WO1996011294A1

WO1996011294A1 - Double striking needle loom

Info

Publication number: WO1996011294A1
Application number: PCT/FR1995/001311
Authority: WO
Inventors: Yvon Le Roy
Original assignee: Laroche S.A.
Priority date: 1994-10-10
Filing date: 1995-10-09
Publication date: 1996-04-18
Also published as: EP0786027B1; AU3657395A; FR2725458B1; DE69505005D1; FR2725458A1; ATE171485T1; EP0786027A1; DE69505005T2

Abstract

A path is defined for a lap (7) between a table (8) and a stripper (9). Introduction (17) and extraction (18) means feed the lap (7) in a plane (P) and in a direction (D). Two lower (19) and upper (21) needle boards are reciprocatingly driven so that the needles (22, 23) penetrate repeatedly into the lap (7) through openings (24, 26) provided in the table and in the stripper. In order to drive reciprocatingly the needle boards (19, 21), common crank means (41, 42) are provided on the same side of the lap (7) and transmit the reciprocating motion to the board (21) situated on the other side of the lap through a mechanical linkage (33) passing on either side of the edges of the lap. Utilisation for simplifying the fabrication and reducing the cost of needle looms particularly in small and medium width.

Description

"Double impact needling machine" DESCRIPTION The present invention relates to a double impact needling machine. We know that a needling machine is a machine in which a sheet of fibers is scrolled, for example from a lapper spreader, while a board provided with many parallel needles is actuated back and forth, so that the needles enter the water table and come out at a rate that can range from a few hundred to about two thousand strokes per minute. This operation has the result of consolidating the web by intertwining the fibers that compose it. By "double impact needling machine" is meant a needling machine comprising at least two needle boards each located opposite one of the faces of the web path, so as to carry out the needling operation from both sides of the tablecloth.

For double impact needling machines, it is usual to provide two back and forth mechanisms, each located opposite one of the faces of the path, with cranks actuated in rotation from a common motor, by means of many trees and corner drives.

The object of the present invention is to produce a double impact needling machine which is less costly to produce and whose synchronization between needle boards is better, thanks to a shorter mechanical connection between the two boards, in particular for needling machines for small and medium tablecloth width.

According to the invention, the double impact needling machine, comprising a frame, means for guiding at least one ply along a travel path, two supports each located opposite a respective face of the travel path and intended to each support a needle board, means for guiding each support in displacement in a strike direction transverse to the faces of the travel path, means for driving said supports back and forth in the strike direction with a relative movement between them, is characterized in that the drive means back and forth are grouped opposite a first face of the path turned towards a first of the two supports, and in that there is provided between the drive means back and forth and the second support a mechanical connection which extends laterally relatively said journey.

Thus, all of the drive means are common to the two needle boards from the drive source and at least to the back and forth drive means, which are grouped opposite the same face of the path. It is therefore particularly simple to establish by the drive means back and forth, for example of the crank type, any desired phase shift between the two needle boards, and this with very reduced mechanical clearances. In particular, in certain embodiments, the crank means may quite simply comprise two cranks integral with one another. The realization is therefore considerably simplified. Synchronization is ensured in a much more direct way between the two needle boards. In addition, on the side of the path which is opposite to the crank means, the structure of the needling machine is less stressed than in known embodiments where there is a rod-crank assembly on each side of the path of the web. According to another of its aspects, the invention is applicable for connecting the two supports independently of each other to the reciprocating drive means while giving each board a movement coordinated with respect to the other board . By "independently" is meant that the two board supports are not directly fixed to each other. "Coordinated movement" means any movement synchronized in a defined manner, including the absence of movement relative between the two boards. The invention then has the advantage that a simple change of crank, or even a simple adjustment of angular setting between two distinct but coaxial cranks makes it possible to operate the needling machine in simultaneous strike, alternate strike or offset strike.

Other features and advantages of the invention will emerge from the description below, relating to non-limiting examples. In the accompanying drawings:

- Figure 1 is an elevational view of a first embodiment of the needling machine according to the invention, with section along the plane I-I of Figure 2; - Figure 2 is a view of the needling machine of Figure 1, along the line II-II of Figure 1;

- Figure 3 is a schematic perspective view of certain parts of the needle loom of Figures 1 and 2; - Figure 4 and a schematic view corresponding to a part of Figure 3, but relating to a second embodiment;

- Figure 5 is a view similar to Figure 3 but relating to a third embodiment; - Figure 6 is a view similar to Figure 5, but with parts broken away and relating to a fourth embodiment; and

- Figures 7 and 8 are partial schematic views, in perspective, of a fifth and a sixth embodiment of the invention.

In the example shown in Figures 1 to 3, the needling machine comprises a frame 1 essentially consisting of two side walls 2, vertical and parallel connected to each other by three plane struts, parallel and horizontal, namely a spacer lower 3, a middle spacer 4 and an upper spacer 6. A needling path is defined in a horizontal plane P and in a direction D for the ply 7 to be needled, between a needling table 8 arranged horizontally under said path and an upper plate or "stripper" 9 arranged parallel to the table 8 at a certain distance above it. The table 8 is rigidly supported by the central spacer 4 by means of a height adjustment means 11. The stripper is rigidly supported by the upper spacer 6 by means of a height adjustment means 12 .

As shown more particularly in Figure 2, each height adjustment means 11, 12 comprises two screw jacks 13 oriented vertically and whose nuts (not shown), each mounted in rotation in a housing 14, are actuated by a screw common end 16.

The sheet of fibers 7 is driven in scrolling along the needling path by an introduction device 17 and an extraction device 18, each shown diagrammatically by a pair of cylinders rotating in opposite directions and between which the sheet passes.

L ¹ needle loom further comprises a lower needle board 19 located under the table 8 and an upper needle board 21 located above the stripper 9. Each board 19, 21 includes a large number of needles 22 and 23 respectively oriented transversely to the plane P with their point directed towards the ply 7 when the planks 19, 21 are in the withdrawal position shown in FIGS. 1 and 2.

By means which will be described in detail below, the needle boards 19, 21 are each moved back and forth in a needling direction A perpendicular to the plane P, between the withdrawal position shown in Figures 1 and 2 to a position of penetration into the ply 7 through openings or perforations 24 and 26 of the table 8 and respectively of the stripper 9. For its back and forth drive, each needle board 19, 21 is fixed to a support 27 and respectively 28. The lower support 27 is rigidly fixed to two sliding columns 29 (see also FIG. 3) mounted vertically, laterally on the side and across the path for the web 7. Similarly, the upper support 28 is fixed to two vertical sliding columns 33 located laterally on either side of the path for the web 7. Each column 29 or 33 is guided in vertical sliding in a sliding bearing 34 through the central spacer 4 and 35 through the upper spacer 6.

The columns 29 associated with the lower needle board 19 have their axes located in the same vertical plane Q perpendicular to the direction D of travel of the web 7. Relative to the direction D, the plane Q is located downstream of a plane R also perpendicular to direction D and in which the axes of the two columns 33 associated with the upper needle board 21 are located.

As shown in Figures 2 and 3, a beam 36 rigidly connects the columns 29 to each other by their lower end. Likewise, the columns 33 associated with the upper board 21 are rigidly connected to one another by their lower end, by means of a beam 37. The beams 36 and 37 are located between the lower spacer 3 and 1 'middle spacer 4 and extend parallel to the width of the path for the ply 7. In the middle of each beam 36, 37 is articulated one of the ends of a respective connecting rod 38, 39 extending downward from of the beam.

The connecting rods 38, 39 are articulated by their other end each to a respective crank 41, 42 produced in the form of a crank pin or pin 43 formed in an eccentric position on a free end of a respective shaft 44 supported in rotation in a bearing respective 46. The axes of articulation of the two ends of the two connecting rods 38, 39 are parallel to the direction D of travel of the ply 7, which allows the connecting rods 38 and 39 to oscillate in the planes Q and R respectively. The two cranks 41, 42 have a common axis of rotation S parallel to the direction D of travel of the ply 7. In the example, the two cranks 41, 42 are integral with one another as well as with a common drive pulley 47 on which circulates a toothed belt 48 for connection with a drive pulley 53 (FIG. 2) mounted for example on the shaft of an electric motor 51. The pulley 47 is located axially between the two shafts 44, midway between the planes Q and R. The housings 49 in which the bearings 46 are mounted are fixed on the upper face of the lower spacer 3.

The two pins 43 are angularly offset by 180 ° around the axis S of the cranks 41 and 42, so that the needle boards 19 and 21 have a relative movement with respect to each other as they are both at the same time in the retracted position as shown in Figures 1 and 2, then, after a 180 ° rotation of the cranks, both at the same time in the penetrating position as shown in Figure 3. This corresponds to the operation in simultaneous strike. One could also obtain the alternating strike operation by making the two coaxial pins 43, so that each board is in the position of maximum withdrawal when the other is in the position of maximum penetration. One could also obtain an offset strike operation, with an angular offset different from 0 ° and 180 ° of the pins 43 around the axis S of the cranks 41 and 42.

In the example shown in Figure 4, the two cranks 41, 42 are always coaxial along the axis S, but they are free to rotate relative to each other, each having its own pulley 47 on which circulates a respective belt 48 or 148. The belt 48 is connected directly to the shaft of a motor 51. The other belt 148 rotates the crank 41 with a pulley 153 which is the same diameter as the pulley 53 mounted on the motor shaft 51. The pulley 153 is connected to the motor shaft 51 via a pair of pinions 54 which reverse the direction of rotation without changing the speed.

Thus, the two cranks 41 and 42 rotate in opposite directions to one another. Originally, the two pins 43 are made to be offset by 180 ° relative to each other around the S axis each time their center passes in the vertical plane containing the S axis, so as to fulfill the operating conditions for simultaneous striking. By this operation in opposite direction of the two cranks, it eliminates or reduces certain reaction torques which, in the example of Figures 1 to 3 are transmitted to the frame of the machine. These couples result from the fact that in the example of FIGS. 1 to 3, the forces applied to the two moving sets back and forth have, at certain stages of the cycle, lines of action very distant from each other.

The example of FIG. 5 will only be described for its differences from that of FIGS. 1 to 3. There is between each pair of columns 29, 33 situated on the same side of the path of the ply a reversing pinion of movement 56 mounted in rotation along an axis T parallel to the width of the ply. Each pinion 56 meshes in two diametrically opposite positions with two racks 57, 58 formed over a certain length of the columns 29 and 33 respectively of the pair considered, from their lower end.

The two pinions 56, each located on a respective side of the path of the web, are rigidly connected to each other by a shaft 59 supported in rotation along the axis T relative to the frame of the needling machine. The shaft 59 rigidly carries a lever 61 midway between the pinions 56. A connecting rod 62 has one end articulated to the lever 61 and another end articulated to a crank 63 driven in continuous rotation by an electric motor 64. The radius of gyration G of the articulated end 66 of the connecting rod 62 around the axis T is larger than the radius of gyration "g" of its other end 67 around the axis S of the crank 63. Thus, the continuous rotation of the crank 63 produces an angular back and forth movement of the lever 61 and therefore pinions 56. This results in a back and forth movement of the columns 29 and 33 in the direction of impact. The movement of the columns 29 is always opposite to that of the columns 33, as is symbolized by the arrows FI and F2. In the example of FIG. 6, which will only be described for its differences from that of FIG. 5, each movement reversing pinion 56 is replaced by a lever 76 fixed in its middle to the shaft 59 and the two ends of which opposite 77 are each articulated at one end of a link 78. The other end of each link 78 is articulated at the movable end of a respective compensating arm 79 whose fixed end is articulated to the frame of 1 needling machine. The center distance E of each arm 79 is equal to the distance H between each axis of articulation of the lever 77 and its axis of rotation T. Halfway between its axes of articulation with the lever 76 and the arm 79 , each link is articulated along an axis U to a respective one of the columns 29 and 33. The arrangement is such that halfway back and forth, the two links 78 are substantially vertical, while the lever 76 and the arms 79 are substantially horizontal. From each link 78, the associated arm 79 extends in the opposite direction to the lever 76. This fully articulated structure not only ensures the back and forth drive of the columns 29 and 33, but also a vertical guidance almost perfect for the U axes. This can make it possible to eliminate the bearings 34 or the bearings 35.

The example of FIG. 7 will only be described for its differences from that of FIG. 6. A first difference consists in that the drive mechanism 83 back and forth from the columns 29 and 33 is located above the plane of travel of the tablecloth to be needled, and no longer below it.

A second difference, independent of the first, lies in the modified structure of the mechanism

83 to rotate the shaft 59 back and forth rotating the reversing levers 76 now located in the upper position.

The mechanism 83 comprises a movement transforming member 161 having one end shaped as a yoke 162 articulated to the shaft 59 along an axis 163 perpendicular to the axis of rotation T of the shaft 59. In the vicinity of its opposite end, the motion transformer member 161 is articulated to a drive shaft 164 along an axis 166 which is perpendicular and eccentric with respect to the axis of rotation 167 of the drive shaft 164. The axis of rotation 167 of the shaft 164 cuts l hinge axis 163 and the axis T of the shaft 59. In the example, the three axes T,

163 and 167 are concurrent at a point of intersection W.

The operation of this back and forth drive mechanism 83 is as follows: when the motor shaft

164 is in continuous rotation, the movement transforming member 161 describes a cone C1 and this produces for the shaft 59 an angular back and forth having for amplitude the angle at the top of the cone C1.

In the example shown, the mechanism 83 comprises two means for adjusting the angular travel of the shaft 59. The first adjustment means makes it possible to move the motor shaft 164 along its own axis 167 as illustrated by the double arrow 168. In addition, the movement transforming member 161 is made in two parts, one of which is a socket 169 articulated at the shaft 164 along the axis 166, and the other is a shaft 171 carrying the yoke 162 and sliding freely in the socket 169 along an axis 172 which is oblique to the axis 167 of the tree 164. Thus , when the shaft 164 is moved along the double arrow 168, the bushing 169 slides on the shaft 171 and this varies the angle at the top of the cone described by the movement transforming member 161. For example, if the 'shaft 164 is moved along arrow 168 to approach the shaft 59, the member 161 can come to describe the cone C2 having a greater angle at the top than the cone C1.

In addition, a second adjustment means makes it possible to adjust the orientation of the drive shaft 164 around the axis of rotation T of the shaft 59, as illustrated by the arrows 173. Thus, for a given angular stroke of the shaft 59 and therefore for a given stroke of the needle boards, the height position of the needles can be selected when they are in the maximum penetration position and respectively in the maximum withdrawal position relative to the ply to be needled.

The example of FIG. 7 also presents a third difference independent of the previous two compared to the example of FIG. 6. More particularly, the columns 29 and 33 are no longer sliding, but guided only by articulations in their travel. comes and goes vertical.

For this, the lower ends of the columns 29 and 33, opposite the shaft 59, are also each articulated with the middle of a link 88, one end of which is articulated to a compensating arm 89 and the other end of which is articulated at a respective end of a reversing lever 86. The mounting of the reversing lever 86, the rods 88 and the compensating arms 89 is substantially symmetrical with that of the reversing lever 76 of the rods 78 and the compensating arms 79, with respect to a horizontal plane. Each reversing arm 86 is supported in its center in a bearing 174 which must preferably be resiliently supported since the kinematic study shows that the bearing 174 undergoes vertical movements of the order of a millimeter in service.

The embodiment of Figure 7 has the advantage of completely eliminating the sliding guides (other than those which only undergo relative movement when the machine is adjusted). The example of FIG. 8 will only be described for its differences from that of FIG. 5.

The reversing wheels 56 no longer drive columns 29 and 33 in opposite movements but each cooperate with an endless toothed belt 91 also bypassing upper reversing wheels 96. Between the wheels 56 and 96 each belt 91 has two vertical sections 93 and 99 movable vertically in opposite directions to each other. The supports 27 and 28 of needle boards are fixed one to the sections 99 and the other to the sections 93 of the two toothed belts 93.

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

For machines of very small width, the connection between the crank means and the needle board situated opposite the other side of the web could pass only through one side of the path of travel of the web 7. In this which relates to the sliding guide for the needle board being located opposite the same face of the ply as the crank means, it is not necessary for the guide means to pass through the plane of travel of the ply.

In the example of FIG. 4, an alternating strike or offset strike operation, that is to say an intermediate between the alternate strike and the simultaneous strike, can be carried out. For this, we make sure that the plane in which the axes of the two crank journals are located when they are offset angularly 180 ° is suitably moved away from the vertical plane.

There could be a crank assembly below each pair of columns 29, 33, the two crank assemblies being driven by toothed belts from a common motor.

The crank pins can of course be replaced by eccentric bores receiving pins attached to the connecting rods. In the example of FIG. 7, one could adjust the angle at the top of the cone such as Cl or C2 described by the movement transforming member such as 161 by providing a means for adjusting the eccentricity of the articulation axis. 166 with respect to the axis 167 of the motor shaft 164.

Claims

1. Double impact needling machine, comprising a frame (1), means (8, 9) for guiding at least one ply (7) along a running path, two supports (27, 28) each located opposite a face respective of the travel path and intended to each support a needle board (19, 21), means (34, 35, 78, 79, 88, 96) for guiding each support (27, 28) in displacement in a direction of strike (A) transverse to the faces of the travel path, means (41, 42, 63, 83) for driving said supports

(27, 28) back and forth in the striking direction with a relative movement between them, characterized in that the drive means back and forth (41, 42, 63, 83) are grouped opposite a first face of the path facing a first of the two supports (27), and in that it is provided between the reciprocating drive means (41, 42, 63, 83) and the second support

(28) a mechanical link (33, 93) which extends laterally relative to said path.

2. Double impact needling machine, comprising a frame (1), means (8, 9) for guiding at least one ply (7) along a running path, two supports (27, 28) each located opposite a face respective of the travel path and intended to each support a needle board (19, 21), means (34, 35) for guiding each support (27, 28) in displacement in a striking direction (A) transverse to the faces of the scrolling path, the supports being connected independently of one another to means (41, 42, 63) for driving said supports (27, 28) back and forth in the direction of striking with a movement coordinated with each other , characterized in that the reciprocating drive means (41, 42, 63) are grouped opposite a first face of the path turned towards a first of the two supports (27), and in that it is provided between the reciprocating drive means (41, 42; 63) and the second support (28) a mechanical connection (33) which extends laterally relative to said path.

3. Needling machine according to claim 1 or 2, characterized in that the back and forth drive means are eccentric means (41, 42, 63, 83) grouped along a common axis (S, 167) for both supports (27, 28).

4. Needling machine according to claim 3, characterized in that the eccentric means (83) comprise a movement transforming member (161) having a first end connected to a motor shaft (164) by an articulation (166) eccentric relative to the motor shaft (164), and a second end (162) articulated to a means (59) for actuating the supports of needle boards.

5. Needling machine according to claim 4, characterized by means for adjusting the orientation of the movement transformer member (161) relative to the axis (167) of the motor shaft (164).

6. Needling machine according to claim 1 or 2, characterized in that the back and forth drive means comprise two coaxial cranks (41, 42) each connected to one of the supports (27, 28).

7. Needling machine according to claim 6, characterized in that the two cranks (41, 42) have crank pins (43) offset angularly about their common axis (S).

8. Needling machine according to claim 6 or 7, characterized in that the two cranks (41, 42) are driven from the same motor (51).

9. Needling machine according to one of claims 6 to 8, characterized in that the two cranks (41,42) are integral with one another.

10. Needling machine according to one of claims 6 to 9, characterized in that the two cranks (41, 42) are driven in opposite directions from one another.

11. Needling machine according to one of claims 1 to

10, characterized in that the mechanical connection (33, 93) extends on either side of the travel path.

12. Needling machine according to one of claims 1 to 11, characterized in that the means for guiding the second support (28) are means (34, 35, 56, 78, 79, 88, 89, 96) for guiding the mechanical connection (33).

13. Needling machine according to one of claims 1 to

11, characterized in that at least one of the supports (27, 28) is fixed to at least one movable column up and down (29, 33) extending laterally relative to the travel path, and in that the guide means comprise for this column two coaxial sliding bearings (34, 35) located on either side of a plane (P) along which substantially extends said path.

14. Needling machine according to claim 13, characterized in that the column (33) simultaneously serves as a mechanical connection between the support (28) and the back and forth drive means (41, 42; 63).

15. Needling machine according to one of claims 1 to 11, characterized in that at least one of the supports (27, 28) is fixed to two movable columns up and down (29, 33) extending laterally from side and on the other side of the travel path, in that the guide means are, for each column, located on either side of a plane (P) along which said path extends substantially, and in that the two columns are connected to each other by a securing means (36, 37).

16. Needling machine according to one of claims 1 to 5, characterized in that the first and the second support (27, 28) are fixed to a first (29) and respectively a second (33) column movable up and down, in that the columns are connected to the reciprocating drive means (41, 42; 63) and are spaced along the longitudinal direction (D) of the travel path.

17. Needling machine according to claim 16, characterized in that it comprises a movable movement reversal means (56, 76) operatively installed between the two columns (29, 33).

18. Needling machine according to claim 17, characterized in that the eccentric means (63, 83) are mounted to actuate the movable movement reversal means (56) angularly back and forth.

19. Needling machine according to claim 17 or 18, characterized in that there is a column (29, 33) for each support (27, 28) and on each side of the travel path, and in that there is two mobile movement reversal means (56, 59, 76), one for each side of the path, the two mobile movement reversal means being coupled in rotation about an axis (T) extending substantially along the path width.

20. Needling machine according to one of claims 17 to 19, characterized in that the movable means for reversing movement comprises a reversing lever (76), and in that means for guiding in translation comprise two rods (78) having each a first articulation with the reversing lever (76), a second articulation with a compensating arm (79) and, midway between the first and the second articulation, a third articulation with a respective one of the columns (29, 33 ).

21. Needling machine according to claim 20, characterized in that at each of their ends, the columns are associated with a reversing lever (76, 86) and with means for guiding in translation of the aforementioned type (78, 79, 88, 89) with link (78, 88) and compensating arm (79, 89).

22. Needling machine according to one of claims 1 to 5, characterized in that the supports (27, 28) are each fixed to one of the opposite vertical sections (93, 99) of an endless element (91) bypassing two return wheels (56, 96), one of which is connected to the reciprocating drive means.