Rolling unit

Abstract

Rolling unit including at least two adjacent rolling stands, each having a pair of rolling rolls mounted on respective motorized shafts. The rolls of one rolling stand are disposed orthogonal and close to those of the adjacent rolling stand. The shafts are eccentrically supported in respective support elements, which are selectively rotatable around their axis and are each provided with rotation means to cooperate mechanically with an adjustment member suitable to make the support elements selectively rotate to determine an adjustment of the gap between the rolls. The rotation means of one pair of the support elements are directly connected kinematically to each other. The adjustment member is disposed, with respect to the rolling stands, so that the center of its gear lies very close to the line joining the centers of the support elements, so that a substantial part is contained in the bulk defined by the rolling stand.

Claims

1. Rolling unit comprising: at least two rolling stands (11a, 11b, 11c, 11d, 11e, 11f) disposed adjacent to each other and each provided with a pair of rolling rolls (12a, 12b) defining a rolling axis (D), mounted on respective first and second motorized shafts (15a, 15b), wherein rotation axes (Z) of the first and second motorized shafts (15a, 15b) are disposed on a first plane (A) of common laying, and wherein said rotation axes (Z) of said first and second motorized shafts (15a, 15b) are disposed substantially parallel to each other, and orthogonal with respect to said rolling axis (D), said pair of rolling rolls of one rolling stand being disposed orthogonal with respect to those of the adjacent rolling stand, said first and second motorized shafts (15a, 15b) being supported in an eccentric position with respect to the respective rotation axes (Z) in respective support elements (16a, 16b), said each support element (16a, 16b) being selectively rotatable around an axis of the support element and each support element being provided with a toothed member (21a, 21b, 121a, 121b), the toothed member of one support element reciprocally and directly engaging the toothed member of the other support element such that rotation of one toothed member causes rotation of the other toothed member, each toothed member being suitable to cooperate mechanically with an adjustment member suitable to make said support elements (16a, 16b) selectively rotate and determine an adjustment of a gap between said rolls (12a, 12b), each adjustment member comprising one gear (25; 125) and a means to make said gear (25; 125) rotate, and the toothed member (21a, 21b; 121a, 121b) of only one of the support elements (16a, 16b) being able to engage with the gear (25; 125) of the adjustment member in order to selectively make said support elements (16a, 16b) rotate and therefore vary the gap between the rolls (12a, 12b), wherein each of said support elements (16a, 16b) has a bulk defined by a second plane (B) and a third plane (C) which are both parallel to said first plane (A) and disposed on opposite sides of said first plane (A), each of the second plane (B) and the third plane (C) intersecting and being tangential to at least one of the support elements (16a, 16b), wherein each adjustment member is disposed, with respect to each rolling stand (11a, 11b, 11c, 11d, 11e, 11f), so that a center of its gear (25; 125) lies along, or very close to, a line joining centers of the toothed members (21a, 21b; 121a, 121b) of the support elements (16a, 16b) so that a part of the adjustment member is contained in a bulk defined by each rolling stand (11a, 11b, 11c, 11d, 11e, 11f), wherein each gear is a first toothed wheel or sector (25; 125), wherein each adjustment member further comprises a second toothed wheel or sector (27, 127) keyed on a same shaft (26, 126) on which said first toothed wheel or sector (25, 125) is keyed and a worm screw (29, 129) meshed with said second toothed wheel (27, 127), and wherein each first toothed wheel or sector (25, 125) acts in a space comprised between said second plane (B) and said third plane (C), and is disposed so as to always intersect said first plane (A).

2. Rolling unit as in claim 1, wherein said toothed members are chosen from a group comprising a toothed crown (21a, 21b) and a toothed sector (121a, 121b).

3. Rolling unit as in claim 1, wherein the support element (16a) on which said first toothed wheel or sector (125) acts is provided with a first toothed element (140), kinematically coupled with said gear (125), and with a second toothed element (121a) distinct and separate from the first toothed element (140) and rotatable with it.

4. Rolling unit as in claim 3, wherein at least one of either the first toothed element (140) or the second toothed element (121a) comprises a toothed circular sector.

Description

DESCRIPTION OF THE DRAWINGS

(1) These and other characteristics of the present invention will become apparent from the following description of a preferential form of embodiment, given as a non-restrictive example with reference to the attached drawings wherein:

(2) FIG. 1 is a schematic representation of a rolling unit according to the present invention;

(3) FIG. 2 is a sectioned view of a part of FIG. 1;

(4) FIG. 3 is a view of a detail of FIG. 2;

(5) FIG. 4 is a lateral view of FIG. 3;

(6) FIG. 5 is a view of a variant of FIG. 3.

(7) To facilitate comprehension, the same reference numbers have been used, where possible, to identify identical common elements in the drawings. It is understood that elements and characteristics of one form of embodiment can conveniently be incorporated into other forms of embodiment without further clarifications.

DESCRIPTION OF SOME FORMS OF EMBODIMENT

(8) With reference to FIG. 1, a rolling unit is denoted in its entirety by the reference number 10 and comprises a plurality of rolling stands 11a, 11b, 11c, 11d, 11e, 11f, each provided with a first rolling roll 12a and a second rolling roll 12b. Each rolling stand 11a, 11b, 11c, 11d, 11e, 11f comprises an adjustment device 13 to adjust the gap between the rolls 12a, 12b which allows to adjust the degree of aperture between the rolls and hence to vary the section sizes of the product that is rolled.

(9) The pair of rolls 12a, 12b of the rolling stand 11b lies on a first lying plane which is angularly offset by 90 with respect to a second lying plane on which lie the pair of rolls 12a, 12b of the rolling stands 11a and 11c disposed respectively upstream and downstream of the rolling stand 11b. An analogous disposition of the rolls 12a, 12b also applies for the other rolling stands 11c, 11d, 11e and 11f.

(10) Between the rolling rolls 12a, 12b a product to be rolled is made to pass, for example a bar or wire, which advances along the rolling axis D, in the direction indicated by the arrow F.

(11) Each first 12a and second roll 12b (FIGS. 2-4) of each rolling stand 11a, 11b, 11c, 11d, 11e, 11f is keyed cantilevered on a shaft 15a, respectively 15b, each having an axis of rotation Z.

(12) The axes of rotation Z of the first shaft 15a and second shaft 15b are disposed on a first plane A of common lying.

(13) The first and second shaft 15a, 15b of the first 12a and second roll 12b have their axes of rotation Z disposed substantially parallel to each other, and orthogonal with respect to the rolling axis D.

(14) Each shaft 15a, 15b (FIG. 2) is mounted on a support element, in this case an eccentric bushing 16a, respectively 16b, provided with a through hole 17 in which the shaft 15a, 15b supporting the rolls 12a 12b is housed.

(15) More specifically, a first eccentric bushing 16a supports the first shaft 15a to which the first roll 12a is associated, while a second eccentric bushing 16b supports the second shaft 15b to which the second roll 12b is associated.

(16) The through hole 17 has its axis offset axially with respect to the longitudinal axis of the eccentric bushing 16a, 16b, so that an eccentricity is obtained between the eccentric bushing 16a, 16b and the shaft 15a, 15b.

(17) The eccentric bushing 16a, 16b (FIG. 2) is housed in a support structure 19 provided with a housing hole 20 and can rotate around an axis Y which is offset with respect to the axis Z.

(18) Each of the eccentric bushings 16a, 16b (FIG. 4) is provided, at one end and on its external surface, with rotation means comprising respective toothed members 21a, 21b, e.g. a toothed crown 21a and respectively 21b.

(19) In particular, the toothed crowns 21a, 21b are of such a size, and are mounted on the support structure 19 in such a way, that they engage reciprocally with each other so that a rotation of one also causes the other to rotate.

(20) Each of the eccentric bushings 16a, 16b of the first 15a and second shaft 15b have an inter-stand bulk comprised between a second plane B and a third plane C (FIG. 3). The second plane B and the third plane C are both parallel to the first plane A on which the axes of rotation Z of the first 15a and second shaft 15b lie.

(21) The adjustment device 13 comprises an adjustment member comprising at least a gear, e.g. a first adjustment or engagement toothed wheel 25, which acts directly on the toothed crown 21a of the first support element 16a.

(22) Means are associated with the first toothed wheel 25 to make it rotate, so as to determine an adjustment of the gap between the rolls 12a, 12b.

(23) In other embodiments, the adjustment member may also comprise a toothed circular sector, a rack or a worm screw.

(24) With reference to FIG. 3, the first toothed wheel 25 acts in the space comprised between the second B and the third plane C described above, and is disposed so as to always intersect the first plane A of lying. In other words, the first toothed wheel 25 is disposed so that at least a substantial part thereof is contained in the bulk defined by the rolling stand 11a, 11b, 11c, 11d, 11e, 11f, that is, between the second B and third plane C.

(25) In particular, the center of the first toothed wheel 25 substantially lies along, or very close to, the line joining the centers of the toothed crowns 21a and 21b, so that the whole adjustment device 13 is disposed continuous in line with the development of the corresponding rolling stand 11a, 11b, 11c, 11d, 11e, 11f.

(26) With this particular configuration, the adjustment device 13 is disposed so as not to occupy the inter-stand space and therefore not to generate an increase in the bulk between the rolling stands 11a, 11b, 11c, 11d, 11e, 11f, in order to overcome the disadvantages of the state of the art.

(27) It is advantageous to provide that the first toothed wheel 25 acts tangentially to the first toothed crown 21a and substantially in correspondence to the intersection with a plane on which the axes Y of the eccentric bushings 16a, 16b lie.

(28) The first toothed wheel 25 is keyed on a shaft 26 (FIG. 4). At the opposite end of the shaft 26 with respect to where the first toothed wheel 25 is mounted, a second toothed wheel 27 is keyed, which in turn engages on a worm screw 29 (FIGS. 2-4), selectively rotatable either manually or by means of suitable motorized actuation members selectively actuated by the user.

(29) In particular, by making the worm screw 29 rotate, a rotation is determined of the second toothed wheel 27 which, since it is solidly associated with the shaft 26, entails an analogous rotation of the first toothed wheel 25 as well.

(30) The rotation of the first toothed wheel 25 determines a consequent rotation of the first eccentric bushing 16a as well, and hence also of the second eccentric bushing 16b, since, in order, the first toothed wheel 25, the first toothed crown 21a and the second toothed crown 21b are reciprocally engaging with each other.

(31) The conformation of the eccentric bushings 16a, 16b is such that a rotation thereof entails a variation in the position of the shafts 15a and 15b, that is, a variation in the reciprocal distance of the axes Z to determine a consequent variation in the gap comprised between the first roll 12a and the second roll 12b.

(32) More specifically, the distance between the axis of rotation Z and the axis Y of the eccentric bushings 16a, 16b determines the amplitude of adjustment of the gap between rolls 12a, 12b. In fact, the variation in the gap between the rolls that can be determined can be as much as double the distance of the axis of rotation Z and the axis Y.

(33) In other embodiments, it may be provided that, instead of being a toothed wheel 25 as described above, the adjustment member is an analogous mechanical member suitable to make the first eccentric bushing 16a rotate, for example it may be provided to use a rack that acts tangentially to the first toothed crown 21a and which is disposed so as to always intersect the first plane A containing the axes of rotation Z of the shafts 15a, 15b. In this case, the term center is taken to mean a substantially median zone on the length of the rack.

(34) In this case the movement of the rack can be obtained by means of linear actuation members possibly also associated with lever mechanisms.

(35) In still other embodiments, the first toothed wheel 25 can be directly associated with actuation means, both manual and motorized, without providing the use of the second toothed wheel 27 and the worm screw 29.

(36) A reducer member may be associated to the worm screw 29, selectively actuated in manual or motorized mode. The reducer member associated to the worm screw 29 allows to achieve a very precise adjustment of the gap between the rolls.

(37) A toothed wheel 30 or mandrel is solidly associated to each of the first 15a and second shafts 15b, at the opposite end to that where the first 12a and second roll 12b are keyed.

(38) An actuation mechanism 31 (FIG. 1), possibly provided with means to reduce the revolutions, is associated to the toothed wheel 30 and is provided to make both shafts 15a, 15b rotate, and hence the rolls 12a, 12b, in order to roll the rolled product.

(39) According to another embodiment shown in FIG. 5, the rolling stands, in this case the rolling stand 11b, instead of comprising eccentric bushings 16a and 16b provided with a toothed crown extending for the whole circumference, are provided only with a toothed portion or element, or toothed sector, e.g. a toothed circular sector, respectively 121a, 121b, which extends angularly for an angle equal to or slightly more than 90.

(40) The toothed portions 121a, 121b reciprocally engage with each other and rotate around the axis Y which is offset with respect to the axis Z of the shafts 15a and 15b in order to determine the desired eccentricity.

(41) The eccentric bushing 16a is in turn provided with another toothed portion or element 140 having the same or different dimensional geometric characteristics as/from the toothing of the toothed portion 121a.

(42) Furthermore, instead of providing to use the first toothed wheel 25 and the second toothed wheel 27 as described above, the adjustment device 13 is provided with a first toothed sector 125 that in turn engages on the toothed portion 140 of the first bushing 16a, and with a second toothed sector 127 that is provided to engage with a worm screw 129 or, in other embodiments, with other mechanical members such as for example a rack. The first toothed sector 125 and the second toothed sector 127 are made to rotate together, since both are mounted solid with a single shaft 126.

(43) By making the worm screw 129 rotate, either manually or with motorized actuation members, the rotation is determined of the second toothed sector 127 and the first toothed sector 125.

(44) The rotation of the first toothed sector 125 determines the rotation of the toothed portion 140 associated with the eccentric bushing 16a and hence the consequent rotation also of the toothed portion 121a solidly associated with the latter.

(45) The rotation of the toothed portion 121a also determines the consequent rotation of the eccentric bushing 16b, and therefore a consequent adjustment of the gap between the rolls 12a and 12b.

(46) In this embodiment too the adjustment device 13 acts only on the eccentric bushing 16a and is disposed so as to directly intersect the first plane A on which the axes of rotation Z of the first 15a and second shaft 15b lie.

(47) The angular amplitude of the toothed portion 140, of the first toothed sector 125 and of the second toothed sector 127, and also their reciprocal disposition with respect to the respective axes of rotation is such as to allow the rotation of the eccentric bushings 16a, 16b and to determine the variation in the reciprocal gap between the rolls 12a, 12b from their minimum value to their maximum value.

(48) It is clear that modifications and/or additions of parts may be made to the rolling unit as described heretofore, without departing from the field and scope of the present invention.

(49) For example, it may be provided that, instead of supporting directly the shafts 15a, 15b of the rolls 12a, 12b, the eccentric bushings 16a, 16b are provided with circular seatings, made eccentric with respect to the axis of longitudinal development of the eccentric bushings 16a, 16b, in which rolling elements can be housed, such as for example bearings.

(50) Furthermore, it may be provided that, with reference to the description regarding FIG. 5, the first toothed sector 125 and the second toothed sector 127 may be replaced by a toothed wheel which performs the same function.

(51) It is also clear that, although the present invention has been described with reference to some specific examples, a person of skill in the art shall certainly be able to achieve many other equivalent forms of rolling unit, having the characteristics as set forth in the claims and hence all coming within the field of protection defined thereby.