ROTARY DI SAGGREGATOR FOR EXCAVATORS AND OPERATING MACHINES IN GENERAL

Abstract

A rotary disaggregator for an operating machine, such as an excavator, comprising a support structure, a single rotating drum comprising a plurality of teeth and a drive unit for the rotating drum. The support structure includes a connection plate which defines a connection plane with respect to the operating machine and comprises a lateral arm, on which the rotating drum is rotatably supported. The rotation axis (X) of the conical drum is inclined with respect to the connection plane in such a manner that a generatrix of the rotating drum is essentially parallel with the connection plane.

Claims

1. A rotary disaggregator for an operating machine, such as an excavator, comprising a support structure which can be connected to a movable arm of the operating machine, a rotating drum comprising a plurality of teeth and a drive unit which is configured to rotate the rotating drum about a rotation axis (X), wherein the rotating drum has a frustoconical shape, the support structure comprising a connection plate which defines a connection plane (a) with respect to the operating machine, the connection plate being configured to fix the rotary disaggregator to the arm of the operating machine in such a manner that the connection plane (a) is substantially perpendicular to the arm of the operating machine, and comprising a support arm, on which the rotating drum is rotatably supported, the rotation axis (X) being inclined with respect to the connection plane (a) in such a manner that a generatrix (Y) of the frustoconical shape defined by the rotating drum is essentially parallel with the connection plane (a), the generatrix (Y) being arranged at an end of the rotary disaggregator opposite the connection plate.

2. The rotary disaggregator according to claim 1, wherein the rotating drum defines a base surface which is opposite along the rotation axis (X) with respect to the end, and comprises a plurality of additional teeth.

3. The rotary disaggregator according to claim 1, wherein the frustoconical shape defined by the rotating drum has a conicity with an angle () which is substantially equal to double an angle of inclination () which is formed between the rotation axis (X) and the connection plane (a).

4. The rotary disaggregator according to claim 3, wherein the angle of inclination () is between 10 and 30.

5. The rotary disaggregator according to claim 3, wherein the angle of inclination () is between 15 and 25.

6. The rotary disaggregator according to claim 1, wherein the support structure comprises a pair of tapered connection plates which form a pair of walls of the support structure and which extend from the support plate towards the support arm, tapering in a direction away from the support plate.

7. The rotary disaggregator according to claim 1, wherein the teeth define a rotation trajectory with a diameter (D) equal to or greater than an extent of the support plate in a direction perpendicular to the generatrix (Y).

8. The rotary disaggregator according to claim 1, wherein the rotating drum defines a greater diameter (D) and a smaller diameter (d).

9. The rotary disaggregator according to claim 8, wherein the teeth which are arranged in the region of the smaller diameter define such a rotation trajectory that the teeth which are arranged in the region of the smaller diameter (d) project with respect to the connection plate along a direction parallel with the generatrix (Y).

10. The rotary disaggregator according to claim 8, wherein the teeth which are arranged in the region of the greater diameter (D) of the rotating drum do not project with respect to the connection plate along the direction parallel with the generatrix (Y).

11. The rotary disaggregator according to claim 1, wherein the drive unit comprises a hydraulic motor and a reduction gear, preferably of the epicyclic type, wherein the hydraulic motor has a rotation axis (R) which is inclined with respect to the rotation axis (X) of the rotating drum, the reduction gear having a rotation axis which coincides with the rotation axis (X) of the rotating drum.

12. The rotary disaggregator according to claim 11, wherein the rotating drum is hollow, the reduction gear being received inside a cavity which is defined by the rotating drum.

13. The rotary disaggregator according to claim 1, wherein the teeth comprise a coupling element which is connected to an external mantle of the rotating drum and a cutting element which is supported by the coupling element and which is intended to come into contact with a surface which is intended to be processed, the coupling element being configured so as to support the cutting element in such a manner that it extends in an inclined direction with respect to a direction which is normal to the external mantle.

14. A rotary disaggregator according to claim 13, wherein the cutting element has an inclination () with respect to a tangential direction of the mantle in the region of the coupling element between 20 and 70.

15. The rotary disaggregator according to claim 1 when dependent on claim 8, wherein the teeth project outwardly from the rotating drum in the region of the smaller diameter (d).

16. The rotary disaggregator according to claim 2, wherein the additional teeth comprise a respective coupling element which is connected to the base surface of the rotating drum and a respective cutting element which is supported by the respective coupling element and which is intended to come into contact with the surface which is intended to be processed, the respective coupling element being configured so as to support the cutting element in such a manner that it extends in an inclined direction with respect to a plane (b) which is defined by the base surface.

17. The rotary disaggregator according to claim 1, comprising a single rotating drum.

18. The rotary disaggregator according to claim 17, wherein the arm comprises a side which is arranged in the axially opposite direction to the rotating drum and which defines an external surface of the arm.

19. The rotary disaggregator according to claim 18, wherein the external surface of the lateral arm extends substantially perpendicularly to the connection plane (a).

20. The rotary disaggregator according to claim 18, wherein an end of the rotating drum is aligned with the side along a direction parallel with the generatrix (Y) or projects with respect to the side along a direction parallel with the generatrix (Y).

21. The rotary disaggregator according to claim 18, wherein the side comprises a lateral wall and a removable covering plate, the lateral wall having an opening which is configured so as to allow access to the drive unit and to be able to be closed by means of the removable covering plate.

Description

[0053] Other advantages, characteristics and the methods for use of the present invention will become evident from the following detailed description of a number of embodiments which are set out by way of non-limiting example. Reference will be made to the Figures of the appended drawings, in which:

[0054] FIG. 1 is a perspective view of a rotary disaggregator according to the present invention;

[0055] FIG. 2 is a front cross-sectional view of the disaggregator of FIG. 1;

[0056] FIG. 3 is a side view of the disaggregator of FIG. 2;

[0057] FIG. 4 is a perspective view of the rotary disaggregator according to the present invention, from which a rotating drum has been removed in order to illustrate additional components thereof.

[0058] Initially with reference to FIG. 1, a rotary disaggregator which is constructed according to the present invention is generally designated 100.

[0059] The disaggregator 100 is of the type intended to be used in an operating machine, such as, for example, an excavator, the excavator not being illustrated in the Figures.

[0060] According to an aspect of the invention, the disaggregator 100 is intended to be fixed to a movable arm of the excavator, as will be better illustrated below.

[0061] Still with reference to FIG. 1, the disaggregator comprises a support structure 1 which can be connected to the movable arm of the operating machine. Preferably, the connection is brought about in the region of a connection plate 10 which defines a connection plane a in the region of which the connection with respect to a corresponding portion of the arm is advantageously brought about.

[0062] For example, the connection plate can be provided with a plurality of holes in which corresponding screws are engaged in order to bring about the connection with respect to the disaggregator which may therefore be moved by means of the arm of the excavator in order to carry out the excavation operations and generally the processing operations required.

[0063] In preferred embodiments, the connection plate 10 is configured to fix the rotary disaggregator 100 to the arm of the operating machine in such a manner that the connection plane a is substantially perpendicular to the arm of the operating machine.

[0064] It will be appreciated that a person skilled in the art will be able to recognize the direction in which the arm of the excavator develops, this typically being in a longitudinal development and therefore defining a corresponding plane which is perpendicular to this longitudinal development direction.

[0065] As illustrated in the example of FIG. 1, the support structure 1 comprises a lateral arm 11 on which a rotating drum 2 intended for carrying out the milling operations is rotatably supported.

[0066] Preferably, the disaggregator comprises a single rotating drum 2 which extends in a cantilevered manner from the support arm 11.

[0067] In any case, it will be appreciated that the present invention may also be used in the case of two rotating drums which are arranged one beside the other.

[0068] The drum 2 is preferably provided with a plurality of teeth 20 which act on the earth or other material to be processed in order to carry out the milling operations.

[0069] The milling is carried out by means of the rotation of the drum about a rotation axis X, which is brought about by means of a drive unit 3 illustrated in FIG. 2.

[0070] According to another aspect of the invention, the rotating drum 2 has a frustoconical shape and has an axis which is inclined with respect to a horizontal plane. In other words, the disaggregator is configured in such a manner that, when it is arranged with the connection plane a parallel with a horizontal plane, the rotation axis X is inclined with respect thereto. Consequently, the rotation axis X is also inclined with respect to the connection plane a.

[0071] Preferably, the rotating drum 2 comprises an external mantle 26 which defines the frustoconical shape thereof, from which the teeth 20 extend. In some embodiments, the rotating drum 2 defines a base surface 25 which essentially defines the smaller base of the frustoconical shape and which in turn comprises a plurality of additional teeth 20A.

[0072] Preferably, the inclination of the rotation axis X and the shape of the drum are such that a generatrix Y of the frustoconical shape is essentially parallel with the connection plane a. In particular, this is carried out in the region of the generatrix Y which is arranged in the region of the end of the rotary disaggregator 100 opposite the connection plate 10. This generatrix will therefore be parallel with the ground when the movable arm of the excavator is perpendicular thereto, allowing the maximum efficiency to be obtained during milling operation.

[0073] This feature can be obtained in some embodiments, such as, for example, the one illustrated in FIG. 2, provided that the frustoconical shape which is defined by the rotating drum 2 has a conicity with an angle which is substantially equal to double an angle of inclination which is formed between the rotation axis X and the connection plane a.

[0074] In the context of the present invention, the term substantially is intended to be understood to mean that a deviation of 5% may be provided.

[0075] In this manner, the generatrix of the frustoconical drum is positioned in a horizontal manner with a simple structure which is particularly suitable for withstanding the stresses to which the disaggregator is subjected during the earth processing operations.

[0076] In the embodiment illustrated in FIG. 2, the angle of inclination is 20. More generally, however, this angle is preferably between 10 and 30 and even more preferably between 15 and 25.

[0077] Advantageously, if there are provided two rotating drums, the second drum will be arranged symmetrically with respect to a vertical plane which is perpendicular to the generatrix Y.

[0078] Now also with reference to FIG. 1 again, there will be illustrated in greater detail preferred features of the support structure 1 and the support arm 11.

[0079] As can be seen in FIG. 2, the support arm 11 is preferably a lateral arm and comprises a side 12 which is arranged in the direction axially opposite the rotating drum 2 and which defines an external surface 12A of the arm 11. This surface preferably forms the outermost portion of the lateral arm and consequently defines the dimensions thereof.

[0080] In some embodiments, the external surface 12A extends substantially perpendicularly to the connection plane a and is essentially aligned therewith.

[0081] In some embodiments, the rotating drum 2 has an end 21 which is arranged in a projecting manner with respect to the above-mentioned side 12. This end is formed in the region of the greater diameter of the frustoconical shape and, as can be observed in the figure, it is arranged along the generatrix Y.

[0082] In other words, the end 21 corresponds to the end which is directed downwards during use.

[0083] The end 21 may alternatively be aligned with the side 12, there generally being provision for the spatial requirement towards the exterior of the disaggregator 100, in the direction of the generatrix Y, to be contained within the end 21 of the drum.

[0084] In this manner, there will not be present portions of the side 12 which are intended to come into contact with the earth while the disaggregator is lowered in the earth, that is to say, it is moved in a direction perpendicular to the connection plane a.

[0085] In the region of an end which is axially opposite the end 21, there may also be provision for there to be no portions of the structure 1 which project beyond the rotating drum 2.

[0086] In this case, in light of the inclination of the drum 2, in some embodiments there may be provision for the teeth 20 to cover the portions of the structure 1 projecting furthest.

[0087] In some embodiments, in fact, the teeth 20 which are arranged in the region of the end 21 project in the direction X away from the support structure 1.

[0088] To this end, there may also be provision for the teeth 20 which are arranged in the region of the smaller diameter to define such a rotation trajectory that the teeth 20 which are arranged in the region of the smaller diameter d project with respect to the connection plate 10 in the direction X.

[0089] In other words, the teeth 20 which are arranged adjacent to the base surface 25 preferably project in the direction X away from the support structure 1.

[0090] It is thereby possible to prevent any impact between the plate and the earth during a processing operation perpendicular to the ground.

[0091] According to another aspect, as may be observed in FIG. 3, the teeth 20 can also define a rotation trajectory with a diameter D equal to or greater than the extent 1 of the support plate in a direction perpendicular to the generatrix Y. Therefore, the drum projects with respect to the plate 10 and in general the structure 1, including in the region of the direction perpendicular to the axial direction.

[0092] Now with reference to FIGS. 2 and 3, in some embodiments the teeth 20 comprise a coupling element 24 which is connected to the external mantle 26 of the drum 2 and a cutting element 23 which is supported by the coupling element 24 and which is intended to come into contact with the surface to be processed. Preferably, the coupling element 24 is configured so as to support the cutting element 23 in such a manner that it extends in a direction which is inclined with respect to a direction normal to the external mantle 26. In preferred embodiments, the cutting element 23 has an inclination y with respect to a tangential direction of the mantle 26 in the region of the coupling element 24 between 20 and 70, as illustrated in FIG. 3.

[0093] In some embodiments, the additional teeth 20A also comprise a respective coupling element 28 which is connected to the base surface 25 of the drum 2 and a respective cutting element 27 which is supported by the coupling element 28 and which is intended to come into contact with the surface to be processed. Preferably, the coupling element 28 is configured so as to support the cutting element 27 in such a manner that it extends in a direction which is inclined with respect to a plane b which is defined by the base surface 25. Preferably, the coupling element 28 has an elongate shape and the cutting element 27 is aligned with the longitudinal direction of the coupling element 28. In preferred embodiments, the coupling element 28 has an inclination with respect to the plane b between 20 and 70, as illustrated in FIG. 2.

[0094] Now with reference to FIG. 1 again, the support structure 1 preferably comprises a pair of tapered connection plates 13 which form a pair of additional walls of the support structure 1.

[0095] The connection plates 13 which extend from the support plate 10 towards the support arm 11, tapering in a direction away from the support plate 10, therefore allowing the cantilevered configuration previously described to be defined.

[0096] According to yet another aspect, the drive unit 3 comprises a hydraulic motor 30 and a reduction gear 31, preferably of the epicyclic type.

[0097] Advantageously, the rotating drum 2 is hollow, with the reduction gear 31 being received inside the cavity 22 which is defined by the rotating drum 2 itself.

[0098] In some embodiments, the hydraulic motor 30 can be arranged in an inclined manner with respect to the reduction gear 31, optimizing the overall dimensions of the drive unit. In general, the hydraulic motor 30 may have a rotation axis R which is inclined with respect to the rotation axis X.

[0099] Vice versa, the rotation axis of the reduction gear 31 coincides with the rotation axis X of the rotating drum 2.

[0100] The rotation drum 2 can be connected to the reduction gear 31 in order to be rotated by means of a connection flange 4, which is illustrated in the embodiments of FIGS. 2 and 4.

[0101] Advantageously, the connection flange 4 can be connected to an external body 33 of the reduction gear 31 by means of threaded connections 34.

[0102] In preferred embodiments, the connection flange 4 has a plurality of seats 40 which extend in a substantially perpendicular direction to the rotation axis X of the drum 2. Now also with reference to FIG. 1, the drum 2 can thereby be fixed to the flange 4 using a series of connection elements 42, for example, screws, which are preferably arranged in the region of the mantle 26 and which engage in the seats 40.

[0103] In this manner, the drum can be constructed in a single piece and can be fixed, once assembled, to the drive unit 3.

[0104] In order to allow simple access to the drive unit 3, without compromising the solidity of the structure, the side 12 preferably comprises a side wall 14 and a removable covering plate 15 for covering an opening 14A.

[0105] Therefore, the invention solves the problem proposed, at the same time achieving a plurality of advantages, including the possibility of carrying out deep processing operations. Furthermore, the disaggregator of the present invention is particularly versatile and manageable as a result of a structure having particularly small dimensions.

[0106] The characteristics of the structure and the drive unit of the disaggregator can further also allow sufficiently high powers to be provided for challenging operations.