignee: Oerlikon Textile GmbH and Co KG
Priority date: 2008-03-03
Filing date: 2009-03-02
Publication date: 2010-11-17
Anticipated expiration: 2029-03-02
Also published as: ATE525509T1; EP2250308B1; WO2009109553A1; US8099840B2; CN101960065A; CN101960065B; US20110047767A1

Abstract

The invention relates to a device for needling a web of fiber, said device comprising at least one driven needle beam. A vertical reciprocal movement of the needle beam is carried out by a vertical drive unit and a superposed horizontal reciprocal movement is carried out by a horizontal drive unit or due to a phase adjustment by the vertical drive unit. A weight balancing device is provided for balancing the inertia forces of the crank mechanisms. In order to be able to balance both vertical and horizontal inertia forces in a simple manner, the weight balancing device is formed by at least one balance weight which is associated with the crank mechanism of the vertical drive unit and which is set-off by an angle in the range of <180° from an eccentric element of the crank mechanism.

Description

Apparatus for needling a fibrous web

The invention relates to a device for needling a fibrous web according to the preamble of claim 1.

In devices for needling a fibrous web, a needle bar, on the underside of which a multiplicity of needles are held, is driven in an oscillating up and down motion, so that the needles puncture the fibrous web guided on a support in a recurring manner. To drive such needle bar crank gears are usually used, with an eccentrically rotating eccentric mass for mass balance are usually compensated by appropriate balancing weights on the crankshaft. Thus, the mass effects due to the rotating us oscillating masses within the device can be kept so small that no inadmissible vibrations occur in the machine frame. To achieve higher production speeds when needling a fiber web drive concepts of the needle bar are now known, in which a superimposed aligned in the horizontal direction reciprocating motion of the needle bar is generated to the up and down movement. Such a device is known for example from DE 196 15 697 Al.

In the known device, the needle bar is driven by a vertical engine to an up and down movement and superimposed by a horizontal engine to a reciprocating motion. Here, the mass forces occur in the device both in the vertical direction and in the horizontal direction. To compensate for the mass forces and moments of inertia, several balance shafts are arranged in the machine frame in the known device, which counteract the mass forces and mass moments of the crank drives by counter-rotating eccentric masses. This form of mass Compensation is technically very complex and requires a considerable amount of space within the device. The free mass forces and moments of inertia occurring with variable stroke adjustment of the horizontal engine are particularly problematical because they increase quadratically with the stroke frequency and linearly with the lifting height. Thus, higher stroke frequencies and thus higher production speeds and larger horizontal strokes of the needle bar in the known device inevitably lead to increased vibrations in the machine frame. However, such vibrations are very negative in terms of noise and especially in terms of product quality.

It is therefore an object of the invention to provide a device for needling a fiber web of the generic type such that a mass balance of the vertical forces occurring in the vertical and horizontal directions is possible by simple means.

Another object of the invention is to provide a device of the generic type which allows variable stroke settings of the needle bar with relatively large horizontal strokes and high stroke frequencies.

This object is achieved by a device with the features of claim 1.

Advantageous developments of the invention are defined by the features and feature combinations of the subclaims.

The invention is distinguished from the principle of compensating for mass forces acting on a crank drive by means of a counterweight arranged in an eccentric plane opposite the eccentric mass. The invention is based on the recognition that the crank drive of the vertical engine can be used to counteract the vertically directed inertial forces and the horizontally directed inertial forces. This is a balancing mass the mass balancing device associated with the crank drive of the vertical engine and arranged at an angle in the range <180 ° offset to an eccentric of the crank drive. The size of the balancing mass and the angular position of the balancing mass on the crank drive can be selected depending on the forces acting in the vertical direction and horizontal direction and mass moments. This allows compensation functions to be implemented on the existing crank drives, which would otherwise only be achieved by additional balance shafts or other complex measures. The balancing mass is for this purpose arranged directly on a crankshaft or an eccentric shaft of the crank drive. It is irrelevant whether the superimposed horizontal movement of the needle bar is generated by a horizontal engine or in phase adjustment directly by the vertical engine. In any case, the occurring horizontal mass forces can be compensated by the balancing mass on the crank mechanism of the vertical engine.

In a particularly preferred embodiment of the invention, the balancing mass is offset by the angle of 90 ° to the eccentric of the crank drive and a second balancing mass offset by the angle of 180 ° to the eccentric of the crank drive attached. Thus, the vertical mass forces of the needle bar on the crank drive can be completely compensated. The horizontal mass forces is offset by 90 ° offset from the eccentric mass of the crank drive balancing mass. Thus, a complete mass balance can be realized with constant horizontal stroke of the needle bar. The needle bar can be operated with correspondingly high stroke frequencies without inadmissible vibrations on the machine frame becoming effective.

The balancing weights assigned to a crank drive can be identical or different in size. The choice of the size of the compensating masses depends essentially on the mass forces occurring during operation. In order to realize a parallel guidance of the needle bar within a machine frame, the vertical engine is preferably formed by two synchronously rotating crank drives. In this case, according to an advantageous further development of the invention, each of the crank drives is assigned in each case one or more compensation masses. Thus, each crank drive can be used to balance the mass of vertical and horizontal inertial forces. The balancing weights on the crank drives of the vertical engine can be identical or different on each of the crank drives. Thus, for example, one of the crank drives can be equipped with two balancing weights, whereas, on the other hand, the second crank drive receives only one balancing weight.

In particularly complex drive concepts of the needle bar, the mass balancing device can also be expanded by arranging an additional balancing shaft with a circumferential eccentric mass within the machine frame. Thus, in particular, the mass moments within the machine frame can be fully compensated. Depending on the drive concept, the balancer shaft can be equipped with a rotating eccentric mass or with two eccentric masses that are offset by 90 °.

In the event that the horizontal movement is generated by the phase adjustment of the vertical engine, the phase adjustment preferably has two separately controllable servo motors, which are assigned to the crankshaft of the crank mechanisms of the vertical engine. Depending on the phase difference between the crankshafts, different strokes in the horizontal movement can thus be realized. For mass and torque compensation, the balance shaft is preferably arranged symmetrically to the two crankshafts of the crank mechanisms.

In order to be able to directly compensate for the mass forces acting in the horizontal engine at a separate crank drive of the horizontal engine,

- A - According to an advantageous development of the invention, at least one further balancing mass is assigned to the crank drive of the horizontal engine and arranged offset by an angle in the range of <180 ° relative to the eccentric of the crank drive.

Alternatively, however, it is also possible to choose the arrangement of the balancing masses on the crank drive of the horizontal engine such that the balancing mass is held offset by 90 ° to the eccentric and a second balancing mass is arranged opposite to the eccentric mass.

In order to realize as possible a flexible horizontal drive of the needle bar, the horizontal engine is preferably formed by two synchronously rotating crank drives. In this case, at least one of the balancing weights is advantageously assigned to each of the crank drives.

In order to enable a variable stroke adjustment, the crank drives of the horizontal engine are driven in opposite directions and designed to be adjustable in their phase positions. By means of the balancing weights assigned to the crank drives, the variable mass forces can be compensated for in addition to the constant mass forces. With a suitable choice of balancing weights thus the resulting mass force disappears approximately for each horizontal stroke adjustment between zero and a maximum stroke.

In order to obtain the most stable possible guidance of the drive movement of the needle bar, the crank drives of the horizontal engine are preferably connected by a coupling gear with the needle bar. Thus, the drive movement of the crank drives via the coupling gear can be converted into an almost exclusive degree movement on the needle bar.

The crank drives of the vertical engine and the horizontal engine are usually by a respective driven crankshaft or a ange- formed driven eccentric shaft, which are connected via a connecting rod with a connecting rod.

To compensate for the mass forces, the balancing weights are applied directly to the crankshaft or to the eccentric shaft.

The device according to the invention is explained in more detail below with reference to an embodiment with reference to the attached figures.

They show:

Fig. 1.1 and 1.2 schematically a side view of a first embodiment of the device according to the invention Fig. 2 shows a schematic side view of an embodiment of a crank mechanism with mass balance

Figures 3.1 and 3.2 schematically a side view of another embodiment of the device according to the invention. Figure 4 shows schematically a side view of another embodiment of the device according to the invention

Fig. 5 shows schematically a side view of another embodiment of the device according to the invention

FIGS. 1.1 and 1.2 show a first exemplary embodiment of the device according to the invention for needling a fibrous web. The exemplary embodiment is shown in FIGS. 1.1 and 1.2 in different operating situations. The description therefore applies to both figures. The embodiment of the device according to the invention comprises a beam support 2, which holds a needle bar 1 on its underside. The needle bar 1 holds on its underside a needle board 24 with a plurality of needles 25th On the beam support 2 engages a vertical engine 3 and a horizontal engine 10 at. By the vertical engine 3, the beam support 2 is oscillated in the vertical direction, so that the needle bar 1 with the needle board 24 performs an up and down movement. The vertical engine 3 is formed by two parallel crank mechanisms 4.1 and 4.2. The crank drives 4.1 and 4.2 have two parallel juxtaposed crankshafts 5.1 and 5.2, which are arranged above the beam carrier 2. The crankshafts 5.1 and 5.2 each have at least one eccentric 6.1 and 6.2 each for receiving a connecting rod 7.1 and 7.2.

In Fig. 1 arranged on the beam support 2 connecting rods 7.1 and 7.2 are shown, which are held with their connecting rod heads on the eccentrics 6.1 and 6.2 of the crankshaft 5.1 and 5.2. At the crankshafts 5.1 and 5.2 even further - may be arranged - connecting rods - not shown here.

The connecting rods 7.1 and 7.2 are connected with their free ends through the hinges 8.1 and 8.2 with the beam support 2. The crankshafts 5.1 and 5.2 are driven synchronously or in opposite directions synchronously, so that the beam support 2 is guided at least approximately parallel.

For superimposed horizontal movement of the needle bar 1, the horizontal engine 10 engages via a crank drive 11.1 directly to the beam support 2. The crank drive 11.1 of the horizontal engine 10 has for this purpose a crankshaft 12.1 and a connecting rod 14.1. The connecting rod 14.1 is connected via an eccentric 13.1 with the crankshaft 12.1. At the free end, the connecting rod 14.1 is coupled by the rotary joint 15 with the beam support 2. The crankshaft 12.1 is driven in synchronism with the crankshafts 5.1 and 5.2 of the vertical engine, so that the needle bar 1 performs a lifting movement with a constant horizontal stroke. The vertical engine 3 and the horizontal engine 10 is associated with a mass balancing device to compensate for the mass forces of the crank mechanisms. The mass balancing device is formed by a plurality of balancing masses which are assigned to the crank drives 4.1, 4.2 and 5.1. The cure drive 4.1 has the balancing weights 9.1 and 9.2. The balancing mass 9.1 is this offset by an angle of 180 ° to the eccentric 6.1 on the crankshaft 5.1. The balancing mass 9.2 is held at an angle of 90 ° offset from the eccentric 6.1 on the crankshaft 5.1.

A third balancing mass 9.3 is arranged as a counterweight on the crank drive 4.2. For this purpose, the balancing mass is 9.3 offset by an angle of 180 ° to the eccentric 6.2 arranged on the crankshaft 5.2.

The crank drive 11.1 of the horizontal engine 10, the balancing weights 16.1 and 16.2 are assigned. The balancing mass 16.1 is this offset by the angle of 180 ° to the eccentric 13.1 held on the crankshaft 12.1. The other balancing mass 16.2 is offset by the angle of 90 ° to the eccentric 13.1 attached to the crankshaft 12.1.

To further explain the mass balancing device, the embodiment in Fig. 1.1 is shown in an operating situation in which the needle bar is shown in an upper position with vertically directed inertial forces. In contrast, in FIG. 1.2, the exemplary embodiment is shown in a middle beam position, in which horizontal mass forces are effective.

In the situations shown in FIG. 1.1, the mass forces generated by the balancing weights 9.1, 9.2, 9.3, 16.1 and 16.2 are represented as vectors. Thus, the force vector of the balancing mass 9.1 is marked with the code letter F _EI . Accordingly, the mass force of the balancing mass 9.2 is referred to the crank drive 4.1 by the letter F _N1 . Analogously, the force vector of the balancing mass 9.3, which is assigned to the crank drive 4.2, denoted by the letter F _E2 . The the crank mechanism 11.1 of the horizontal engine 10 associated balancing weights 16.1 and 16.2 are denoted by the code letters F _N3 and F _E3 and shown as force vectors.

In the operating positions shown in FIGS. 1.1 and 1.2, the mass force F _B acting on the needle bar is compensated by the forces F _EI + F _E2 + F _{E3 of} the balancing weights 9.1, 9.2 and 9.3 of the crank drives 4.1 and 4.2. In the operating positions shown, the mass forces F _N1 and F _{N3 of} the balancing weights 9.2 and 16.2 are opposite. Thus, it is possible to compensate for the horizontal and the vertical mass force by the balancing weights 9.1, 9.2 and 9.3. The balancing weights 9.2 and 16.2, which cause the mass forces F _N1 and F _N3 , are now chosen so that they cancel each other in each position of the needle bar and cause a mass moment to compensate for the caused by the working line distance between beam forces and balancing forces mass moment.

In the exemplary embodiments illustrated in FIGS. 1.1 and 1.2, there are basically two options for attaching the balancing weights to the respective crank drive. FIG. 2 shows a further possible arrangement of a compensating mass, as may alternatively be embodied, for example, on the crank drive 4.1 of the vertical drive mechanism 3 or of the crank drive 11.1 of the horizontal drive mechanism 10. For this purpose, the crank drive 4.1 is assigned a compensating mass 9.2. The balancing mass 9.2 is offset by an angle α to the eccentric 6.1 of the crankshaft 5.1. The angle α is less than 180 ° and preferably chosen such that both horizontally acting and vertically acting forces can be compensated by the balancing mass 9.2. Thus, the number of balancing weights can be reduced while maintaining the same effect.

In FIGS. 3.1 and 3.2, a further exemplary embodiment of the device according to the invention is shown schematically in a side view in several operating positions. represented. The embodiment of FIGS. 3.1 and 3.2 is substantially identical to the embodiment of FIGS. 1.1 and 1.2, so that only the differences will be explained at this point and otherwise reference is made to the above description. In Fig. 3.1, the embodiment is shown in an upper position of the needle bar and in Fig. 3.2 in a middle position of the needle bar.

In the exemplary embodiment illustrated in FIGS. 3.1 and 3.2, two needle bars 1.1 and 1.2 are respectively held on the beam support 2, each of which carries a needle board 24 and a plurality of needles 25 on their undersides. The beam support 2 is coupled to a vertical engine 3, 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 15 with a handlebar 19. In this embodiment, the rotary joint 15 is arranged substantially with the hinges 8.1 and 8.2 for connecting the vertical engine 3 at a common height on the beam support 2, so that arranged to the transverse sides of the beam support 2 link 19 allow the power instructions and the leadership of the beam support 2 ,

For the deflection of the link 19, a horizontal engine 10 is provided, which is formed by two crank drives 11.1 and 11.2. The crank mechanisms 11.1 and 11.2 each have a crankshaft 12.1 and 12.2, which are arranged parallel to each other and together with the crankshafts 5.1 and 5.2 of the vertical engine 3 form a common drive plane. The crankshafts 12.1 and 12.2 are connected via their eccentric 13.1 and 13.2 each with a connecting rod 14.1 and 14.2. The connecting rods 14.1 and 14.2 are directed in an inclined position to each other, so that the free ends of the connecting rods 14.1 and 14.2 are connected via a double pivot joint 21 together with a coupling gear 17. The coupling mechanism 17 consists in this embodiment of a rocker arm 18 which is pivotally mounted on a pivot bearing 26. The rocker arm 18 has at a free end below the pivot bearing 26 has a pivot, with which the link 19 is connected to the rocker arm 18. At the opposite free end of the rocker arm 18, a further rotary joint is provided, on which a push rod 20 engages. The push rod 20 is coupled to an opposite end by the double pivot 21 with the connecting rods 14.1 and 14.2.

The crankshafts 12.1 and 12.2 of the crank mechanisms 11.1 and 11.2 are driven in opposite directions at the same speed, wherein the phase angles of the crankshafts 12.1 and 12.2 are adjustable relative to each other in dependence on a desired horizontal stroke. The phase angles and thus the desired horizontal stroke of the crankshafts 12.1 and 12.2 can be carried out, for example, by two separate servomotors which effect a rotation of the crankshafts 12.1 and 12.2 relative to each other. The drive of the crankshafts 14.1 and 14.2 can be carried out by a common drive or separately via separate drives.

To compensate for the mass forces on the crank mechanisms 4.1, 4.2, 11.1 and 11.2, a mass balancing device is provided, which is formed by a plurality of the crank mechanisms associated with balancing masses. Each of the crank drives 4.1 and 4.2 of the vertical engine 3 has two balancing weights. A first balancing mass is arranged as a counterweight on the crank drives 4.1 and 4.2 and arranged at an angle of 180 ° offset from the eccentrics 6.1 and 6.2 of the crankshafts 5.1 and 5.2. The balancing weights are denoted by the reference numeral 9.1 on the crank drive 4.1 and 9.3 on the crank drive 4.2. A second balancing mass is arranged offset by 90 ° to the eccentrics 6.1 and 6.2 at the shafts 5.1 and 5.2. The balancing weights 9.2 and 9.4 of the crank drive 4.1 and 4.2 are designed to be larger in mass than the balancing weights 9.1 and 9.3. The crank mechanisms 11.1 and 11.2 of the horizontal engine 10 each have a balancing mass 16.1 and 16.2. At the crank drive 11.1 the balancing mass 16.1 is offset at an angle <180 ° to the eccentric 13.1 of the crankshaft 12.1. The angle α, which denotes the offset between the eccentric 13.1 and the balancing mass 16.1 on the crankshaft 12.1, is approximately 20 ° in this exemplary embodiment. The position of the balancing mass 16.1 and also the position of the balancing mass 16.2 is essentially determined by the arrangement of the crank drives 11.1 and 11.2 to each other. So are the connecting rods

14.1 and 14.2 arranged in an inclined position and connected to each other via the double pivot 21. The balancing mass 16.2 on the crank drive 11.2 is thus mounted in the same position and in the same size on the crank drive 11.2.

To drive the needle bar 1.1 and 1.2, both the crank drives 4.1 and 4.2 of the vertical engine 3 and the crank mechanisms 11.1 and 11.2 of the horizontal engine 10 are driven synchronously and in opposite directions. In Fig. 3.1, the situation is shown in which the beam support 2 is held with the needle bar 1.1 and 1.2 in an upper dead position. FIG. 3.2 illustrates the exemplary embodiment in the operating situation, in which the beam support 2 with the needle bar 1.1 and 1.2 in a middle position during execution of a horizontal movement. The mass forces 9.1 to 9.4 and the balancing weights 16.1 and 16.2 are associated mass forces denoted by the code letters F _A and F _E.

The four balancing forces F _A1 to F _{A4 of} the balancing weights 9.2, 9.4, 16.1 and

16.2 compensate each other in the dead states of the beam carrier 2, as can be seen from FIG. 3.1. The mass forces F _EI and F _E2 caused by the balancing weights 9.1 and 9.4 are opposite to the mass force F _B acting on the beam carrier 2. Between the death positions remains due to the misalignment of the force components, a resultant inertial force. With a suitable choice of the balancing weights 9.2, 9.4, 16.1 and 16.2, with this force component the hori- zontal mass force of the beam carrier with the needle bar 1.1 and 1.2 compensated in the horizontal direction. In the vertical direction, the compensating force changes only slightly, especially at low adjustment angles and therefore misalignments of the force components, so that the force compensation for each horizontal stroke is maintained to a maximum adjustment angle of approximately 20 ° in very good nutrition, as can be seen from the situation in FIG 3.2.

However, it is also possible to design the mass balance, for example, to an adjustment angle that is different from zero. This means that the compensating masses on the crank drives 11.1 and 11.2 of the horizontal engine 10 are rotated by the angle α, so that the corresponding compensating forces are perpendicular at a corresponding displacement angle. This has the consequence that the usable adjustment angle can be doubled, without there being significant deviations in the vertical force compensation. The balancing weights 9.1 to 9.4 on the crank drives 4.1 and 4.2 of the vertical engine 3 are to be adapted in this case so that the mass forces in the vertical and horizontal directions are balanced for the region of the horizontal stroke.

In order to compensate in particular in addition to the balance of inertial forces and any form of occurring free mass moments, the embodiment shown in FIGS. 3.1 and 3.2 run the device according to the invention with a mass balancing device, in which in addition to the balancing masses in addition a balance shaft with a rotating eccentric mass is provided. Such an embodiment is shown in FIG.

The embodiment of FIG. 4 is identical to the embodiment of FIG. 3.1 except for the mass balancing device. In that regard, reference is made to the above description and then explained only the differences. For mass balance, the mass balancing device on several balancing weights and a balancer shaft with rotating eccentric mass. The balancing shaft 22 is arranged in the drive plane between the crank drives 11.1 and 11.2 of the horizontal engine 10. The balance shaft 22 extends parallel to the lying in the drive plane crankshafts 12.1 and 12.2, which are also held parallel to the arranged in the same plane crankshafts 5.1 and 5.2 of the vertical engine 3. At the balance shaft 22, an eccentric mass 23 is arranged. The balancing shaft 22 is driven synchronously to the crankshafts 12.1 and 12.2 of the crank drives 11.1 and 11.2, wherein the balancer shaft 22 and the crankshaft 12.1 have the same direction of rotation.

For mass balance, the balancing weights 16.1 and 16.2 are arranged on the crankshafts 12.1 and 12.2 of the crank drives 11.1 and 11.2. The arrangement is identical to the previously described embodiment of FIG. 3.1.

The crank mechanisms 4.1 and 4.2 of the vertical engines 3 are also each two balancing weights assigned in an offset arrangement to each other. Thus, the balancing weights 9.1 and 9.2 are assigned to the crank drive 4.1 and the balancing weights 9.3 and 9.4 to the crank drive 4.2. The balancing weights 9.1 to 9.4 of the crank drives 4.1 and 4.2 are designed differently in size. The balancing mass 9.2, which is arranged essentially to compensate for horizontal mass forces on the crank drive 4.1, is smaller than the balancing mass 9.4 on the second crank drive 4.2 of the vertical engine 3.

Overall, results in the situation shown in Fig. 4, a balance of power between the forces generated by the balancing weights. The mass force F _{M of} the eccentric mass 23 acts rectified to the mass force F _{A4 of} the balancing mass 16.2 on the crank drive 11.2. The mass forces F _M and F _A4 are opposed by the mass forces F _A1 , F _A2 and F _A3 . The on the beam support 2 effective vertical mass force F _B is compensated by arranged on the crank drives 4.1 and 4.2 balancing weights 9.1 and 9.4 and their mass forces F _EI and F _E2 .

5, a further embodiment of the device according to the invention for needling a fibrous web is shown schematically in a side view. The embodiment of FIG. 5 differs substantially from the aforementioned embodiments in that no separate horizontal engine is present to produce a superimposed horizontal movement of the needle bar. In the embodiment of the device according to the invention shown in Fig. 5, the superimposed horizontal movement of the needle bar via the vertical engine 3 is initiated.

For this purpose, the vertical engine connected to the beam carrier 2 has two parallel crank drives 4.1 and 4.2 arranged parallel to each other. The crank drives 4.1 and 4.2 have two parallel juxtaposed crankshafts 5.1 and 5.2, which are arranged above the beam carrier 2. The crankshafts 5.1 and 5.2 each have at least one eccentric section for receiving at least one connecting rod. FIG. 5 shows the connecting rods 7.1 and 7.2 arranged on a beam support 2, which are guided with their connecting rod heads on the crankshafts 5.1 and 5.2.

The crankshafts 5.1 and 5.2 are assigned a phase adjustment device 36. The phase adjustment device 36 has two servomotors 34.1 and 34.2, which are assigned to the crankshafts 5.1 and 5.2. The servomotors 34.1 and 34.2 are connected to a control device 35. Via the control device 35, the servomotors 34.1 and 34.2 can be activated independently of one another in order to turn the crankshafts 5.1 and 5.2 in their positions. Thus, the phase angle between the two crankshafts 5.1 and 5.2 can be adjusted. In addition to the pure vertical up and down movement of the beam support 2 can thereby perform a superimposed horizontal movement of the beam support 2. at an offset of the phase angles of the crankshafts 5.1 and 5.2 is introduced via the connecting rods 7.1 and 7.2 on the beam support 2 a skewing, which generates a progressive movement in the direction of movement of a fiber web movement component. The size of the phase adjustment between see the crankshafts 5.1 and 5.2 is directly proportional to a stroke length of the horizontal movement. The stroke of the horizontal movement can therefore be adjusted via the phase angle of the crankshafts 5.1 and 5.2.

In the situation illustrated in FIG. 5, a phase difference is set between the crankshafts 5.1 and 5.2, so that the beam carrier 2 with the needle bar 1.1 and 1.2 executes a constant stroke in the horizontal direction.

To guide the beam carrier 2, a guide device 27 is provided. The guide device has a link 19, which is connected to a free end via a rotary joint 15 with the beam support 2. At the opposite end of the handlebar engages a first rocker 28, which is connected via a pivot bearing 32 to a machine frame and a rotary joint 30 with the handlebars. At a distance from the first rocker 28, a second rocker 29 is provided, which is held via a pivot 31 in the central region of the link 19 and a pivot bearing 33.

The guide device 27 is arranged above the beam support 2. The pivot bearings 32 and 33 are arranged between the connecting rods 7.1 and 7.2. The handlebar 19 is connected in the middle of the beam via the rotary joint 15 with the beam carrier. This allows a secure guidance of the beam support during the drive movement realized by the vertical engine 3.

The cranks drives 4.1 and 4.2 associated mass balancing device is formed in this embodiment by a total of four balancing weights 9.1, 9.2, 9.3 and 9.4. The balancing weights 9.1 and 9.2 are the crankshaft

5.1 assigned. The balancing weights 9.3 and 9.4 are on the crankshaft 5.2 attached. The balancing mass 9.1 is arranged on the crankshaft 5.1 offset by the angle 180 ° to the eccentric 6.1. The balancing mass 9.2 is offset by an angle of 90 ° to the first balancing mass 9.1 attached to the crankshaft 5.1.

In the case of the crank drive 4.2, the balancing mass 9.3 is offset by 180 ° relative to the eccentric 6.2 on the crankshaft 5.2. The balancing mass 9.4 is offset by the angle of 90 ° to the first balancing mass 9.3 held on the crankshaft 5.2. Thus, both the vertical and the horizontal inertia forces on the crank drives 4.1 and 4.2 can be compensated advantageously by the balancing weights 9.1 to 9.4.

In order to achieve in particular complete compensation of the mass forces and moments of inertia, the mass balancing device additionally has a balancing shaft 22, which is arranged above the crankshafts 5.1 and 5.2. The balance shaft 22 is held symmetrically to the crank drives 4.1 and 4.2. At the balance shaft 22 two eccentric weights 23.1 and 23.2 are arranged. The balancer shaft 22 extends parallel to the crankshafts 5.1 and 5.2 and is driven in synchronism with the crankshafts 5.1 and 5.2. The direction of rotation of the balance shaft 22 and the direction of rotation of the crankshafts 5.1 and 5.2 is indicated in Fig. 5 in each case by an arrow.

The function for balancing the mass forces in the operation of the device shown in Fig. 5 is identical to the aforementioned embodiments, so that there is no further explanation.

The invention extends not only to the embodiments shown in FIGS. 1, 3 and 4 of a device for needling a fibrous web, but can also be advantageously applied to other engine concepts in which the needle bar is guided with a constant horizontal stroke or with variable horizontal strokes. deploy. The invention is particularly advantageous in the case of such devices. gene, in which the stroke adjustment of the horizontal stroke takes place by rotation of two eccentric shafts to each other. It should be expressly mentioned at this point that the invention is not limited to the fact that the crank mechanisms are driven by crankshafts. Basically, the crankshafts can easily be replaced by eccentric shafts.

LIST OF REFERENCE NUMBERS

1, 1.1, 1.2 Needle bars

2 beam supports

3 vertical engine

4.1.4.2 Crank drives

5.1.5.2 Crankshafts

6.1,6.2 eccentric

7.1,7.2 connecting rods

8.1,8.2 swivel joint

9.1,9.2,9.3 balancing mass

10 horizontal drive

11.1, 11.2 Crank drive

12.1, 12.2 crankshaft

13.1, 13.2 eccentric

14.1, 14.2 connecting rod

15 swivel joint

16.1, 16.2 balancing mass

17 coupling gear

18 rocker arms

19 handlebars

20 coupling link

21 double swivel joint

22 balance shaft

23,23.1,23.2 eccentric mass

24 needle board

25 needles

26 pivot bearings

27 guide device 28 first swingarm

29 second swingarm

30 swivel joint

31 swivel joint 32 swivel bearings

33 pivot bearings

34.1, 34.2 servomotor

35 control device

36 phase adjuster

Claims

claims

A device for needling a fiber web with at least one driven needle bar (1), with a vertical engine (3) for oscillating movement of the needle bar (1) in a vertical upward and downward movement, with a horizontal engine (10) or a vertical engine (3 ) for performing a superimposed oscillating movement of the needle bar (1) in a horizontal reciprocating motion, wherein the vertical engine (3) separate crank drives (4.1, 4.2), and with a mass balancing device (9.1, 9.2 ) to compensate for the mass forces of the crank drives (4.1, 4.2), characterized in that the mass balancing device by at least one balancing mass

(9.2) is formed, which is associated with the crank drive (4.1) of the vertical engine (3) and which is offset by an angle (α) in the range of less than 180 ° to an eccentric (6.1) of the crank drive (4.1).

2. Apparatus according to claim 1, characterized in that the balancing mass (9.2) offset by the angle of 90 ° to the eccentric (6.1) of the crank drive (4.1) is arranged and that a second balancing weight (9.1) by the angle of 180 ° offset from the eccentric (6.1) of the crank drive (4.1) is arranged.

3. A device according to claim 2, characterized in that the two balancing weights (9.1, 9.2) are the same size or unequal size formed.

4. Device according to one of claims 1 to 3, characterized in that the vertical engine (3) by two synchronously rotating crank drives (4.1, 4.2) is formed and that the mass balancing device is formed by several balancing weights (9.1 - 9.4), the the two crank mechanisms (4.1, 4.2) are assigned.

5. Apparatus according to claim 3, characterized in that the eccentrics (6.1, 6.2) of the crank drives (4.1, 4.2) of the vertical engine

(3) in each case at least one of the balancing weights (9.1 - 9.4) are assigned.

6. Device according to one of claims 1 to 5, characterized in that the mass balance device has an additional balance shaft (22) with a circumferential eccentric mass (23) or with two offset by 90 ° to each other rotating eccentric masses (23.1, 23.2).

7. Device according to one of claims 1 to 6, characterized in that the phase adjustment device (36) has two crankshafts (5.1, 5.2) of the crank mechanisms (4.1, 4.2) associated actuating motors (34.1, 34.2) and that the balance shaft (22) symmetrical to the crankshaft (5.1, 5.2) is arranged.

8. Device according to one of claims 1 to 6, characterized in that the horizontal engine (10) has at least one separate crank drive (11 -1) and that at least one further balancing mass (16.1) is provided, the crank drive (11.1) of the horizontal engine (10) is assigned and offset by an angle in the range of less than 180 ° to an eccentric (13.1) of the crank drive (11.1) is arranged.

9. Apparatus according to claim 8, characterized in that the compensating mass (16.1) offset by the angle of 90 ° to the eccentric (13.1) of the crank drive (11.1) is arranged and that a second balancing mass (16.2) by the angle of 180 ° offset from the eccentric (13.1) of the crank drive (11.1) is arranged.

10. Apparatus according to claim 8 or 9, characterized in that the horizontal engine (10) by two synchronously revolving crank drives (11.1, 11.2) is formed and that each of the crank mechanisms (11.1, 11.2) at least one of the balancing weights (16.1, 16.2) assigned are.

11. The device according to claim 10, characterized in that the crank mechanisms (11.1, 11.2) of the horizontal engine (10) are driven in opposite directions and that the phase angles of the two crank mechanisms (11.1,

11.2) are designed to adjust a stroke adjustable.

12. The apparatus of claim 10 or 11, characterized in that the horizontal engine (10) has a coupling gear (17), which is the

Connection between the crank drives (11.1, 11.2) and the needle bar (1) forms.

13. Device according to one of claims 1 to 12, characterized in that the crank drives (4.1, 4.2, 11.1, 11.2) each have a driven crankshaft (5.1, 5.2, 12.1, 12.2) or eccentric shaft and a connecting rod connected via a connecting rod with the crankshaft or eccentric shaft connecting rod (7.1, 7.2, 14.1, 14.2).

14. The apparatus according to claim 13, characterized in that the compensating mass (9.2) or the balancing weights (9.1 - 9.4, 16.1, 16.2) on the crankshaft (5.1, 5.2, 12.1, 12.2) or eccentric shaft are arranged.