EP0803001B1 - Alternating actuation device, and needling machine provided therewith - Google Patents

Abstract

PCT No. PCT/FR96/00053 Sec. 371 Date Aug. 11, 1997 Sec. 102(e) Date Aug. 11, 1997 PCT Filed Jan. 12, 1996 PCT Pub. No. WO96/21764 PCT Pub. Date Jul. 18, 1996The needling machine includes a support and a stripper defining a path for a lap. A needle board supported by sliding rods has a reciprocating motion between the represented maximum penetration position and the withdrawal position by means of two rod-eccentric devices, each having a rod hinged to the sliding rod. Each pair of rods is hinged to a crankshaft supported by bearings and carrying an equilibration device. The bearings are supported in a crankcase by partitions in a position situated axially between the eccentrics and the equilibration device. The crankshaft extends from the crankcase through simple sealing liners. An advantage of the present needling machine is that the crankcase is stiffened and crankshaft deformations are reduced to increase the striking rate.

Description

The present invention relates to a device alternative actuation for needling machine.

The present invention also relates to such needling machine thus equipped, used to consolidate mechanically a sheet of fibers, for example from a lapper spreader.

Known needling machines have a support called a board on which needles are attached. Of alternative actuating devices with connecting rods and cranks, communicate to the board a movement alternative so that the needles cross the sheet of fiber at a rate that can go into production of 1000 at 2000 rounds per minute.

Additional devices also allow to regulate the flow of fibers entering and leaving the machine with or without stretching and at selected speeds according to the rate of strike in number of strokes per minute, equivalent of the number of movements alternating needles per minute.

DE-A-1 660 778 describes a device actuation in which a crankshaft supported by four levels drives the needle board in reciprocating through two connecting rods. There is a landing on either side of each connecting rod, schematically and without corresponding description.

DE-A-2 111 496 describes successive crankshafts arranged along an upper beam of the needling machine. Each end of the crankshaft is supported by a bearing. In another provision, crankshafts, parallel instead of aligned, are arranged transversely to the beam. Considering the limited width of the beam, the bearings are brought back towards the middle and are thus positioned between a central balancing means and each eccentric of connecting rods.

These known devices operate in the open air and are lubricated with grease.

We still know actuation devices mounted in a sealed housing and lubricated with oil. In this case the crankshaft, oriented along the width of the tablecloth to be needled, is supported in rotation by two bearings mounted in openings provided in two opposite end walls of the housing. Between the two bearings, the crankshaft has two eccentrics forming a crank and each connected to a connecting rod actuation, and supports means for balancing the inertia and / or counterweight type. Through each of bearings, the crankshaft comes out of the housing to be connected to a power source and / or another coaxial crankshaft, belonging to another actuation device.

Known actuating devices are subject to high alternating loads, generating vibrations dangerous and noise. The strength to do getting the needles into the tablecloth is important. This leads to generously size the parts mobile alternative actuation devices. It results in large inertial forces intermittent force of penetration and extraction needles, and that the actuating devices in back and forth are subject to substantial constraints and mechanical deformations. Ultimately, we must limit the rate of typing.

The object of the invention is to increase the rate of strike permitted to needling machines and / or to reduce adverse effects of alternating charges for a rate given.

According to a first aspect of the invention, the actuating device for needling machine comprising a casing in which at least one crankshaft is rotatably supported by at least two bearings, the crankshaft with two eccentrics to each which is hinged one end of a connecting rod intended to be connected by its other end, at least indirectly, to a needle board, means being also fixed to the crankshaft, is characterized in that the two bearings are supported at inside the housing in an axially located position between the two eccentrics, in that the means balancing are located axially between the two bearings, and in that each eccentric is located between the respective one of the two bearings and a wall housing peripheral.

So the distance between the two bearings is reduced, and this greatly reduces the deformation in bending of the crankshaft.

In addition, the bearings are supported closer one on the other side in the housing, which increases rigidity of their mutual positioning, and therefore reduced again the deformations allowed at the crankshaft. The bearing supports that it is, according to the invention, necessary to provide inside the housing, can be designed as interior reinforcements for the casing.

In particular, these supports can be produced in the form of internal walls or partitions which brace the outer walls of the housing.

Thanks to the invention, the deformations generated by the striking and inertia forces in the device are considerably reduced, the mechanical reliability is increased, vibrations are lower, and therefore the strike rate may be increased.

• des moyens pour faire défiler la nappe de fibre selon un plan de défilement,
• un support de planche à aiguilles,
• des moyens d'actionnement pour actionner mécaniquement le support de planche à aiguilles en va et vient selon une direction transversale au plan de défilement,

est caractérisée en ce que les moyens d'actionnement comprennent au moins un dispositif selon le premier aspect de l'invention.According to a second aspect of the invention, the needling machine for mechanically consolidating a sheet of fibers, comprising:

• means for scrolling the fiber web according to a running plane,
• a needle board support,
• actuating means for mechanically actuating the needle board support back and forth in a direction transverse to the running plane,

is characterized in that the actuating means comprise at least one device according to the first aspect of the invention.

Other features and advantages of the invention will emerge from the description below, relating to nonlimiting examples.

• la figure 1 est une coupe schématique partielle de face, d'une aiguilleteuse selon l'invention, la moitié droite de la figure correspondant à une variante ;
• la figure 2 est une vue suivant II-II de la figure 1 ;
• la figure 3 est une vue de détail d'un palier, avec visualisation simultanée de deux variantes ;
• la figure 4 est une vue d'un détail du vilebrequin; et
• les figures 5 et 6 sont des vues analogues aux figures 3 et 4 respectivement, mais relatives à une autre famille de variantes.

In the accompanying drawings:

• Figure 1 is a partial schematic front view of a needling machine according to the invention, the right half of the figure corresponding to a variant;
• Figure 2 is a view along II-II of Figure 1;
• Figure 3 is a detail view of a bearing, with simultaneous viewing of two variants;
• Figure 4 is a view of a detail of the crankshaft; and
• Figures 5 and 6 are views similar to Figures 3 and 4 respectively, but relating to another family of variants.

The needling machine shown in Figures 1 and 2 includes a generally horizontal perforated table 1 and a retaining plate 2, also called "stripper", placed approximately parallel to a certain distance above table 1. Table 1 and stripper 2 define a path between them in a plane substantially horizontal for a sheet of fibers 3. The stripper 2 includes perforations aligned with those of table 1. At the entrance of the journey are placed introducer means 4 (FIG. 2) shown diagrammatically under the shape of a pair of motor rollers between which passes the tablecloth 3. At the end of the path, the tablecloth 3 consolidated and compacted by needling is driven by extractor means 6 also shown schematically by two motor rollers between which the tablecloth passes.

The stripper 2 is placed between the path of the tablecloth 3 and a series of needle boards 7. The needle boards 7 are arranged in two rows which follow one another in the direction of travel of the tablecloth 3 (Figure 2). In each row, the planks needles 7 are aligned along the width of the tablecloth 3 (Figure 1).

Each plate 7 carries on the side of the stripper 2 a large number of needles 8 oriented perpendicularly in the plane of the path of the sheet 3, with their point directed towards the web 3. Each needle is positioned opposite a perforation in stripper 2 and a corresponding perforation of table 1. Each board with needles 7 is fixed, on the side opposite needles 8, to a support 9 itself fixed to the end of two rods 11 sliding climbs each along an axis 12 parallel to needles 8 and perpendicular to the plane of path of the sheet 3. The rods 11 associated with the boards of the same row are located in the same plane perpendicular to the direction of travel of fibers. For its sliding guide, each rod 11 is guided in two stages of sliding coaxial 13 and 14, axially spaced. The bearings 13 and 14 are made integral with a casing waterproof 16 which will be described later. Landings 13 and 14 include, for example, anti-friction rings 17 for contact with the rod 11. The bearings 14 are tracked in the direction of support 9, by means not shown ensuring the housing is sealed around each rod 11.

Each mobile unit made up of two rods sliding 11, and support 9 and board 7 associates is animated in service of an alternative movement back and forth in direction 12 between a position 7a (FIG. 2) in which the end of the needles, designated in this case by 8a, crosses the stripper 2, tablecloth 3 and table 1, and a release position 7b in which the needles 8 are completely released at least from table 1 and table 3, and possibly the stripper 2.

To communicate this back and forth movement to the moving element, the rod 11 is articulated by a articulation 18 at one end of a connecting rod 19 of which the other end is connected by a hinge 21 to an eccentric 22 belonging to a crankshaft 23 rotated by non motor means represented.

As shown in Figure 1, there is a crankshaft 23 for each support 9. The associated crankshafts 23 supports 9 of the same row are coaxial and coupled in rotation about their common axis 24 by coupling devices 26. Devices 26 are of a known type capable of transmitting a strong couple of rotation, substantially without angular play around axis 24, while admitting that the crankshafts 23, at instead of being strictly coaxial, form a slight angle one to another. So each crankshaft 23 can work in bending independently of the two crankshafts 23 to which it is coupled by the coupling devices 26.

At one end of each row of planks with needles, the corresponding crankshaft 23 is coupled at least indirectly to a motor drive (not shown), and at the other end of the row, the corresponding crankshaft 23 has a free end.

There are therefore two rows of crankshafts 23, one for each row of needle boards, like this is illustrated in Figure 2.

The simultaneous observation of Figures 1 and 2 shows that the machine has as many housings 16 as there are of needle boards 7 in one of the rows. Each casing 16 rotatably supports two crankshafts 23 of which the axes 24 are parallel and which are associated with two needle boards 7 located side by side and each belonging to one of the rows. Each crankshaft 23 (figure 1) carries balancing means 27 with inertia to stabilize the rotational movement and possibly counterbalanced to counterbalance the equivalent eccentric mass which is rotating around of the axis 24 of each crankshaft. Ways balancing 27 are known per se.

The housings 16 are fixed to a frame 28 of the needling machine, shown schematically and partially in Figure 2 and can also support fixed or adjustable table 1, the stripper 2 and introducer devices 4 and extractors 6. Each casing 16 is composed of two partial housings 29 and 31 respectively forming bodies and cover. Partial housings 29 and 31 are fixed to each other according to a joint plane 32 containing the geometric axes 24 of the two crankshafts 23.

Sliding guides 13 and 14 for rods 11 are supported by the body 29. The cover 31 closes the body 29 on the side opposite the rods sliding 11.

Each crankshaft 23 has two bearings cylindrical 32 each located between a respective one of eccentrics 22 and a central area 33 on which are fitted the balancing means 27. Each cylindrical seat 32 cooperates with a rolling bearing 34 respectively supported by the housing 16. Each eccentric is located axially between one of the bearings 34 on the inside of the housing 16 and a device seal 36 which ensures the seal between the crankshaft 23 and an orifice 37 in the peripheral wall of the casing 16, through which the crankshaft 23 extends outwards from the housing 16, to the device neighbor 26. Each orifice 37 is defined jointly by the two partial housings 29 and 31, which each have a corresponding half-bore. The orifices 37 are deprived of bearing. Housing 16 encloses so, tightly, for each of the two associated crankshafts 23, the two eccentrics, the two bearings, the balancing means 27, both connecting rods 19 and the two joints 18. The assembly is lubricated with oil retained inside the housing thanks to the tightness of it.

To support the bearings 34, the casing 16 comprises support means 38. In the example illustrated by left part of the casing 16 shown in FIG. 1, which corresponds to the example shown in Figure 2, the support means 38 include for each pair of 34 coplanar bearings, a partition 39 formed of a single block in the body 29 of the casing 16. The partition 39 is connected to the front and rear walls 41 of body 29 as well as to the bottom wall 42 of the latter, thus forming stiffening spacer between these walls 41 and 42.

As shown in more detail in Figure 3, the wall 39 has in its free edge 43 located in the parting line 32, for each of the two bearings coplanar 34, a semi-circular notch 44 of which the diameter corresponds to the outside diameter of the bearing 34. According to a first embodiment illustrated by the left half of Figure 3, the bearing 34 is retained in the notch 44 by a cap 46 having a face semicircular interior 47 of the same diameter applying to the rest of the periphery of the bearing 34. The cap 46 is fixed by two opposite ears 48 against the free edge 43 of the partition 39, by means of screws 49.

In an alternative embodiment shown in dashed line in the left part of Figure 3, notch 44, instead of being carried by partition 39 can be carried by a cradle 51 fitting into a larger notch 52 formed in the free edge 43 of the partition 39. The cradle 51 has two ears opposite 53 (only one of which is visible in FIG. 3). Each screw 49 passes through one ear 48 of the cap 46 and a corresponding ear 53 of the cradle 5i, and squeezes these two ears stacked against the top edge notch of the partition 39.

According to a third embodiment illustrated in right part of Figures 1 and 3, and which will not be described that for its differences from the first mode of realization, there is a second partition 54 which belongs to the cover 31 of the casing 16. A free edge 56 of the partition 54 is located in the joint plane 32 so as to be adjacent to the free edge 43 of the partition 39 when the two partial housings 29, 31 are assembled together.

The edge 56 of the partition 54 presents for each of the two coplanar bearings 34 a semicircular notch 57 of the same diameter as the notch 44 of the partition 39. When the two partial housings 29, 31 are joined together, the notch 57 comes match with notch 44 to form a circular bezel rigorously positioning the bearing 34.

In the schematic representations in Figures 1 and 2, the eccentrics 22 are shown with a relatively strong offset, to make the designs clearer.

In practice, the back and forth stroke necessary for the needle boards 7 being only a few centimeters, a much smaller offset is sufficient and an embodiment of the type shown diagrammatically in FIG. 4 is then advantageous. The diameter D ₁ of the bearing 32 is greater than the diameter D ₂ of the eccentric 22 so that the bearing 34 can, in a first stage of its assembly, reach position 34a by fitting from the corresponding end of the crankshaft 23, that is to say located on the same side of the balancing means 27 as the bearing 34 being installed. To allow the bearing 34 to reach the position 34a, it is provided, for example, as shown, that the diameter D ₃ of the end of the crankshaft 23 is sufficiently small so that the peripheral wall of the eccentric 22 is everywhere radially projecting compared to this end.

If the eccentric 22 was directly adjacent to the bearing 32, the passage of the bearing 34 from the position 34a to the service position on the bearing 32 would require that the diameter D ₁ is at least equal to the diameter D ₂ of the eccentric 22 increased by twice the eccentricity E of the eccentric 22. So that the minimum necessary diameter D ₁ for the bearing 32 can be less than this value, there is provided between the eccentric 22 and the bearing 32 a transition zone 58 which, in an angular region 58a, is radially set back relative to the region 22a where the periphery of the eccentric 22 is the most distant from the axis 24 of the crankshaft 23. The maximum radial size M of the eccentric 22 and of the transition region 58 considered together is less than the diameter D ₁ of the bearing surface 32. This allows the bearing 34 to pass from position 34a to a position 34b around the transition region 58, whose axial dimension L is greater at this lle of the bearing 34. The transition region 58 is for example made in the form of a cylinder having with respect to the axis 24 an eccentricity "e" less than the eccentricity "E" of the eccentric 22. The eccentricities "e" and "E" are oriented in the same radial direction from the axis 24. The periphery of the transition region 58 is everywhere radially set back relative to the bearing 32, so that the bearing 34 can without difficulty being fitted on the bearing 32 from position 34b. To avoid unnecessarily creating regions of weakness on the crankshaft 23, the transition region 58 has as large a diameter as possible. As a result, the transition region 58 has an angular region 58b which is radially projecting from the region 22b where the periphery of the eccentric 22 is closest to the axis 24 of the crankshaft.

The central zone 33 of the crankshaft 23 has a diameter D ₄ greater than the maximum radial size N of the eccentric 22 and the bearing 32 considered together, which allows, before the fitting of the bearing 34, to be fitted without difficulty the balancing means 27 from the end of the crankshaft 23 even if, as shown, the axial dimension of the balancing means 27 is greater than the axial dimension L of the transition region 58. The bearing 34 is retained axially between a shoulder 59 separating the bearing 32 and the central zone 33, and an elastic stop ring 61.

In the example of FIGS. 5 and 6, which will only be described for its differences from that of FIGS. 3 and 4, the rolling bearing 34 is replaced by a plain bearing 34 comprising two semi-cylindrical bearings 64 which can be fixed one in the notch 44 of the wall 39 or of the cradle 51, the other in the notch 57 of the cap 46 or of the wall 54. The mounting resembles that of the connecting rod bearings of a heat engine cylinders and pistons, for the connection between the connecting rods and the engine crankshaft. In particular, the mounting of the bearing requires no fitting from the ends of the crankshaft. Thus, the bearing 32 can, as shown, be radially recessed with respect to other regions of the crankshaft, located axially on either side of the bearing 32, without this resulting in impossibility of mounting. The transition region 58 is deleted. Axial stops not shown can ensure the axial positioning of the crankshaft 23, but this is not essential since in theory the crankshaft does not undergo any axial load. As in the previous example, the diameter D ₄ of the central region 33 of the crankshaft 23 is at least equal to the maximum radial size N that the balancing device 27 must cross by fitting from the end of the tree.

Of course, the invention is not limited to examples described and shown.

In the examples where there is only one partition interior such as 39 to support each landing, this partition could be secured to the cover of the casing instead of being integral with the casing body as this has been described.

To allow the mounting of the bearing and the means balancing without resorting to the solution advantageous described with reference to Figure 4, we could make the crankshaft in the form of two half crankshafts fixed to each other in the region of the central zone 33 after fitting the bearing and the balancing means from the central zone 33, which would have a diameter at most equal to that of the bearing 32.

We could also, from a realization according to Figure 4 or Figure 6, make each device balancing 27 in two parts fixed to each other along a substantially axial joint plane, to avoid the need for fitting by fitting.

In this case, the diameter of the central region 33 of the crankshaft can be freely chosen in relation to other diameters of the crankshaft.

Claims (15)

1. Needling machine actuation device comprising a crankcase (16) in which at least one crankshaft (23) is supported in rotation by at least two bearings, the crankshaft comprising two eccentrics (22) with each of which is articulated one of the ends of a connecting rod (19) intended to be connected at its other end, at least indirectly, to a needle board (7), equilibration means (27) furthermore being attached to the crankshaft (23), characterized in that the two bearings (34) are supported inside the crankcase (16) at a position situated axially between the two eccentrics (22), in that the equilibration means (27) are situated axially between the two bearings (34), and in that each eccentric (22) is situated between the respective one of the two bearings (34) and a peripheral wall of the crankcase (16).
2. Device according to Claim 1, characterized in that at least one of the eccentrics (22) is situated axially between the respective one of the bearings (34) and a sealing device (36) fitted in an orifice (37) of the crankcase (16) traversed by the crankshaft (23) without being supported there (23).
3. Device according to one of Claims 1 or 2, characterized in that the crankshaft (23) comprises for each bearings (34) a bearing surface (32) having a diameter (D₁) greater than the diameter (D₂) of the closest eccentric (22), but less than the diameter (D₂) of the eccentric increased by twice its off-centring (E), and in that the crankshaft (23) comprises between each bearing surface (32) and the closest eccentric (22) a transition zone (58) which is radially recessed with respect to a region (22a) where the distance between the periphery of the eccentric and the axis (24) of the crankshaft (23) is the greatest.
4. Device according to Claim 3, characterized in that the transition zone (58) is radially protruding with respect to a region (22b) where the distance between the periphery of the eccentric (22) and the axis (24) of the crankshaft (23) is smallest.
5. Device according to Claim 3 or 4, characterized in that the transition zone (58) is off-centred with respect to the axis (24) of the crankshaft (23).
6. Device according to one of Claims 3 to 5, characterized in that the equilibration means (27) are fitted over a central zone (33) of the crankshaft (23), and in that the diameter (D₄) of the central zone (33) is at least equal to the maximum radial dimension (N) of the eccentric (22) and of the bearing surface (32) considered together.
7. Device according to Claim 6, characterized in that the equilibration means (27) have a greater axial dimension than that of the transition zone (58).
8. Device according to Claim 1 or 2, characterized in that the bearings are of the plane type each comprising two semi-cylindrical bushes (64).
9. Device according to one of Claims 1 to 8, characterized in that the crankcase (16) comprises two partial crankcases (29, 31) attached to each other and in that one of the partial crankcases comprises internal partitions (39, 54) having free edges (43, 56) which have recesses (44, 57) forming bearing housings, the bearings (34) being fitted in these housings and in bearings caps (46) attached to the internal partitions (39, 54) opposite the recesses.
10. Device according to one of Claims 1 to 8, characterized in that the crankcase (16) comprises two partial crankcases (29, 31) attached to each other and comprising at least one pair of internal partitions (39, 54) defining between them at least one housing for fitting the respective one of the bearings (34).
11. Device according to one of Claims 1 to 8, characterized in that the crankcase (16) comprises two partial crankcases (29, 31) attached to each other, in that one of the partial crankcases comprises internal partitions (39), and in that for the fitting of each bearing a bearing cradle (51) and a bearing cap (46) are attached to a free edge (43) of each internal partition (39).
12. Device according to one of Claims 1 to 8, characterized in that the bearings (34) are supported by internal partitions (39, 54) of the crankcase (16) which form braces between outer walls (41, 42) of the crankcase (16).
13. Device according to one of Claims 1 to 12, characterized in that it comprises for each connecting rod (19) a rod (11) articulated with the said other end of the connecting rod and slidingly mounted in slide guides (13, 14) supported by the crankcase (16), each rod (11) being intended to connect one of the connecting rods (19) with the needle board (7).
14. Needling machine for mechanically consolidating a fibre fleece, comprising:

    means (1, 2, 4, 6) of causing the fibre fleece (3) to move in a plane of motion,

    a needle board support (9),

    actuation means for mechanically actuating the needle board support (7) in a reciprocating manner in a transverse direction with respect to the plane of motion,

    characterized in that the actuation means comprise at least one device according to one of Claims 1 to 13.
15. Needling machine according to Claim 14, characterized in that the actuation means comprise several actuation devices aligned in the direction of the width of the fleece, and whose crankshafts (23) are coupled by couplings (26) accepting an angular deflection between the successive crankshafts.

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