Bar feeder for multi-spindle lathes, with selective drive

Abstract: A bar feeding device for multi-spindle machine tools; the device comprises a rotating drum (10) provided with a plurality of guides (11) for the bars, which longitudinally extend in different angular positions, on the outer surface (40) of the drum (10). Bar pushing members (12) slidingly movable along the guides, are connected to a control system comprising a set of peripheral gears (41) circumferentially arranged at one end, and supported to rotate with the drum, coplanarly around a central pinion gear (42) connected to a drive motor; the pinion gear (42) is tangentially arranged in an offset angular position, to selectively engage each peripheral gear (41) over a predetermined arch shaped path by rotation of the drum (10).

Description: The present invention refers to an automatic apparatus for feeding elongated work-pieces, such as bars and the like, to multi-spindle machine tools and, more generally refers to improvements to the drive devices of the bar pushing members in bar feeders of rotating drum type, for allowing a selective operation when the feeder drum is at a standstill with a guide for the bars in a predetermined angular position, as well as when the drum is rotationally actuated by the same machine tool; in this way it is possible to anticipate the forward movement of the bars while each spindle of the machine tool is rotating and approaching to a predetermined working position. A bar feeder comprising the features of the preamble of claim 1 is disclosed in US-A-42 92 864 (see especially figure 5). Automatic apparatuses for loading and feeding bars to be worked to multi-spindle machine tools are generally well known, according to which the apparatus comprises a frame member for supporting a bar guide drum to rotate according to a horizontal axis coinciding with the rotational axis of the spindle-holder turret of the machine tool; bar guides longitudinally extending with respect to the drum are provided in angular spaced apart positions and axially aligned to corresponding spindles of the machine tools, each guide for the bars being provided with a bar-pushing member selectively operated to move a bar forward through a respective spindle of the machine, when the drum is at a standstill, and the guide is in a predetermined angular position. Apparatuses of the above mentioned type are shown and described in several prior patents, for example in US 3.874.519, US 4.088.230, US 4.292.864, US 4.604.924 and US 4.700.593. It is also well know that to achieve high productions, in multi-spindle automatic lathes, the working speed is constantly increased and the operative cycles are correspondingly reduced; consequently the structure and the operative mode of the bar feeder automatic apparatuses were improved to satisfy the new and bigger requirements of these machine tools. For example, a prior European patent application EP-A-0 123 658 discloses a drive device for the bar pushing members of a drum feeder of the know type, which uses a mechanical drive device comprising a plurality of gear members operationally connected by endless chains to a respective bar-pushing member; the various gears are radially arranged with their axis at one end of the drum to rotate with the latter, and gear coupling means being provided to connect each gear member to a power operated conical gear co-axially arranged with respect to the drum. A circular cam acts on the coupling means to selectively connect each pushing member to a drive motor of the central conical gear while the drum of the feeder is rotating and a selected one of the bar guides is approaching to a predetermined angular position. This solution, even if allowing the forward movement of the bars as soon as the spindle collects of the machine tool are opened, while the feeder drum is rotating, in practice presents a quite complex structure which, because of the delays caused by the coupling backlashes, does not allow for a perfect synchronism during working. Moreover, the more complex coupling system at one end of the drum, with its own weight and inertia negatively affects the drum by opposing to the rotational force exerted by the machine tool itself; the use of such a drive device does not allow to operate at high rotational speeds, and therefore the feeder cannot be used in machine tools of the fast type. Moreover, the extreme mechanical complexity of the drive device causes a difficult set-up, higher breakdown risks due to bad coupling operation and higher maintenance costs. In order to improve such a feeder, European patent application EP-A-0 174 034, discloses another mechanical solution, which is simplified in some particulars, but however always employing teeth couplings connectable to the pushing members and operating only when the drum is at a standstill condition when each guide for the bars is in correspondence of an angular position where the bars should be moved forward in the respective spindle of the machine tool. Although with this second solution the bar feeder is simplified and the entire weight of the drum is partially reduced, however it does not allow for an anticipated feeding of the bars when the drum is revolving; therefore again it cannot be used in machine tools of the fast type. In a further European patent publication, EP-A-0 338 606, an hydraulic solution has been suggested, according to which hydraulic drive motors are used for each pushing member, wherein the various hydraulic motors are supported at one end of the drum to be selectively fed by a suitable rotating oil distributor. This document is therefore limited to suggest only a different solution to the problem of the anticipated forward movement of the bars, without however achieving the aim of simplifying the feeder construction and to substantially reducing the weight of the rotating bar-guide drum. On the contrary, under some points of view, this hydraulic solution is quite worse with respect to a mechanical solution, as the higher weight of the hydraulic motors and of the oil herein contained, constitute a concentrated mass which can cause distortions to the drum when the latter is under rapid rotation, thus requiring drums having a sturdy construction and consequently a higher weight. An object of the present invention is to provide for a bar feeder for multi-spindle machine tools of the above mentioned type, which uses a mechanical solution for driving the bar-pushing members, by means of which it is possible to achieve the two aims of lightening the whole rotating structure of the drum and of allowing a selective anticipated feeding of the single bars while the drum is still rotating, which, when necessary, can be changed thus enabling the feeder to be particularly suitable for being used in multi-spindle machine tools of the fast type. For the total elimination of the mechanical coupling, the rotating drum is remarkably lightened, consequently reducing the risk of distortions and/or deformations of the same drum and of the bar guides, as well as damages to the same bars. A further object of the present invention is to provide for a bar feeder as previously referred to, wherein the drive of the pushing members is quite simplified, because it takes advantage of the rotation of the same drum to selectively connect each pushing member to a unique drive motor, by means of an original and extremely simplified gear system. Such a feeder requires therefore a minimum maintenance and consequently a low cost, by maintaining a high reliability degree as the number of the moving parts subjected to wear is greatly reduced with respect to a conventional bar feeding device. The particularly innovative and original feature of the present invention, resides in the possibility to use the same rotation of the feeder drum and a particular crown wheel system to selectively connect each bar pushing member to a single drive motor. Moreover, the proposed solution allows for driving each bar pushing member at one or more working positions and to arrange for an adequate advance angle for driving the bar pushers self-adjusting to the requirements of different working machines. These and other objects are obtained by means of a bar feeder according to claim 1. According to the invention, a bar feeder for multi-spindle machine tools has been provided, of the type comprising: a support frame for a drum member rotatably supported by the frame to turn according to a horizontal axis, the drum member being provided with a plurality of bar guides longitudinally extending in angularly spaced apart positions, said bar guides being axially aligned to corresponding spindles of the machine tool; bar pushing members being slidably supported to move along said guides, in combination with a mechanical drive system comprising a plurality of peripheral crown gear members, circumferentially arranged to the rotational axis of the drum, each crown gear being operatively connected to a respective bar-pushing member, said crown gears being provided at one end of the drum and supported to rotate with respect to a central drive gear member connected to a drive motor for sliding each bar-pushing member along the guides for the bars, characterized in that said crown gears and said drive gear member are coplanary arranged with respect to each other, to provide rotational axe parallely arranged to the longitudinal rotating axis of the drum, in that the drive gear is provided in a offset position with respect to the rotation axis of the drum, and tangentially arranged inside the crown gears to selectively engage and disengage each peripheral gear member along a predetermined arched path, by the rotation of the feeder drum itself. These and other features and advantages of the bar feeder embodying the invention will be more clear from the following description of some preferred embodiments making reference to the attached drawings, wherein: Fig. 1 is a longitudinal sectional view of part of a feeder according to the invention; Fig. 2 is a front view, according to line 2-2 of Fig. 1; Fig. 3 is an enlarged detail of Fig. 2 to show the engaging and the disengaging steps of a gear with respect to the central pinion gear; Fig. 4 is an enlarged detail of Fig. 2 to show a possible variation of the means for adjusting the position of the central pinion gear with respect to the crown gears driving the bar pushing members; Fig. 5 shows a view similar to that of Fig. 2 for a further variation providing for the use of two independent drive pinions gears; Fig. 6 is a perspective view of the drum; Fig. 7 is a cross-sectional view according to line 7-7 of Fig. 1. With reference to figures 1 and 2, the feeder according to the invention substantially comprises a drum 10 constituted for example by a special section in aluminium, provided by a plurality of bar guides 11 longitudinally extending to the drum 10 in angularly spaced apart positions shown in figure 7; each guide 11 for the bars is provided with a respective bar pushing member 12 which is suitably driven to slide along the same guide 11. The drum 10 is supported at each end to rotate according a own longitudinal axis, by means of a disk 13 made of plastic material, provided with hollow hub 14 wherein one end of the drum 10 is fitted and suitably blocked to prevent removal of the drum. The disk 13 is supported to rotate by a set of idle rollers 15 provided on a support plate 16 which is part of the frame structure of the feeder. Reference 17 in figures 1 and 2 further indicates the whole mechanical drive device of the bar pushing members 12 according to the invention. More precisely, each pushing member 12 is supported to longitudinally slide along one guide 11 for the bars and it is connected, by means of a plate 18, to an endless chain 18A which runs inside the drum 10; at the back end of the drum which is opposed to the front end connected to the machine tool, the chain 18A engages with a cogged wheel 19 operatively connected to a cylindrical gear 21 by means of conical idle gears 20, the rotational axis of the cylindrical gear 21 being parallely arranged to the longitudinal rotational axis of the drum 10. As it can be seen in figure 2, the drive mechanism 17 comprises a set of gears 21 circumferentially arranged to define a crown gear system rotatably supported with the drum 10, to selectively engage and disengage a central pinion gear 28 along an arched path; each of the crown gears 21 is mechanically connected to a respective bar-pushing member 12, without any intermediate coupling member, and the crown gears 21 are coplanary arranged among each other, as well as with respect to the central pinion gear 22 connected to a rotating shaft 22A supported by a tiltable support element, for example a transversal rod 23 pivoted at its top end 24, the rod 23 near its lower end rests against two side adjustable stops members 25 which bias the rod 23 to engage the pinion gear 22 with the cylindrical gears 21, as explained further on. A cogged wheel 26 is provided at the rear end of the shaft 22A (figure 1), said wheel 26 being connected by a chain 27 to a second cogged wheel 28, or in another way, of a drive motor 29 which in turn is supported at the lower end of the rod 23. The drive motor 29 may be of any suitable type, for example hydraulic, electric or pressure air actuated type. Always in figure 2, it can be seen that the crown gears 21 are provided on a support plate 30 fixed by bolts to the disk 13 maintaining a circumferential disposition of their rotational axis, parallel to the longitudinal axis of the drum. From the same figure 2, it appears that the central pinion gear 22 is supported by the bar 23 in a predetermined angular position, which is offset with respect to the longitudinal axis of the drum, tangentially inside the crown gears 21 to selectively engage with each one of the said crown gears in a predetermined angular position indicated by the reference 21A, while rotating with the drum 10 according to the arrow F in figure 1. The engagement position of the central gear 22 with the crown gears 21 may be suitably adjusted by acting on the side stops 25. It should be noted that for simplifying the description, the position of the gear 21A, which in figure 2 is engaged with the central pinion gear 22, has been modified in figure 1 for an explaining purpose only. With reference now to figure 3 and to the previous figures, we will better describe the characteristics and the working mode of the device 17 for selectively driving the pusher members 12 of the feeder. In figure 2 reference 21A indicates the position of each crown gear 21 when the drum is at a standstill condition in which a bar to be worked, should be fed forward for a predetermined length, through a corresponding spindle of the machine tool. Under this condition, the crown gear 21A is completely engaged with the pinion gear 22, thus maintaining a tangential arrangement of the respective "pitch line"; therefore, the drive motor 29, by the chain 27, the pinion gear 22, the gear set 21, 20, 19 and the endless chain 18A, drives the forward sliding of the pushing member 12 to move the bar into the guide 11 for a predetermined length. However, as initially stated, the engagement of each crown gear 21 with the central pinion gear 22 may occur with a certain advance because of the rotation of the drum 10; this engagement is maintained for a predetermined rotational angle, bridging the stop position A of the drum where each guide 11 of the feeder and the respective spindle of the machine tool result positioned in correspondence of a loading and forward feeding station for the bars. More precisely, as shown in the scheme of figure 3, the engagement of each crown gear 21 with the pinion gear 22 occurs along an arched path having a predetermined length, comprising an inlet section B1 along which the gear 21A which is approaching to position A is engaging pinion 22, and an outlet section B2 along which the gear 21B, moving away from position A, disengages from pinion gear 22. The beginning of the engagement phase of the gear 21A and the end of the disengagement phase of the gear 21B may timely coincide or may occur in different moments taking advantage of the rotational movement of the drum 10 and to the particular eccentric position of the pinion gear 22 with respect to the drum 10 and the set of crown gears 21 the axis of which are arranged along a circumference concentric with the axis of the drum. The advanced engagement of the crown gear 21A with the gear 22 at the inlet side B1, is allowed as usually the opening of the spindle collects of a machine tool occurs in turn with a certain advance with respect to the working position where the bar is usually moved forward in the machine tool, and by the fact that the same gear 21A, owing to the rotation of the drum 10, gradually approaches the pinion gear 22 which may freely rotate by keeping the drive motor 29 in idle condition as far as the output gear 21B, in turn, is disengaged. By suitably positioning the pinion gear 22 with an appropriate eccentricity both in a vertical and horizontal directions with respect to the rotational axis of the crown 10, such as in an advanced angular position with respect to position A, it is possible to change the angular ratio between the inlet section B1 and the outlet section B2, the first one being equal to or larger than the second one. In the second case the disengagement of the gear 20B which is leaving position A, occurs before the engagement phase of the inlet gear 20B be completed; the difference existing between the two angles defines the angle advance of the gear 22 which allows for operating each crown gear 21 and therefore to move each bar pusher 12 with a certain advance while the drum 10 of the feeder is still rotating. In this way an anticipated bar feeding is obtained particularly suitable when using the feeder with machine tools of the fast type. For explanatory purpose, by considering that in six-spindle machine tools a rotation of about 40° is devised for the control cam driving all machine movements, including opening of a spindle collect which is approaching the position in which the forward movement of bars to be worked occurs, it is possible to provide for an angular inlet section B1 of about 20° wideness and an outlet section B2 having an equal wideness or less, for example of 15°, in such a way that in the remaining 5° of the drum rotation, it is possible to provide for a rapid and advanced forward movement of the bars, which can continue for a period of time depending on the drive cam of the machine tool, with the drum at a standstill condition after the crown gear 21A having reached the position A shown in figure 2. The advanced engagement of the inlet gear 21A with respect to the theoretic position A represented in figure 2, is advantageous as when starting the drive motor 29, the toothing of the gear 21 is already in mesh with the toothing of gear 22, thus avoiding crashes or dangerous strikes for the teeth of the same gears. Advantageously the gears may be constituted of a suitable plastic material, for example of polyurethane elastomeric material having a hardness equal to or higher than 80 Shores in order to take advantage from the same elasticity of the teeth to compensate possible little interferences in the case the gear teeth are slightly elongated and ended with a rounded tip in order to avoid direct contact among the tips of the same gears 21 and 22 while they are engaging at the beginning of the inlet section B1. The use of plastic material for gears 21 and 22 as well as for rotating disk 13 and hub 14 is advantageous in that allows to substantially reduce the weight and rotational inertia of the drum, during revolution, avoiding kick back on the machine tool at each starting or stopping of the rotor; therefore fast rotating feeders may be provided according to the invention. It is also important that the position of the pinion gear 22 could be changed or suitably adjusted with respect to the position of the crown gear 21A. In this connection, as already said with reference to figure 2, the pinion gear 22 is positioned on a bar 23 pivoted to its upper end 24. At the opposite end of the rod 23 two adjustable stops 25 are provided on both sides, which comprise for example a bolt screwing into a corresponding support member fastened to the frame 16; acting on the bolt it is possible to make the rod 23 slightly rotate around its pivot point 24, in this way moving away or approaching the gear 22 to the gear 21 in the position A, with respect to a calculated theoretical position. In this case the rod 23 and the gear 22 are prevented from rocking by two side stops 25. In some cases it would be more advantageous to allow the gear 22 for a short movement away from the gear 21A in order to reduce possible stresses and wear caused by the initial mesh. In this connection, as shown in the detail of figure 4, the stop device 25 on the side of the rod 20 which is opposite with respect to the engagement side between gears 21 and 22, may be subjected to an elastically yieldable spring means which tends to push and makes the rod 23 rotate the gear 22 in the engagement direction with the gears 21. In particular, as shown in figure 4, the stop device 25 comprises a pin member 31 sliding in a hollow screw 32 which may be screwed and blocked in an adjusted position into a support bush 33 by means of a suitable locking nut, as shown. A spring 34 is housed into the hollow screw 32, to thrust the pin member 31 towards the bar 23 supporting the central gear 22. Figure 5 of the attached drawings shown a further embodiment particularly suitable to be used with machine tools having two positions for loading and moving forwards the bars, which in the example of figure 5 are shown in diametrically opposite positions. In the case of figure 5, two independent pinion gears 22 are provided, every one supported with its own drive motor by a rod 23, in a way similar to the one previously described when making reference to figure 2; therefore in figure 5 the same reference numbers have been used to indicate similar or the same parts. Also the operating mode of the drive device of figure 5 substantially does not vary with respect to the one of figure 2 with the only difference that in this case there is the contemporaneous engagement of two crown gears with the respective pinion gears and consequently the contemporaneous operation of the two bar pushing members which are arranged in opposite angular positions of the drum. With reference to figs. 6 and 7, we will now describe the general features of the bar feeder according to the invention. As previously stated, the bar feeder substantially comprises a hollow tubular drum 10, better shown in the detail of fig. 2. The drum 10 of the feeder is moreover provided, in predetermined angular positions, with a plurality of guides 11 for the bars, in which each guide 11 comprises two sets of opposed jaws, wherein a first set of jaws 35 is suitably fixed to the drum 10 by square rods 36 while the other set of jaws 37 is supported by rods 38 to rotate between open and closed conditions thus allowing the loading of a new bar in a predetermined angular position during the working cycle of the machine tool. The guides 11 are supported in axially spaced apart positions of the drum 10, by means of a plurality of circular sectors 39 peripherally arranged around the tubular body of the drum 10, as shown in figure 2. More precisely, according to a further feature of the invention, the drum 10 is in the form of a double wall cylindrical hollow body, for example aluminium extruded, comprising an external peripheral wall 40 and a plurality of reinforcement internal elements such as tubular elements 41 having the double function of reinforcing the drum 10 and housing the chains 18A and connection members 18B which drive the sliding pushing members 12 for the bars. As clearly shown in fig. 6, each tubular element 41 inside the drum 10, opens on the peripheral surface 40 by a longitudinal slit 42 which allows the protrusion of the plate 18 to which the corresponding pushing member 12 is fixed. To increase the resistance to bending and the twist stiffening of the drum, the same drum is provided with an inner wall 43 integral with the tubular elements 41 inside the drum. The drum 10 is moreover provided with anchoring means for the circular sectors 39 supporting the bar guides which are longitudinally extending on the outer wall 40 of the drum; in the shown case, the anchoring means comprises T-shaped ribs 44 radially extending from the peripheral surface 40 in an intermediate position between the slits 42 of two adjacent tubular elements 41. However it is evident that for replacing the T-shaped ribs, any kind of suitably shaped ribs could be used, or alternatively the longitudinal anchoring means could be in turn constituted by a set of internal and/or external channel members, between the tubular elements 25. The use of a hollow cylindrical body for the drum 10 provided with internal and/or external reinforcement means, allows for numerous and certain advantages, among them a higher capacity of the drum to resist to bending and torsion actions during rotation, thus allowing to maintain a perfect linearity of the guides and a perfect alignment of the bars to the spindles of the machine tool; the possibility of obtaining the cylindrical body 10 from aluminium extrusion sections remarkably reduces the weight of the drum and inertia problems when the bar feeder is connected to fast-operated machine tools. It is in fact clear from fig. 2 that the internal tubular elements 41 and the T-shaped ribs 44 co-operate to increase the resistance to the bending stress, consequently increasing the twisting torque. Moreover, the internal tubular elements 41 and the external ribs 44 are advantageously used for additional functions greatly simplifying the structure of the whole rotating drum. As initially said, each bar guide 11 is constituted by a set of fixed jaws 35 and by a set of turntable jaws 37 connected to rods 36 and 38 supported by a plurality of shaped plates 39 circumferentially arranged on the outer wall of the drum 10. More precisely, as shown in fig. 7 of the attached drawings, in correspondence to each support point of the guides 11, a set of shaped plates 36 is provided, the number of each being equal to the number of the guides 11, circumferentially arranged around the cylindrical body 10 of the drum. Each support plate 39 is in the form of a circular sector resisting on the cylindrical outer surface of the drum 10. Each circular sector 39 and the drum 10 are moreover provided with connecting means comprising a T-shaped slot 45 at the inside edge of plate 39, which slidingly fits on a corresponding T-shaped rib 44 of the drum 10; in this way the supporting plates 39 for the guides 11 may be easily assembled and positioned in a perfectly aligned way, by simple sliding along each rib 44 till the predetermined position of guide support. Each plate 39, in turn, is provided at one end with a square hole 46 through which a square rod 36 for the fixed jaws 35 is passing through and, at the other end, a circular hole 32 is provided in which a cylindrical sleeve 38 is housed for the rotation of the square rod 48 to which the mobile jaws 37 are fixed. From fig. 7 of the attached drawings, it can also be seen that each support plate 39 at each end is delimited by a flat surface which, together with the opposite flat surface of an adjacent plate, defines a radial slit 49 axially aligned with a longitudinal slit 42 on the peripheral surface of the drum 10, to allow the passage of the plate 18. From the above, it is evident that according to a particular embodiment of the invention, a bar feeder for multi-spindle machine tools has been provided comprising a rotating drum having a particular structural shape, which at the same time is extremely stiff and light as it can be extruded in the form of an aluminium section with all involved functional advantages. Moreover, the use of arch shaped plates for supporting the guides for the bars in combination with connecting means allowing sliding of the support plates during the assembling on the cylindrical drum, greatly simplify the structure of the feeder with the subsequent constructive and maintenance advantages. From what said and shown in the attached drawings it is evident that a bar feeder has been provided comprising a gearing device of new design for driving the single pushing members to advance the bars along the guides on a rotating drum, and towards the respective spindles of a machine tool, in which a quite simple and advantageous use is made of the rotational movement of the same drum, to selectively engage a set of crown gears connected to the bar-pushing members, peripherally arranged around the rotational axis of the drum, with a central pinion gear in an eccentric and misaligned position, in such a way that the engagement of each crown gear is kept over a predetermined arched path, thus eliminating the use of mechanical couplings and of the cam systems employed in the bar feeder previously known. It is thus obtained a feeder structure extremely simple, lightened and particularly suitable for application on machine tools of the fast type; practically it has been evaluated a reduction of substantially 1/3 of the weight of the drive members which are to be necessarily supported by the drum. Moreover, by suitably choosing the diameters and the positions of the various crown gears as well as the eccentricity of the pinion gear, it is possible to obtain an advanced drive of each bar-pushing member or to vary the same advance when the drum is still rotating. The use of suitable materials and design for the rotating drum, the guides for the bars, the gears and for the several components of the entire device, allow for a further reduction in the weight of the rotating masses.

Claims: A bar feeding device for multi-spindle machine tools, of the type comprising: a support frame (16) for a drum (10) rotatably supported by the frame (16) to turn according to a horizontal axis, the drum (10) being provided with a plurality of bar guides means (11) longitudinally extending in angularly spaced apart positions to be axially aligned with corresponding spindles of the machine tool; a bar pushing members (12) slidingly provided along the bar guide means (11), in combination with drive means (17) comprising a set of peripheral gears (21) operatively connected to corresponding pushing members (12) of the bar feeding device, said peripheral gears (21) being supported to turn with the drum (10), and to selectively engage and disengage with at least one pinion gear (22) connected to a drive motor (29), whereby the peripheral gears (21) and the pinion gear (22) of the drive means are coplanary arranged at one end of the drum (10); the rotational axes of the peripheral gears (21) are angularly spaced and parallely arranged to the longitudinal axis of the drum (10) and the pinion gear (22) is tangentially arranged with respect to the set of the peripheral gears (21) of the drive, to selectively engage each peripheral gear (21) over a predetermined arched path (B1, B2), by the rotation of the drum (10), characterized in that the pinon gear (22) is arranged inside the set of peripheral gears (21). A bar feeding device according to claim 1 characterized in that said pinion gear (22) is adjustably supported with respect to the peripheral gears (21) of the drive means for the pushing members (12) of the bar feeding device. A bar feeding device according to claim 2 characterized in that said pinion gear (22) is provided on a movable support member (23), and adjustable stop means (25) are provided on at least one side of the pinion support member (23) to change the position of the same pinion gear (22) with respect to the peripheral gears (21) driving the pushing members (12) of the bar feeding device. A bar feeding device according to the previous claim 3 characterized by comprising a stop means (25) on one side of the pinion support member (23) and elastically yielding spring means (34) to urge the pinion gear (22) into engagement with the peripherally gears (21) along said arched path (B1, B2). A bar feeding device according to previous claim 1, characterized by comprising at least a first and a second pinion gear (22), connected to a respective drive motor (29) each pinion gear (22) being provided on a respective movable support member (23) and biasing means (25) to urge the pinion gear (22) on each support member (23) to selectively engage the peripheral gears (21) for the pushing members (12) in angularly spaced apart position during rotation of the drum (10). A bar feeding device according to claim 1 characterized in that said drum (10) is in the form of a tubular hollow body comprising an inner and an outer wall (43, 40) co-axially arranged, and straightening means comprising tubular members (41) peripherally arranged and longitudinally extending between the inner and the outer walls (43, 40) of the body (10) each tubular member (41) being provided with a longitudinal slit (42) opening on the peripheral outer wall (40) of the drum. A bar feeding device according to claim 6 comprising bar guide members (35, 37) longitudinally aligned on supporting rods (36, 48) parallely arranged with respect to outer wall (40) of the drum (10), said rods (36, 48) being supported in axially spaced apart positions by shaped plates (39) fixed to the outer wall (40) of the drum (10), characterized in that slide connecting means are provided between the drum (10) and the shaped plates (39) for supporting the rods (36, 48) of the guide members (35, 37) said connecting means comprising interengaging rib and slot members (44, 45) longitudinally extending between facing surfaces of the drum (10) and the shaped plates (39). A bar feeding device according to claim 6 characterized in that the shaped plates (39) supporting the rods (36, 48) for the bar-guide members (35, 37), are in the form of arch-shaped plats circumferentially arranged around the outer wall (40) of the drum (10). A bar feeding device according to claims 6 and 8 characterized in that the flat facing ends surfaces of the circumferentially arranged arch-shaped plates are spaced apart to define a slit (49) radially extending from a slit (42) on the outer wall (40) of the drum, and control means for moving the bar pushing members (12) along the guides (11) for the bars, the control means comprising a sliding control member (18B) inside a stiffening tubular bar (41) of the drum, and plate means (18) to connect each pushing member (12) to control member (18B) sliding inside a stiffening tubular bar (41), said plate connecting means radially extending between the sliding control member (18B) and the pushing member (12), through the slits (42) on the outer wall (40) of the drum and between the facing end surfaces of contiguous arch shaped plates (39).

Inventors: CUCCHI GIOVANNI, CUCCHI, GIOVANNI
Applicants: CUCCHI GIOVANNI & C SRL, CUCCHI GIOVANNI & C. S.R.L.
Application year: 1996
Main classification: B23B13
IPC codes: B23B13