DESCRIPTION

The present invention concerns a vibration device . In particular, the present invention concerns a vibration device connectable to an operating machine for a relative movement thereof and designed to cause the vibration of a tool .

STATE OF THE ART

In the earth movement sector, vibration devices designed to cause the vibration of appropriate tools are well-known; said tools , according to their particular structural characteristics , are used for compacting the soil , for vibro-driving piles into the ground or for other analogous operations that require a vibrating tool .

As known, any one of said vibration devices is reversibly couplable for the respective movement to an operating machine such as , for example , an excavator, a backhoe , a loader, a scraper or a bulldozer, and has a lower portion to which a tool i s rigidly connectable , said tool varying according to the type of operation to be carried out : for example , said tool can consist of a plate or a roller in the case of compacting operations , or a pile driver or a grab in the case of vibro-driving operations . In any case , the operation required is carried out using both the force exerted downwards by the operating machine and the vibration of the tool .

In detail , the vibration device usually comprises a support frame reversibly couplable to the operating machine , and a vibrating frame supported by the support frame and at the lower end of which the tool can be rigidly connected . The vibrating frame furthermore supports a rotating member driven in rotation around a hori zontal axis to generate a vibration of the tool . In fact , the rotating member comprises a shaft driven in rotation by an actuator, and an eccentric body fixed on the shaft so that the relative centre of mass l ies outside the rotation axis : in this way, the rotation of the rotating member results in a corresponding circular vibration of the vibrating frame and therefore also of the tool connected to it .

Said solution has proved to be fairly ef fective in the various compacting and vibro-driving operations , but at the same time not particularly versatile . In fact , it has been observed that as the type of earth to be handled varies , in particular as the relative composition and humidity varies , to obtain optimal results , tool vibrations of di f ferent intensities are necessary . Consequently, vibration devices are available on the market adapted to the di f ferent types of earth, each one characteri zed by a di f ferent mass of the relative eccentric body, since as said mass varies , the intensity of the vibration generated also varies . In this way, however, every time a di f ferent type of earth is encountered, the vibration device has to be changed .

It is evident that said solution is fairly costly for the sector operators , who are thus obliged to purchase and maintain a plurality of di f ferent vibration devices ; it also entails considerable downtime when the vibration device has to be replaced .

The problem of effectively handling di f ferent types of earth, at the same time limiting working costs and times , is currently unresolved, and represents an interesting challenge for the applicant .

SUMMARY OF THE PRESENT INVENTION

The present invention concerns a vibration device . In particular, the present invention concerns a vibration device connectable to an operating machine for a relative movement and designed to cause the vibration of a tool . The drawbacks described above are solved by the present invention according to at least one of the following claims .

According to some embodiments of the present invention, a vibration device is provided, said device being connectable to an operating machine for a relative movement , said device comprising :

- support means couplable to said operating machine ,

- a vibrating unit comprising a vibrating frame supported by said support means and designed to support a tool , and a rotating member supported by said vibrating frame and drivable in rotation relative to said vibrating frame around a first axis by first actuation means to generate a vibration of said tool , said rotating member having a respective centre of mass , characteri zed in that said rotating member comprises a first body and a second body hinged to said first body along a second axis substantially parallel to said first axis , and second actuation means designed to rotate said second body relative to said first body around said second axis to move said centre of mass relative to said first axis .

According to an embodiment as described above , said second actuation means comprise a linear actuator having a first end connected to said first body and a second end connected to said second body .

According to an embodiment as described above , said linear actuator is housed in a corresponding seat provided in said first body .

According to an embodiment as described above , said second body is rotatable relative to said first body between a first extreme position, in which said centre of mass is arranged at a first minimum distance from said first axis , and a second extreme position, in which said centre of mass is arranged at a second maximum distance from said first axis .

According to an embodiment as described above , said first distance is substantially null .

According to an embodiment as described above , said device comprises a hydraulic motor carried by said vibrating frame , said hydraulic motor actuating said first actuation means .

According to an embodiment as described above , said support means comprise a support frame couplable with said operating machine , said support frame supporting said vibrating frame , shock absorber means being interposed between said support frame and said vibrating frame to prevent propagation of a vibration of said vibrating unit to said operating machine .

According to an embodiment as described above , said rotating member comprises a third body hinged to said first body along said second axis , said second actuation means being designed to rotate said third body relative to said first body around said second axis to move said centre of mass relative to said first axis .

According to an embodiment as described above , said first body comprises a shaft extending along said first axis and a disc fitted on said shaft , said second body being hinged to said disc .

According to an embodiment as described above , said second body has a first slot , said shaft engaging said first slot . BRIEF DESCRIPTION OF THE FIGURES Further characteristics and advantages of the vibration device according to the present invention will appear clearer from the following description, provided with reference to the attached figures which illustrate at least one non-limiting embodiment example thereof . In particular :

- figure 1 is a three-dimensional perspective view of a preferred non-limiting embodiment of a vibration device according to the present invention;

- figure 2 is a front elevation view of figure 1 ;

- figure 3 is a lateral elevation view of figure 1 ;

- figure 4 is a section view of figure 3 according to line IV- IV;

- figure 5 is a three-dimensional perspective view of a rotating member of a vibration device according to the present invention; figure 6 is a three-dimensional perspective view of figure 5 from a di f ferent observation point ;

- figure 7 is a lateral elevation view of figure 5 ;

- figure 8 is a lateral elevation view of figure 5 with parts removed for clarity .

DETAILED DISCLOSURE OF THE PRESENT INVENTION

In figures 1 , 2 and 3 , the number 1 indicates overall a vibration device .

With reference to figure 1 , the device 1 firstly comprises support means 2 couplable , preferably in a reversible manner, with an operating machine known and not illustrated, for the movement of the device 1 overall .

The support means 2 comprise a support frame 20 couplable with the operating machine ; the support frame 20 is composed in turn of a first lateral plate 201 and a second lateral plate 202 facing each other and thus defining a direction of development which is indicated below, for the sake of convenience , as "vertical" , and an upper plate 203 arranged perpendicular to the lateral plates 201 , 202 j oining them at the top and defining a direction which below will be indicated for the sake of convenience as "hori zontal" . The first lateral plate 201 is portalshaped, and therefore has a first base portion 2010 to which the upper plate 203 is connected, and a first front arm 2011 and a first rear arm 2012 extending vertically from the first base portion 2010 . Analogously, also the second lateral plate 202 is portal-shaped, and has a second base portion 2020 , a second front arm 2021 (visible in figure 4 ) and a second rear arm 2022 .

The device 1 further comprises a vibrating unit 3 supported by the support frame 20 by means of shock absorber means 4 configured to prevent the vibrations of the vibrating unit 3 from spreading to the support frame 20 and therefore to the operating machine .

The vibrating unit 3 comprises a vibrating frame 30 supported by the support frame 20 and designed to support a tool 31 , and a rotating member 32 (visible in figures 4 to 8 ) supported by the vibrating frame 30 so that it can be driven in rotation relative to it around a first axis A by first actuation means 5 , so as to selectively generate a circular vibration of the entire vibrating unit 3 , and therefore also of the tool 31 . Preferably, the first axis A is arranged hori zontally .

In further detail , the vibrating frame 30 comprises a first front portion 301 , a second front portion (not visible in the figure ) , a first rear portion 303 and a second rear portion 304 facing respectively the inner faces of the first front arm 2011 , the second front arm 2021 , the first rear arm 2012 and the second rear arm 2022 . The shock absorber means 4 comprise in particular a first front antivibration element 41 connected to , and interposed between, the first front arm 2011 and the f irst front portion 301 , and analogously a second front anti-vibration element 42 (visible in figure 4 ) , a first rear anti-vibration element 43 and a second rear anti-vibration element 44 interposed between the respective arms of the support frame 20 and the relative portions of the vibrating frame 30 facing them . Said anti-vibration elements 41 , 42 , 43 , 44 can be made of rubber and, in addition to providing the support connection between the vibrating unit 3 and the support frame 20 , they isolate as far as possible the vibrating unit 3 from the support frame 20 in order to prevent the vibrations of the vibrating unit 3 from spreading to the operating machine .

The vibrating frame 30 further comprises an upper portion 305 facing the lower face of the upper plate 203 , while the shock absorber means 4 also comprise a rubber buf fer element 45 fixed on the lower face of the upper plate 203 to avoid any risk of impact between the upper portion 305 of the vibrating frame 30 and the upper plate 203 of the support frame 20 .

The tool 31 is connectable to a lower portion of the vibrating frame 30 , and in the embodiment shown in the figures consists of a compactor plate arranged hori zontally . Alternatively, the compactor element can consist of a compactor roller, a pile driver or a grab . Furthermore , the rotating member 32 is driven in rotation relative to the vibrating frame 30 around the first axis A by first actuation means 5 , which consist preferably of a hydraulic motor 5 mounted on the vibrating frame 30 , which can be preferably remote-operated by an operator who also controls the movement of the operating machine .

With reference to figure 4 , the rotating member 32 comprises firstly a shaft 320 supported by the vibrating frame 30 by means of a first bearing 307 and a second bearing 308 , the shaft 320 being drivable in rotation around the first axis A relative to the vibrating frame 30 by the first actuation means 5 . The rotating member 32 comprises a disc 321 fitted in an intermediate position on the shaft 320 so that it is integral with it : the assembly of the shaft 320 and the disc 321 therefore forms a first rigid body 3200 freely rotatable relative to the vibrating frame 30 around the first axis A.

The disc 321 can have a toothed outer surface : in this way the disc 321 can mesh with the corresponding discs of any additional rotating members , identical to the rotating member 32 and not illustrated in the figure . Said additional rotating members can characteri ze the device 1 when it is necessary to operate the tool 31 with a vibration having greater amplitude than the one obtainable only with the rotating member 32 : in this case the toothed outer surface of the disc 321 , meshing with analogous toothed surfaces of the additional rotating members , is able to drive also the latter in rotation, exploiting the torque delivered by the first actuation means 5 .

With reference to figures 5 to 8 , the rotating member 32 further comprises a second rigid body 322 hinged to the first body 3200 , in particular to the disc 321 , along a second axis B parallel to and distinct from the first axis A, preferably by means of a pin inserted in a first hole 3211 provided in the disc 321 and in a second hole 3221 provided in the second body 322 . The rotating member 32 comprises second actuation means 324 configured to rotate the second body 322 relative to the first body 3200 around the second axis B : in this way the second actuation means 324 allow the position of the centre of mass of the rotating member 32 relative to the first axis A to be varied as required . In particular, the second body 322 is rotatable relative to the first body 3200 between a first extreme position, in which the centre of mass of the rotating member 32 is at a first minimum distance from the first axis A, and a second extreme position, in which the centre of mass o f the rotating member 32 is at a second maximum distance from the first axis A, while also being able to stably assume all the intermediate positions . Preferably the first distance is substantially null , and therefore when the second body 322 is in the first extreme position, the centre of mass of the rotating member 32 lies on the first axis A.

When the centre of mass of the rotating member 32 l ies on the first axis A, the driving in rotation of the rotating member 32 does not result in a vibration of the entire vibrating unit 3 , since the rotating member 32 i s in a "balanced" configuration : said configuration is useful when the first actuation means 5 drive the rotating member 32 in rotation from a standstill , since a minimum torque is required . When the centre of mass of the rotating member 32 does not lie on the first axis A, on the other hand, the driving in rotation of the rotating member 32 results in a circular vibration which is transmitted through the bearings 307 , 308 to the entire vibrating unit 3 , since the rotating member 32 is in an "unbalanced" configuration . In particular, the amplitude of the vibration generated increases as the distance of the centre of mass of the rotating member 32 from the first axis A increases , and is maximum when the second body 322 i s in the second extreme position .

The second actuation means 324 comprise in particular a linear actuator 324 , preferably of hydraulic type , which has a first end 3241 connected to the first body 3200 ( in particular to the disc 321 ) and a second end 3242 (visible in figure 8 ) connected to the second body 322 , in particular to one end of the second body 322 opposite the second hole 3221 . Preferably, the linear actuator 324 is housed in a corresponding seat 3210 provided in the first body 3200 , in particular in the disc 321 .

Also the linear actuator 324 can be preferably remote- operated by the same operator who controls the movement of the operating machine : in this way it is possible to modi fy in remote mode the overall extension of the linear actuator 324 , thus moving the second body 322 relative to the first body 3200 in a position chosen as required, also intermediate , between the first extreme position and the second extreme position, thus adj usting as required the position of the centre of mass o f the rotating member 32 relative to the first axis A.

Preferably, the second body 322 has a first slot 3220 configured to house a first end of the shaft 320 , so that the movement of the second body 322 relative to the first body 3200 results in a relative movement of the shaft 320 inside the first slot 3220 .

Preferably, the rotating member 32 further comprises a third rigid body 323 hinged to the first body 3200 , in particular on the opposite face of the di sc 321 relative to the second body 322 , along the second axis B, preferably by means of the pin inserted in the first hole 3211 which is also inserted in a third hole 3231 provided in the third body 323 . The third body 323 is preferably identical to the second body 322 , and therefore has a second slot 3230 to house a second end of the shaft 320 , while the second actuation means 324 are configured also to rotate the third body 323 relative to the first body 3200 around the second axis B, simultaneously with the second body 322 : in this way the centre of mass of the rotating member 32 can be moved to an even greater distance from the first axis A, obtaining vibrations with even greater amplitude .

On the basis of the above description, it can be easily understood that the device 1 is perfectly able to resolve the drawbacks of the state of the art illustrated above .

Each time a di f ferent type of earth to be compacted is encountered, it is suf ficient for the operator of the operating machine to appropriately control the second actuation means 324 to modi fy the position of the centre of mass of the rotating member 32 relative to the first axis A. In this way, in fact , while not modi fying the overall mass of the rotating member 32 , its moment of inertia relative to the first axis A is modi fied, obtaining vibrations of di f ferent amplitude without replacing the vibration device , thus reducing both the maintenance costs and working times .