FR2967939A1 - Lateral compression type shear press for compressing scrap iron, has vertical press comprising cover, where crushing force of cover in specific angular position is greater than crushing force of cover in another angular position - Google Patents

Abstract

The present invention relates to a machine for compressing any type of material, in particular for compressing and cutting scrap, comprising a box (2) for compression, a vertical press (3) comprising a rotary mounting cover (31) on the side wall (22) of the body, and at least one jack (32) for moving said lid between a 0 ° angular position and a 90 ° angular position, and a transverse press (5). The transverse dimension of the plate (311) of vertical compression of the lid, is greater than or equal to 60% of the transverse dimension of the bottom wall (21) of the box (2), and the crushing force (F) of the lid in the angular positions of 40 ° to 90 ° is greater than the crushing force of the lid in the angular positions less than 40 °.

Description

The present invention relates to a machine for compressing any type of material, especially scrap. The present invention relates more particularly to a machine for compressing and cutting scrap, conventionally called shear press, in particular s type side compression. Such compression press type presses conventionally comprise a substantially L-shaped compression box mounted on a frame, said box comprising a longitudinal side wall and a bottom wall, and being equipped with a vertical press and a transverse press. The vertical press comprises a compression cover rotatably mounted on the side wall of the body, said lid being in the form of a lever with a first arm formed of a vertical compression plate, and at least one second arm extending outward from the body. ls actuating cylinder, rotatably mounted on the frame by its cylinder and whose end of its rod is rotatably mounted to said second arm, allows said cover to move between a 0 ° angular position, said open position, and a position angular about 100 °, said closed position. The transverse press comprises a transverse compression plate 20 slidably mounted on the compression box, substantially perpendicular to the side wall of the body, and a displacement system adapted to move said pressure plate in the compression box between a remote position and a compression position. The machine further comprises a longitudinal press, disposed at a transverse end of the box, comprising a pusher plate for longitudinally compressing the scrap and for pushing the compressed scrap, referred to as a package, to a shear assembled to the frame at the other end. of the crate to cut the package into several packets of desired length.

For vertical compression, the jack and the lid are conventionally defined so that the crushing force of the lid is maximum at the half-stroke of the jack in order to balance the forces on either side of a median position. or to an angular position of about 50 °, the crushing force of the lid increasing from 0 ° to 50 ° and decreasing from 50 to 100 °. In combination with this crushing force, the width of the vertical compression platter of the lid is slightly greater than the width of the pusher plate. After performing the vertical compression, the cover is returned to a 90 ° angular position and the transverse press is actuated to effect transverse compression. The object of the present invention is to provide a solution for improving the compression efficiency of such machines. For this purpose, the present invention provides a machine for compressing any type of material, in particular scrap metal, in particular a machine for compression and cutting, such as a press-type press machine with lateral compression, comprising: a frame, - a compression box, of substantially L-shaped cross section, mounted on the frame, comprising a longitudinal side wall, for example substantially vertical, and a bottom wall, for example substantially horizontal, - a vertical press comprising: a compression cover rotatably mounted on the side wall of the box about a longitudinal pivot axis, said cover being in the form of a lever with a first arm formed of a compression plate having an internal surface of compression, and at least a second arm extending outwardly relative to the body; an actuation system comprising at least one cylinder, preferably hydraulic, of which a first element among its cylinder and the end of its rod is rotatably mounted to said second arm about a pivot axis parallel to the axis of rotation; pivoting the lid, and the other element is rotatably mounted on the frame about a pivot axis parallel to the pivot axis of the lid, for moving said lid between a 0 ° angular position, said open position, wherein the inner compression surface is disposed substantially parallel to the side wall of the compression box, for example substantially vertically, and a so-called closed 90 ° angular position, wherein said inner compression surface is disposed substantially parallel to the bottom wall 3 of the compression box, for example substantially horizontally, and a transverse press comprising a compression plate cross-section having an inner surface, substantially parallel to the side wall, for example vertical, slidably mounted on the compression box substantially perpendicular to the side wall of the body, and - a displacement system adapted to move said transverse compression plate in the compression box between a spaced apart position and a compression position, characterized in that - the transverse dimension, or width, of the vertical compression plate, is greater than or equal to 60% of the transverse dimension of the bottom wall of the the compression box when the transverse compression plate is in a spaced position, and preferably in that, when the lid is pivoted from its open position to its closed position, the crushing force of the lid in the angular positions of the 40 ° to 90 ° is greater than the crushing force of the lid in the lower angular positions at 40 °. According to the invention, the vertical compression plate of the cover has a large internal compression surface and the lever effect of the vertical press is defined so that the crushing force is greatest in angular positions. the cover corresponding to the compression zone of the material where the forces necessary to compress the material are the most important, either to the angular positions of the cover from 40 ° to 90 °. This shift in the angular position range where the crushing force is greatest, combined with a large cover, increases the compaction efficiency, and thus increases the productivity of the machine. Preferably, the crushing force of the lid in the angular positions of 50 ° to 90 ° is greater than the crushing force of the lid in the angular positions of less than 50 °.

According to another feature, the crushing force at the angular positions of 40 ° to 90 ° is greater than or equal to 80% of the maximum crushing force. Preferably, the crushing force at the angular positions of 50 ° to 90 ° is greater than or equal to 90% of the maximum crushing force. Preferably, the transverse dimension of the vertical compression plate is greater than or equal to 75%, preferably greater than or equal to 80%, of the transverse dimension of the bottom wall of the compression box when the transverse compression plate is in spread position. According to one embodiment, the compression box comprises two transverse walls, the vertical compression plate of the lid extends substantially from one wall transverse to the other of the box and covering at least 60%, preferably at least 75%, more preferably at least 80%, of the surface of the bottom wall of the body in the position away from the transverse compression plate. According to a particular feature, the maximum crushing force is obtained for an angular position of the cover between 60 ° and 80 °. Preferably, the maximum crushing force is obtained for an angular position of the cover between 65 ° and 75 °. According to one embodiment, the cylinder (s) for actuating the vertical press and the actuating system of the transverse press are able to be controlled by a control unit of the machine to simultaneously perform a moving the lid to its closed position and moving the transverse compression plate toward its compression position, at least a portion of the lid pivoting range from its open position to its closed position, for example so that the tray transverse compression is disposed near the end edge of the vertical compression plate when said lid has reached its closed position, and / or to simultaneously move the lid towards its open position and a displacement of the transverse compression plate towards its spaced apart position, at least over part of the pivoting range of the lid from its closed position to its open position, d preferably over the whole of said range. The simultaneous movement of the vertical press and the transverse press makes it possible to increase the compaction efficiency and also to improve the compaction cycle time and therefore the productivity of the machine. According to one embodiment, the machine comprises a bucket pivotally mounted on the frame, between a substantially horizontal loading position and an inclined unloading position, about a pivot axis disposed under the bucket, in front of the transverse compression plate 5 between the latter and the side wall of the box, in order to dump the material to be compressed, substantially in the middle of the compression box, and at least partly in the pressure corridor, and thus increase the closing speed of the box by moving the vertical compression plate to the closed position and the transverse compression plate to the compression position. According to one embodiment, the machine further comprises a longitudinal press disposed on a first transverse side of the compression box, and / or a shear disposed on the second transverse side of the compression box, the longitudinal press serving to push the Compacted material obtained after vertical and transverse compression, called a package, in the direction of the shear to cut the compacted material into packets of desired length. The invention will be better understood, and other objects, details, features and advantages will become more clearly apparent from the following detailed explanatory description of a presently preferred particular embodiment of the invention, with reference to the drawings. attached diagrams, in which: - Figures 1 to 3 are different perspective views of a compression press and cutting machine of the shear press type according to the invention, the cover being in the open position; - Figure 4 is another perspective view of the machine of Figure 1, the lid being closed; FIG. 5 is a diagrammatic cross-sectional view, substantially in a sectional plane passing through one of the jacks 30 for actuating the lid, the lid being in an angular position close to its open position at 0.degree. angle R of the order of 10 °; - Figure 6 is a view similar to that of Figure 3, the lid being in its closed position at 90 °; FIG. 7 is a graph illustrating the crushing force of the cover as a function of its angular position; FIGS. 8A to 8E are schematic views of the machine, along a sectional plane passing through one of the actuating cylinders, illustrating various steps of a vertical compression process and transverse compression of scrap; and, Figs. 9A and 9B are views similar to those of Figs. 8A and 8E illustrating two steps of a vertical compression and lateral compression process according to an alternative embodiment. The figures illustrate a shear press type machine according to the invention for compressing scrap in the form of a longitudinal lo packet of given rectangular section, and then cutting said package into several packets of desired length. The machine comprises a compression box 2 mounted on a frame 1, intended to receive the scrap to be compressed, a vertical press 3 for the vertical compression of the scrap received in the box, a transverse press 5 for transverse compression of the scrap. , a longitudinal press 6 for thrusting the scrap to a shear (not shown), and possibly for the longitudinal compression of the scrap, and a skip 7 for loading scrap into the crate.

The compression box 2, of substantially L-shaped cross section, comprises a rectangular bottom wall 21 mounted substantially horizontally on the frame, a substantially vertical longitudinal side wall 22, an upstream vertical transverse wall 23, and a transverse wall. vertical called downstream 24.

The longitudinal press 6 comprises a vertical, rectangular, pusher plate 61 capable of being displaced longitudinally by an actuating system 62 of the hydraulic cylinder type, along the bottom wall 21 and the side wall 22. Actuation enables the pusher plate to be moved from a retracted position illustrated in FIG. 2, in which the pusher plate is disposed substantially against the upstream wall 23, in the direction of the downstream wall 24, in order to push the compacted scrap through an opening 25. The shape of the pusher plate corresponds to that of the opening 25, and its width defines the pusher corridor of the body.

The machine comprises a shear (not shown), known per se, mounted at this opening 25, for cutting the package.

The transverse press 5 comprises a transverse compression plate 51, rectangular, having a substantially vertical internal compression surface 51a. This plate 51 extends substantially from a transverse wall 23 of the body to the other 24, and is slidably mounted on the bottom wall 21, substantially perpendicular to the side wall of the body. The transverse compression is effected by means of an actuating system comprising at least one hydraulic jack, for example two hydraulic cylinders 52, able to move said plate 51 in the box between a spaced position illustrated in FIGS. 3 and 5, and a compression position illustrated in Figure 8E, wherein the transverse compression plate is disposed at a distance from the side wall that is less than or equal to the width of the pusher plate 61 and the opening 25. With particular reference to Figures 5 and 6, the vertical press 3 ls comprises a compression cover 31 in the form of a lever rotatably mounted along the upper edge of the side wall of the body about a longitudinal axis B, having a first arm formed by a compression plate 311 having an internal compression surface 311a, and two second arms 312 formed of two longitudinally offset tabs 20 (FIG. 4) from each other and extending outward from the body. The vertical compression is performed under the action of at least one hydraulic actuating cylinders, for example two hydraulic actuating cylinders 32. According to Figures 5 and 6, each cylinder 25 is for example pivotally mounted by its cylinder 321 in the lower part of the frame about an axis A, parallel to the axis A, and its rod 322 is pivotally mounted to a second arm 312 The cylinders are adapted to move the cover from an angular position of angle R to 0 °, said open position, in which the internal surface 311a of the vertical compression plate 311 is arranged substantially vertically, as illustrated in FIGS. FIGS. 1 to 3, to an angular position of angle R at 90 °, referred to as the closed position, in which the internal surface 311a is arranged substantially horizontally, as illustrated in FIG. 6. In the closed position, the distance between the surface 311a and the bottom wall 21 is substantially greater than the height of the transverse compression plate 51.

In the present embodiment, the plate 311 extends substantially from one transverse wall to the other of the box, and its width, which corresponds substantially to the distance between the axis B and the end edge 311b free is substantially equal to 80% of the distance between the side wall 22 and the inner surface 51a of the transverse compression plate in the separated position. The compression plate in the closed position thus covers substantially 80% of the compression zone of the body corresponding to the surface of the bottom wall when the transverse compression plate is in the separated position. The crushing force (Fe) at a point P of the plate depends on the normal components (FN) of the force (Fv) of the actuating cylinders 32 which is perpendicular to the second arm 312, the length AP, and the DB length of the second arm: Fe = n (FN x DB) / LP, where n is the number of cylinders. The leverage effect of the vertical press during the rotational movement of the cover, which corresponds to (FN x DB) / Fv, is defined so that the crushing force Fe of the cover in the angular positions of 40 ° to 90 ° of the lid is greater than the crushing force of the lid in the angular positions less than 40 ° 20 of the lid. Furthermore, the lever effect is defined so that the crushing force at the angular positions of 40 ° to 90 ° is at least 80% of the maximum crushing force. The crushing force of the lid increases from 0 ° to 70 °, and decreases slightly from 70 ° to 90 °. In the illustrated embodiment, the axes A, 25 D of the cylinders in the open position of the lid are slightly outwardly offset with respect to the axis B, and the longitudinal axis of the cylinders passing through the axes A and D is slightly shifted outwards with respect to the plane DB of the second arms passing through the axes D and B when the cover is at 0 °.

The lever arm effect according to the rotation of the lid is defined as a function of the lateral offset (L1) of the axis A with respect to the axis B, the vertical offset (L2) of the axis B with respect to the axis A, the lateral offset (L3) of the axis D relative to the axis A when the cover is at 0 °, and the vertical offset (L4) of the axis D relative to the axis A when the lid is at 0 °.

The plane DB of the second arms passing through the axes D and B is inclined with respect to the inner surface of the vertical compression plate of the lid by an angle a. In the illustrated example, this angle α is about 20 °, FN is thus equal to Fv when the cover is at an angular position of 70 °. The maximum crushing force is thus obtained at this angular position of 70 °. According to an exemplary embodiment, Fv = 120 t (in tons per cylinder); L1 = 85 cm; L2 = 285 cm; L3 = 55 cm; L4 = 205 cm. FIG. 7 shows the crushing force of the lid at a point P positioned substantially in the middle of the machine's pusher pack or corridor as a function of the angular position of the lid, in the case of a machine having the parameters defined below. above, with two actuators 32 actuating the lid, the distance BP being substantially equal to 40 cm. In this example, the maximum crushing force Fe at 70 ° is about 510 t. The crushing force is at least 84.5% of the maximum crushing force at the angular positions of 40 ° to 90 °, and at least 93.5% of the maximum force at the angular positions of 50 ° to 90 °. The bucket 7 comprises a rectangular bottom wall 71 closed on three sides by a vertical rear wall 72, and two vertical transverse walls 73. The bucket is pivotally mounted on the frame, above the transverse press 5, its open side facing the compression box. For its pivotal mounting, the bucket comprises two arms 74 mounted extending downwards from the transverse walls of the bucket, arranged on either side of the upstream and downstream walls 23, 24 of the body, and whose ends are pivotally assembled on the chassis about a pivot axis C, parallel to the aforementioned axes A, D and B, shown schematically in FIGS. 5 and 6. Said axis C is disposed in front of the transverse compression plate 30 when the latter is in the spaced apart position, for example at a height substantially corresponding to half the height of the plate. In its loading position, the bottom wall 71 of the bucket is disposed substantially horizontally, its open side being disposed substantially vertically of the plate 51 of transverse compression 35 when the latter is in its spaced apart position. Two jacks 75, connected to the frame and the bucket, provide pivoting of the bucket to tilt 2967939 lo the latter in a so-called unloading position shown in Figure 8B, to dump the scrap in the compression box. This pivoting mounting of the bucket around a C axis offset to the body allows to dump the scrap in the middle of the box, at least in part s in the pusher corridor. The vertical press 3 and the transverse press 5 are advantageously able to be moved simultaneously, in order to optimize the compaction phase, which can represent 30 to 50% of the production time. When the lid is moved from its open position at 0 ° to its closed position at 90 °, the transverse compression plate is simultaneously moved from its spaced apart position towards the side wall. To do this, the machine comprises two independent hydraulic pressure lines, one for the cylinders of the transverse compression plate, and possibly those of the bucket, and ls a line for the cylinders of the cover, and possibly the cylinders of the pusher tray. A method of compressing scrap with the machine according to the invention will now be described with reference to Figs. 8A to 8E. According to FIG. 8A, the scrap M1 to be compressed is first fed into the bucket which is in the loading position, the lid being in the open position at 0 °, the transverse compression plate 51 being in the spaced apart position. The bucket is tilted unloading position via the cylinders 75 to dump the loose scrap M1 in the box 2 compression. The lid is then actuated by the cylinders 32, as shown in FIG. 8C. Simultaneously, the bucket is returned to its loading position. Simultaneously with the displacement of the cover towards its 90 ° position, the transverse compression plate 51 is moved transversely from its position away towards the side wall of the body, as shown in FIG. 8D. By way of example, the displacement of the transverse compression plate begins when the lid is substantially in its angular position at 45 °. When said lid has reached its closed position at 90 °, the compression plate is for example disposed substantially at the end edge 311b of the vertical compression plate. The movement of the lid is continued to its compression position shown in FIG. 8E. The longitudinal press can then be activated to push the M2 package of scrap towards the opening 25 to cut it by means of the shears. Advantageously, the movement of the transverse compression plate simultaneously with the movement of the lid begins s from an angular position of the lid which is parameterizable manually. The movement of the compression plate to its compression position may be effected simultaneously with the movement of the lid over the entire pivot range of the lid, from its open position at 0 ° to its closed position at 90 °, or at only one Part of the pivoting range of the lid, this depending on the amount and nature of the scrap placed in the crate. For the opening of the body, the movement of the lid from its closed position at 90 ° to its open position at 0 ° and the movement of the compression plate transverse from its compression position to its position ls spaced, are advantageously carried out simultaneously, movements starting substantially simultaneously, automatically. According to one embodiment, the cylinders 32 for actuating the vertical press are able to move the compression plate in rotation beyond the angular position at 90 °, for example about 20 °, towards an angular position. said extreme closed position, which is therefore 110 ° in the example considered. The machine may operate in a first automatic or manual mode, as previously described with reference to Figs. 8A to 8E, with simultaneous movement of the transverse compression plate and the cover at least over a portion of the lid pivot range, or in a second automatic or manual mode in which, once the scrap is discharged into the compression box, the lid is lowered to its closed position shown in FIG. 9A, then to its extreme closed position illustrated at 30 9B, the compression plate being held in the spaced position during this pivoting of the lid. The compression plate is then brought back to the closed position at 90 °, as shown in FIG. 9A, and then the compression plate is moved from its remote position to its compression position shown in FIG. 8E.

Although the invention has been described in connection with a particular embodiment, it is obvious that it is in no way limited thereto and that it comprises all the technical equivalents of the means described and their combinations if These are within the scope of the invention.

Claims (10)

REVENDICATIONS1. Machine for compression of any type of material (M), comprising s - a frame (1), - a compression box (2), of substantially L-shaped cross section, mounted on the frame, comprising a side wall (22) longitudinal, and a bottom wall (21), - a vertical press (3) comprising a - a cover (31) rotatably mounted on the side wall (22) of the body about a pivot axis (B) longitudinal, said lid being in the form of a lever with a first arm formed of a compression plate (311) having an inner compression surface (311a), and at least one second arm (312) extending outwardly relative to the body, and - an actuating system comprising at least one jack (32) of which a first element among its cylinder (321) and the end of its rod (322) is rotatably mounted to said second arm about a pivot axis (D), and the other element is rotatably mounted on the frame around a pivot axis (A) for moving said cover between an angular position at 0 °, said open position, in which the internal compression surface is disposed substantially parallel to the side wall (22) of the compression, and a so-called closed 90 ° angular position, in which said inner compression surface (311a) is disposed substantially parallel to the bottom wall (21) of the compression box, and - a transverse press (5) comprising - a transverse compression plate (51) having an inner surface (51a), substantially parallel to the side wall, slidably mounted on the compression box substantially perpendicular to the side wall of the body, and - a suitable displacement system moving said transverse compression plate into the compression box between a spaced position and a compression position, characterized in that the transverse dimension of the vertical compression plate (311) is greater than or equal to 60% of the transverse dimension of the bottom wall (21) of the compression box (2) when the transverse compression plate (51) is in position spaced, s - and in that, when pivoting the lid from its open position to its closed position, the crushing force (Fe) of the lid in the angular positions of 40 ° to 90 ° is greater than the force of crush the lid in angular positions less than 40 °. 10 2. Machine according to claim 1, characterized in that the crushing force (Fe) of the cover in the angular positions of 50 ° to 90 ° is greater than the crushing force of the cover in the angular positions of less than 50 ° . Machine according to claim 1 or 2, characterized in that the crushing force (Fe) at the angular positions of 40 ° to 90 ° is greater than or equal to 80% of the maximum crushing force. 4. Machine according to claim 3, characterized in that the crushing force (Fe) at the angular positions of 50 ° to 90 ° is greater than or equal to 90% of the maximum crushing force. 20 5. Machine according to one of claims 1 to 4, characterized in that the transverse dimension of the plate (311) vertical compression is greater than or equal to 75% of the transverse dimension of the bottom wall (21) of the body when the transverse compression plate (51) is in a spaced position. 25 6. Machine according to one of claims 1 to 5, characterized in that the maximum crushing force (Fe) is obtained for an angular position of the cover between 60 ° and 80 °. 7. Machine according to claim 6, characterized in that the maximum crushing force (Fe) is obtained for an angular position of the lid between 65 ° and 75 °. 8. Machine according to one of claims 1 to 7, characterized in that the (s) cylinder (s) actuating (32) of the vertical press (3) and the actuating system (52) of the press transverse are controllable to simultaneously move the cover 35 to its closed position and a displacement of the transverse compression plate to its compression position and to simultaneously move the cover to its open position and a displacement of the tray. transverse compression towards its separated position. 9. Machine according to one of claims 1 to 8, characterized in that it comprises a bucket (7) pivotally mounted on the frame (1) about a pivot axis (C) disposed under the bucket, in front of the plate (51) of transverse compression, in order to discharge the material (M1) to compress substantially in the middle of the compression box. 10. Machine according to one of claims 1 to 9, characterized in that it further comprises a longitudinal press (6) arranged on a first transverse side of the box (2) of compression, and a shear disposed of the second transverse side of the compression box, the longitudinal press for pushing the material (M2) compacted, in the direction of the shear to cut the compacted material into packets of desired length.