ITMI20111890A1 - SHOCK - Google Patents

Description

â € œSHOCK ABSORBERâ €

FIELD OF THE TROVATO

The present invention relates to a shock absorber, in particular a shock absorber that can be used to slow down the opening or closing stroke of doors, sliding doors, such as cabinet or furniture doors, mobile systems for accessing rooms, sliding partitions, drawers for furniture, etc.

In detail, one or more shock absorbers according to the invention are suitable for being interposed between the fixed structure of a wardrobe with sliding doors and the respective door in order to appropriately dampen the opening / closing forces of the same and limit the impacts of the mobile body on the respective jamb.

STATE OF THE ART

As is known, various types of shock absorbers specifically intended for use on sliding door wardrobes are widely available on the market.

The shock absorbers used in furniture items are for example mounted in correspondence with devices or mechanisms for opening or closing doors and / or shutters, in order to slow down the opening and / or closing stroke of the sliding element near the end of stroke of the latter.

In general, shock absorbers have a cylinder filled with oil inside which a suitable piston guided by a respective rod moves by sliding.

In general (but not necessarily) the shock absorbers are mounted on the fixed frame that carries and guides the sliding element and interact with the latter in correspondence with the final closing / opening phases of the same.

In detail, the leaf or sliding door, when it reaches the limit switch, interacts with the piston (or cylinder) of the loaded shock absorber which slows down the stroke of the sliding element itself due to the friction that occurs. they generate inside the cylinder during the movement of the piston, linked to the leakage of the oil contained in the internal chamber of the piston itself.

In other words, the shock absorbers in accordance with the state of the art consist of a cylinder inside which a substantially sealed piston can slide on the cylinder, which compresses a predetermined fluid, typically oil, following pressure increase. The oil begins to draw in correspondence with a slight gap between the piston and the cylinder, generating a frictional force between them due to the viscosity of the oil.

Working in this way, the shock absorber slows down the stroke of the sliding element and absorbs any blows between the frame and the element itself.

In particular, it is known from the document EP 198180 to produce a shock absorber in which the piston is made up of two elements, one fixed to the piston rod itself, the other movable relative to the first. These two elements allow two conditions to be defined: a first damping condition in which the second element substantially occludes each passage for the oil, allowing the latter exclusively to seep between the internal surface of the cylinder and the external surface of the piston and a second reset condition in which, vice versa, the oil can flow through openings with less hydrodynamic resistance.

In this way, by means of a simple structure, it is possible to obtain the aforementioned damping effect in one direction and a faster rearming in the opposite direction.

Although the aforementioned shock absorber allows rapid rearming, it is nevertheless affected by some drawbacks and / or operating limits and has therefore proved to be improved in some respects.

First of all, the piston is geometrically complex with a consequent increase in costs. Secondly, the piston allows to modulate the damping force only in relation to the closing speed of the leaf and therefore to the pressure that is generated inside the cylinder, attributing to the shock absorber a lower sensitivity on the closing of the leaf. .

It is also known from document EP 1563763, a further improvement of the device highlighted above in which the piston once again consists of only two movable elements relatively to each other.

The first element attached to the piston rod itself has a head portion peripherally equipped with four chamfers designed to create preferential paths for the oil; this first element continues in an axial direction with a shank made in one piece to the aforementioned portion, but with a reduced section and ending with a plurality of elastic hooks.

The head of the piston and the elastic elements define an annular seat in which a hollow cylinder of axial development is engaged, lower than that of the seat, which, in the damping condition, abuts against the head portion of the piston, occluding the aforementioned preferential passages for oil and therefore offering a higher resistance to movement; vice versa in the reset condition this cylindrical element is held between the aforementioned elastic elements, but spaced from the main portion of the piston in such a way that oil passages with less resistance are defined and therefore reset takes place extremely quickly.

However, even this last type of shock absorbers is affected by some drawbacks and / or operating limits and has therefore proved to be improved in some respects.

Also in this case the structure of the piston is still geometrically complex. Moreover, with a guiding surface of the piston (head portion) shaped against the internal wall of the cylinder which is not developed axially and therefore with a risk of generating oscillations or vibrations, especially in the event of small misalignments of the cylinder rod. These misalignments could lead to oil leaks and therefore affect the functionality of the shock absorber which could drain in a short time and require replacement.

Also in this last patent described, the "shock absorber allows to generate a well defined damping force during the closing and / or opening condition of the door." In particular, previously described, the closing force that is generated is exclusively linked to the variation of the closing speed of the leaf and therefore to the increase of the pressures inside the cylinder.

As previously mentioned, this attributes to the shock absorber a low sensitivity on the closing of the door and therefore limited in order to guarantee a soft approach of the door in the closed condition.

PURPOSE OF THE FIND

The aim of the present invention is therefore to solve one or more of the drawbacks and limitations of the previous solutions.

A first objective of the invention is to provide a shock absorber that allows a soft approach of the door during the closing phase of the same.

A further object is to provide a shock absorber of a simple conception which nevertheless exhibits considerable sealing reliability, particularly without significantly increasing production and / or assembly costs.

A further object of the invention is also to ensure compliance with the dimensions and overall dimensions of shock absorbers in use today so as to be able to intervene by replacing previous generation shock absorbers which are now discharged or defective.

These and other objects which will become clearer in the course of the following description are substantially achieved by a shock absorber in accordance with one or more of the following aspects.

In a 1st aspect, a shock absorber (1) is provided for furniture items, comprising:

> a jacket (2) having a substantially elongated shape extending along a prevalent development direction (3) and having a first and a second end (4, 5), said jacket (2) defining inside it a housing seat (6 );

> at least one fluid disposed inside the housing seat (6); > at least one piston (7) comprising a movable body (8) engaged inside the housing seat (6) and which defines a first and a second chamber (A, B) inside the latter in fluid communication with each other, said piston (7) further comprising a stem (9) integrally connected with said movable body (8) and at least partially protruding from said jacket (2), said piston (7) being movable by relative sliding with respect to the jacket (2) along the prevailing development direction (3) of the same, said piston (7) being configured to define a damping condition in which, following the stress of the rod (9) by means of a thrust force (Fs) external direction, in particular having an inward direction in said housing seat (6), the mobile body (8) moves in a first direction of travel and, interacting with the fluid, allows the passage of the latter, from the first to the second chamber generating a resist force body (Fr) opposing the external thrust force (Fs),

said movable body (8) comprising a first and a second element (10, 11) movable relatively to each other which, during the damping condition, are both configured to move, at least for a distance, relative to the stem (9) along the direction of prevailing development (3) and generate respectively a first and a second resisting force (FI, F2) which contribute to the formation of the resisting force (Fr) of the mobile body (8).

In a 2nd aspect in accordance with the previous aspect, the first and second elements (10, 11), during the damping condition, are configured to move relative to each other and with respect to the stem (9) between at least a first condition in which generate a first overall resisting force (Frj), a second condition in which they generate a second overall resisting force (Fr2), said second overall resisting force (Fr2) being greater than the first overall resisting force (Frj), and a third condition in which generate a third overall resisting force (Fr3), said third overall resisting force (Fr3) being greater than the second overall resisting force (Fr2).

In a 3rd aspect in accordance with the previous aspect, the piston (7) comprises an engagement element (16) connected and carried integrally by the rod (9) of the piston itself, called first and second element (10, 11), in the first condition, being spaced with respect to said engagement element (16) while in the second condition the first element (10) is substantially in contact with the engagement element (16) and the second element (11) is spaced from the first element (10), said first element (10), in the third condition, being substantially in contact with the engagement element (16) and the second element (11) being substantially in contact with the first element (10) . In a 4th aspect in accordance with the 2nd or 3rd aspect the first element (10) has a first passage opening (10d) to allow a passage of fluid coming from the first chamber (A) and directed towards the second chamber ( B).

In a 5th aspect in accordance with Î “preceding aspect the passage light (10d) of the first element (10) is an internal passage light.

In a 6th aspect in accordance with any of the aspects from the 2nd to the 5th the second element (11) presenting a respective second passage port (11le) to allow a passage of fluid coming from the first chamber (A) and directed towards the second chamber (B).

In a 7th aspect in accordance with the previous aspect, the passage light (Ile) of the second element (11) is an internal passage light.

In an 8th aspect in accordance with the 6th or 7th aspect in the first condition the first passage opening (1 Od) of the first element (10) and the second passage opening (Ile) of the second element (11) allow the fluid passage.

In a 9th aspect in accordance with any of the aspects from the 6th to the 8th in the second condition and in the third condition the first passageway (10d) of the first element (10) is substantially occluded, increasing the resistance to passage of fluid.

In a 10th aspect in accordance with any of the 2nd to 9th aspects, the housing seat (6) has a prismatic shape.

In an 11th aspect in accordance with the previous aspect, the housing seat (6) has a substantially cylindrical shape.

In a 12th aspect in accordance with the previous aspect, the first and second elements (10, 11) are at least partially shaped against the housing seat (6) of the jacket (2), said first element (10) having a lateral surface external (12) which in cooperation with the housing seat (6) defines a lateral leakage port (13) which allows the fluid to leak from the first to the second chamber (A; B).

In 13th aspect in accordance with 1â € ™ 11 <0> or 12th aspect the second element (11) has an external lateral surface (14) which in cooperation with the housing seat (6) defines a lateral leakage opening (15) which allows the fluid to seep from the first to the second chamber (A, B).

In a 14th aspect in accordance with any of the 12th to 13th aspects in the first condition the first port of the first element (10) and the second port of the second element (11) allow the passage of fluid, in the second condition the first passage opening (10d) of the first element (10) is substantially occluded and the fluid leaking through said lateral leakage opening (13), in the third condition the first passage opening (10d) of the first element (10) is substantially occluded, the second element (11) being substantially in contact with the first element (10) and the fluid leaking through said lateral leakage port (13) of the first element (10) and through said lateral leakage port (15) of the second element (11).

In a 15th aspect according to any of the preceding aspects the fluid is an incompressible fluid.

In a 16th aspect in accordance with the previous aspect the fluid is oil.

In a 17th aspect in accordance with any of the aspects from 13 ° to 16 ° the lateral leakage opening (13) of the first element (10) has an area, according to a cross section to the prevailing development direction (3) , equal to or less than the area of the lateral leakage opening (15) of the second element (11).

In an 18th aspect in accordance with any of the aspects from the 2nd to the 17th the first and second elements (10, 11), during the passage from the first to the second condition, are configured to slide relative to the stem (9) and long the prevailing development direction (3).

In a 19th aspect in accordance with the previous aspect in which the first and second elements (10; 11) are configured to slide along the prevailing development direction respectively with a first and second sliding speed. In a 20th aspect according to the previous aspect, the first scrolling speed of the first element (10) is higher than the second scrolling speed of the second element (11).

In a 21st aspect according to any of the 2nd to 20th aspects, the ratio between the first overall resisting force (Fri) and the second overall resisting force (Fr2) is less than 0.5.

In a 22nd aspect according to any of the 2nd to 21st aspects the ratio of the first overall resisting force (Fri) to the second overall resisting force (Fr2) is less than 0.3.

In a 23rd aspect according to any of the 2nd to 22nd aspects the ratio of the first overall resisting force (Fr ^ to the second overall resisting force (Fr2) is less than 0.1.

In a 24th aspect according to any of the 2nd to 23rd aspects the ratio of the second overall resisting force (Fr2) to the third overall resisting force (Fr3) is less than 1.

In a 25th aspect according to any of the 2nd to 24th aspects, the ratio of the second overall resisting force (Fr2) to the third overall resisting force (Fr3) is less than 0.9.

In a 26th aspect according to any of the 2nd to 25th aspects, the ratio of the second overall resisting force (Fr2) to the third overall resisting force (Fr3) is less than 0.85.

In a 27th aspect according to any of the 2nd to 26th aspects, the ratio between the first overall resisting force (Frj) and the third overall resisting force (Fr3) is less than 0.4.

In a 28th aspect according to any of the 2nd to 27th aspects, the ratio of the first overall resisting force (Fri) to the third overall resisting force (Fr3) is less than 0.2.

In a 29th aspect according to any of the 2nd to 28th aspects, the ratio of the first overall resisting force (Fri) to the third overall resisting force (Fr3) is less than 0.07.

In a 30 ° aspect in accordance with any of the preceding aspects, the housing seat (6) has a substantially cylindrical shape.

In a 31 ° aspect in accordance with any one of the aspects from 12 ° to 30 ° the external lateral surface of the first and second element (10, 11) presenting respectively, according to a cross section to the prevailing development direction (3), a shape substantially circular.

In a 32 ° aspect in accordance with the previous aspect the shape of the first element (10) having a diameter greater than or equal to the diameter of the shape of the second element (11).

In a 33 ° aspect in accordance with any of the aspects from 13 ° to 32 ° the external lateral surface (12) of the first element (10) has an extension, along the prevailing development direction (3), equal to or greater of the extension of the external lateral surface (14) of the second element (11).

In a 34 ° aspect in accordance with the previous aspect, the ratio between the extension of the external lateral surface (12) of the first element (10), along the prevailing development direction (3), and the extension of the external lateral surface (14) of the second element (11), along the prevailing development direction (3), is superior

to the .

In a 35 ° aspect in accordance with the 33 ° or 34 ° aspect the ratio between the extension of the external lateral surface (12) of the first element (10), along the prevailing development direction (3), and the extension of the external lateral surface (14) of the second element (11), along the prevailing development direction (3), is greater than 1.5.

In a 36 ° aspect according to the 33 ° or 34 ° or 35 ° aspect the ratio between the extension of the external lateral surface (12) of the first element (10), along the prevailing development direction (3), and the extension of the external lateral surface (14) of the second element (11), along the prevailing development direction (3), is greater than 1.7.

In a 37th aspect in accordance with any of the preceding aspects, the piston (7) is configured to define a reset condition in which the piston (7) itself, in motion in a second direction of travel opposite to the first direction of travel and in interaction with the fluid, it allows the passage of the latter from the second to the first chamber (B; A) with consequent displacement of the stem (9) in the outgoing direction from said housing seat (6).

In a 38th aspect in accordance with any of the 3rd to 37th aspects the first and second elements (10, 11) are committed to the commitment element (16) and being aligned along the prevailing development direction (3 ).

In a 39th aspect in accordance with any of the aspects from the 3rd to the 38th the first element (10) is turned towards said first extremity (4) while said second element (11) is turned towards said second extremity (5 ).

In a 40 ° aspect in accordance with any of the aspects from the 3rd to the 39 ° the engagement element (16) is configured to allow said first and second element (10, 11) to flow along the development direction prevalent (3) for a predetermined run.

In a 41st aspect in accordance with any of the aspects from the 3rd to the 40th the commitment element (16) comprises a base (16a) which develops along the prevailing direction of development (3) between a lower surface (16b), facing the first end (4) of the liner (2), and an upper surface (16c), facing the second end (5) of the liner (2), said engagement element (16) further comprising a body (16d) connected with said base (16a) and emerging transversely, in particular orthogonally, from the upper surface (16c) of the latter.

In a 42 ° aspect in accordance with the previous aspect, the first and second element (10, 11) presenting respective passing seats (17, 18) suitable for allowing the engagement of the first and second elements (10, 11) to the body (16d) of the engagement element (16), said first and second element (10, 11) being able to slide along said body (16d) for the predetermined stroke.

In a 43 ° aspect in accordance with the 41 ° or 42 ° aspect the engagement element (16) includes a stop portion (19) arranged on one end of this body (16d) facing the second end ( 5), said upper surface (16c) and said abutment portion (19) of the engagement element (16) defining the predetermined stroke of the first and second element (10, 11).

In a 44th aspect in accordance with any of the 41st to 43rd aspects during the transition from the first to the second condition, said first element (10) is configured to move between the base (16a) of the engagement element (16) and said second element (11) while said second element is configured to move between the stop portion (19) and the second element (11), and in which, during the passage between the second and third condition, said first element (10) moves integrally with the stem (9) while said second element (11) moves between said first element (10) and said abutment portion (19).

In a 45 ° aspect in accordance with any of the 3 ° to 44 ° aspects the piston (7) comprises a predetermined number of axial grooves (26) extending substantially along a direction parallel to the prevailing development direction (3) of the jacket ( 2), said axial grooves (26) being configured to define a passage opening inside the mobile element to allow the passage of fluid both in the damping condition and in the reset condition.

In a 46 ° aspect in accordance with the previous aspect the axial grooves (26) are arranged on the first element (10) and / or on the second element (11) and / or on the engagement element (16).

In a 47 ° aspect the engagement element (16) comprises a predetermined number of axial grooves (26), said movable body (8) comprising at least one closing body (10c) able to abut, during the damping condition, to at least one of the axial grooves (26) of the engagement element (16), the abutting of the closing body (10c) with at least one of the axial grooves (26) of the engagement body (16) defining limiting the passage of fluid inside the mobile body (8) with respect to the passage of fluid in the reset condition.

In a 48 ° aspect in accordance with the previous aspect, the first element (10) comprises said closing body (10c) able to abut, during the damping condition, to at least one of the axial grooves (26) of the element commitment (16).

In a 49th aspect in accordance with any of the aspects from the 42nd to the 48th the seats (17; 18) of the first and second element (10, 11) define in cooperation with the element of commitment (16) a € ™ passage opening which is configured to allow the passage of fluid between the two chambers during the damping and / or reset condition, said first and second element (10, 11) being configured to allow the dimensional variation of said opening passage during the relative movement of said first and / or second element (10, 11) with respect to the engagement element (16), the dimensional variation of the passage opening causes a variation of the resisting force of passage of the fluid between the two bedrooms.

In a 50 ° aspect in accordance with the previous aspect during the damping condition the passage opening is at least partially occluded while during the rearming condition the passage opening is totally free.

In a 51st aspect in accordance with any of the 41st to 50th aspects, the commitment element (16) comprises a first portion (16e) connected to the base (16a) of the commitment element itself, called the first portion (16e) having a substantially cylindrical shape extending parallel to the prevailing development direction (3) of the jacket (2) and having a diameter (D1) smaller than the diameter of the base (16a).

In a 52 ° aspect in accordance with the previous aspect the engagement element (16) comprises a second portion (16i) connected with the first portion (16e) of the engagement element (16) itself, called second portion (16i) having a substantially cylindrical shape extending parallel to the prevailing development direction (3) of the jacket (2) and having a diameter (D2) smaller than the diameter of the base (16a).

In a 53 ° aspect in accordance with the previous aspect the diameter (D2) of the second portion (16i) of the engagement element (16) is smaller than the diameter (DI) of the first portion (16e).

In a 54 ° aspect in accordance with the 52 ° or 53 ° aspect the first and / or second portion (16e, 16i) are configured to abut the through seat of the first and / or second element (10, 11) during the condition of damping to allow a variation of the passage of fluid inside the mobile body (8) and consequently allow a variation of the damping force of the piston (7).

In a 55th aspect in accordance with any of the 3rd to 54th aspects the engagement element (16), in particular the body (16d) of the engagement element, includes at least one extending guide (24) along the prevailing development direction (3) of the jacket (2), said guide (24) being configured to receive in engagement said first and / or second element (10, 11) and being configured to guide the latter in sliding along the predetermined race. In a 56 ° aspect in accordance with the preceding aspect the guide (24) comprises at least one groove, in particular a through groove passing through the body (16d) of the engagement element (16).

In a 57th aspect in accordance with the 55th or 56th aspect, the first element (10) comprises at least one projection (23) adapted to engage with said guide (24) which guides said first element (10) in motion and preventing to the latter to rotate relative to the commitment element (16).

In a 58 ° aspect in accordance with any one of the aspects from 42 ° to 57 ° the first element (10) comprises two projections (23) arranged in correspondence with the through seat (17) and having an inward direction with respect to the latter, said protrusions (23) being substantially facing each other which define, in correspondence with the protrusions themselves, an opening having a substantially â € œHâ € shape.

In a 59 ° aspect in accordance with any one of the aspects from 55 ° to 58 ° the second element comprises at least one projection (20) able to engage with the guide (24) which guides said second element (11) in motion and preventing to the latter to rotate relative to the element of commitment (16).

In a 60 ° aspect in accordance with the previous aspect, the second element (11) comprises two protrusions (20) arranged in correspondence with the through seat (18) and having an inward direction with respect to the latter, called protrusions (20) being substantially facing each other, they define, in correspondence with the protrusions themselves, an opening having a substantially â € œHâ € shape.

In a 61 ° aspect in accordance with the previous aspect the projections (20) of the second element (11) contact the abutment portion (19) of the engagement element (16) and allow to keep the second element engaged ( 11) with the body (16d) of the engagement element (16).

In a 62 ° aspect in accordance with any one of the 42 ° to 61 ° aspects, the through seat (17) of the first element (10) has a substantially cylindrical shape which extends from a lower surface (10a) of the first element itself, facing the first end (4) of the jacket (2) to an upper surface (10b), of the first element itself, facing the second end (5) of the jacket (2).

In a 63 ° aspect in accordance with any of the 42 ° to 62 ° aspects the upper surface (16c) of the engagement element (16) is configured to contact the lower surface (10a) of the first element (10) to limit its travel during the second and third conditions.

In a 64 ° aspect in accordance with any one of the 42 ° to 63 ° aspects, the through seat (18) of the second element (11) has a substantially cylindrical shape which extends from a lower surface (11a) of the second element itself, facing the first end (4) of the jacket (2) to an upper surface (11b), of the second element itself, facing the second end (5) of the jacket (2).

In a 65 ° aspect in accordance with any of the aspects from the 3rd to the 64th, the first element (10) comprises a predetermined number of reliefs (21) emerging from a lower surface (10a) of the latter, called reliefs ( 21), during the damping condition, in particular during the second and third condition, by contacting an upper portion (16c) of the engagement element (16) and allowing to space the lower surface (10a) of the first element ( 10) from the upper surface (16c) of the engagement element (16).

In an aspect 66 in accordance with any one of the aspects from the 3rd to the 65th the predetermined number of reliefs (21) during the second and third condition, contacting said upper portion (16c) of the engagement element (16) and allowing to distance the lower surface (10a) of the first element (10) from the upper surface (16c) of the engagement element (16).

In a 67th aspect in accordance with any of the preceding aspects, the second element (11) comprises a predetermined number of reliefs (22) emerging from a lower surface (11a) of the latter, called reliefs (22), during the damping and / or reset condition, contacting an upper surface (10b) of the first element (10) and allowing the upper surface (10b) of the first element (10) to be spaced from the lower surface (11a) of the second element (11). In a 68 ° aspect in accordance with any of the preceding aspects, the shock absorber comprises at least one compensation element (25) arranged inside the housing seat (6) substantially in correspondence with the first end (4) of the jacket ( 2), said compensation element (25) being configured to compensate for the volume variation caused by the rod during the movement of the piston (7).

In a 69 ° aspect in accordance with the previous aspect, the compensation element (25) is configured to absorb the shock from the fluid, at the beginning of the first condition, generated by the stress of the piston (7) through the external force (Fs).

In a 70 ° aspect in accordance with the 68 ° or 69 ° aspect the compensation element (25) comprises at least one sponge, in particular a closed cell sponge.

In a 71 ° aspect in accordance with any of the aspects from 3 ° to 70 ° the stem (9) has a substantially elongated shape comprising a first and a second extremity (9a, 9b), said stem (9) having, in correspondence of said first end (9a), a connection portion (9c) which allows engagement with the engagement element (16), said stem (9) further comprising a thrust portion (9d) arranged in correspondence of said second end (9b) and which is configured to receive and transmit to the mobile body (8) the external thrust forces (Fs) during the damping and / or rearming phase.

In a 72 ° aspect in accordance with any of the preceding aspects, the shock absorber comprises a sealing device (27) arranged at the first end (4) of the jacket (2) configured to prevent the leakage of fluid from the inside of the housing seat (6) towards the outside.

In a 73 ° aspect in accordance with the previous aspect the sealing device (27) comprises:

> at least one closing element (28) having a lateral flange (29) coupled to the housing seat (6) in correspondence with the first terminal end (4) of the jacket (2) and a central seat (30) suitable for housing and allowing the passage of the stem (9);

> at least one sealing gasket (31), arranged inside the jacket (2) and in contact with the closing element (28), said sealing gasket (31) including a passage opening (32) for the stem (9) in correspondence with which there is a scraping portion (33) active on said stem (9) and configured to prevent the leakage of fluid towards the outside; And

> a retaining element (34), in particular cooperating with the jacket (2), active on the sealing gasket (31) to allow the latter to be kept in the operating position, said retaining element (34) also presenting It is a central seat (35) adapted to allow the passage of the stem (9).

In a 74 ° aspect in accordance with the previous aspect, the holding element (34) has a base (35a) able to cooperate with a corresponding undercut (36) of the jacket (2) disposed inside the housing seat ( 6) configured to determine a resting condition for the retaining element (34) itself, and consequently of the gasket (31), and to prevent movements from the first terminal end (4) towards the second terminal end (5).

In a 75 ° aspect in accordance with the previous aspect, the base (35a) has a disc shape whose lateral surface is substantially counter-shaped to the housing seat (6) of the jacket (2), said retaining element (34 ) comprising a thrust portion (37) arranged in correspondence with the central seat (35) and emerging transversely with respect to the latter, in particular emerging along the prevailing development direction (3) of the liner (2), said thrust portion (37) having a contact surface (38) facing towards said stem (9), said scraping portion (33) also having a substantially discoidal shape whose lateral surface is substantially counter-shaped to the housing seat (6) of the liner (2), the scraping portion (33) being arranged in correspondence with the central seat (35) of the retaining element (34) and emerging transversely with respect to said central seat (35), in particular emerging along the prevailing development direction (3) of the shirt (2).

In a 76 ° aspect in accordance with the 73 ° or 74 ° or 75 ° aspect the gasket (31) is interposed, in operating conditions, between the closing element (28) and the retaining element (34 ) so as to define a packing designed to hold the gasket in position, at least along the prevailing development direction (3). In an aspect 77 in accordance with any one of the aspects from 73 ° to 76 ° the gasket (31) comprises a sealing element (39) emerging transversely from the gasket (31) itself and which substantially defines a closed ring around the stem, said sealing element (39) being configured to prevent, in conditions of use, the leakage of the fluid arriving from the jacket (2) and passing between the gasket (31) and the closing element (28).

In a 78 ° aspect in accordance with any of the aspects from 73 ° to 77 ° the scraping portion (33) of the gasket (31) comprises, in longitudinal section, at least one deformable fin (40) capable of acting under pressure on the stem (9) and having a free end (41) elastically connected to the stem (9), the fin (40) developing from a first end (42) placed at a predetermined distance from the stem (9) up to € ™ free end (41) attached to the stem (9).

In a 79 ° aspect in accordance with any of the aspects from 73 ° to 78 ° the closing element (28) embracing at least in part said gasket (31). In an 80 ° aspect in accordance with any of the aspects from 73 ° to 79 ° the closing element (28) comprises a connection portion (28a) adapted to engage with a relative connection portion of the jacket (2), said connection portions allowing to lock along the prevailing development direction (3) said closing element (28) and consequently said gasket (31) and said retaining elements (34).

In an 81 ° according to the previous aspect, the connecting portions of the liner (2) and of the closure element (28) are threaded portions able to cooperate with each other.

In an 82 ° aspect in accordance with any one of the aspects from the 37 ° to the 81 ° the first and second element (10, 11), in the reset condition, generating a resetting force (Fa) that opposes the sliding piston (7). In an 83 ° aspect in accordance with the previous aspect, the resetting resistant force (Fa) being lower than the resisting force (Fr) generated by the first and second elements (10, 11) in the damping condition,

In an 84 ° aspect in accordance with any of the aspects from the 37 ° to the 83 ° the first and second elements (10, 11), in the reset condition, allowing a passage of fluid from the second to the first chamber (B; A ) greater than the passage of fluid from the first to the second chamber (A; B), during the damping condition.

In an 85th aspect in accordance with any of the aspects from the 37th to the 84th the first and second elements (10, 11), in the rearm condition, being close together, in particular in contact with each other.

In an 86 ° aspect in accordance with the previous aspect, the upper surface (11b) of the second element (11), in the reset condition, being substantially in contact with the stop portion (19) of the engagement element ( 16).

In an 87th aspect in accordance with any of the aspects from the 37th to the 86th, the rearm phase takes place in less than 5 seconds.

In an 88th aspect in accordance with any of the aspects from the 37th to the 87th, the rearm phase takes place in less than 3 seconds.

In an 89th aspect in accordance with any of the aspects from the 37th to the 88th, the rearm phase takes place in less than 2 seconds.

In a 90 ° aspect in accordance with any of the preceding aspects, the housing seat (6) has at least one discharge area (43) comprising at least one cavity (44) extending along the prevailing development direction (3), called cavity ( 44) being configured to allow greater leakage of fluid, in a damped and reset condition, with respect to the passage of fluid generated by the housing seat (6) outside the discharge area (43).

In a 91 ° aspect in accordance with the previous aspect, the unloading area (43) is arranged in correspondence with the second end (5) of the jacket (2) and is able to ensure the piston (7) to perform all the pre-established stroke in the damping phase.

In a 92 ° aspect in accordance with any of the preceding aspects, the jacket (2) has an auxiliary opening (2b) arranged at the second end (5) and which places the housing seat (6) in fluid communication ) with the external environment, said shock absorber (1) including a top cap (52) configured to prevent, in conditions of use of the shock absorber itself, leakage of fluid from said housing seat (6) towards the ™ external environment.

In a 93 ° aspect in accordance with the previous aspect, said top cap (52) comprises at least one abutment portion (57) configured to cooperate with a respective abutment portion (2c) of the jacket (2) and prevent, under conditions of use of the shock absorber, the leakage of fluid between the housing seat (6) and the external environment.

In a 94 ° aspect in accordance with the previous aspect, the abutment portion (57) of the top cap (52) is configured to cooperate with the abutment portion of the jacket (2) to define a contact area, called zone contact having a closed profile arranged around said auxiliary opening (2b). In a 95 ° aspect in accordance with the 93 ° or 94 ° aspect, the stop portion (57) develops along a prevalent development plane, transversal, in particular, orthogonal to the prevailing development direction (3) of the shock absorber ( 1) or in which the abutment portion (57) has a substantially conical shape, the abutment portion (2c) of the jacket (2) being at least partially counter-shaped to the abutment portion of the top cap (52) to define said contact area .

In a 96 ° aspect in accordance with any one of the 92 ° to 95 ° aspects the top cap (52) comprises at least one fastening portion (58) configured to engage with a respective fastening portion (2d) of the liner (2) , said fixing portion (58) of the top cap (52) being configured to constrain the top cap itself to the liner (2) and to ensure cooperation between the abutment portions (2c; 57) of the liner (2) and of the plug respectively upper (52).

In a 97 ° aspect in accordance with the preceding aspect the fixing portion (58) comprises a threaded portion or a quick coupling.

In a 98 ° aspect in accordance with any of the 92 ° to 97 ° aspects the top cap (52) comprises at least one maneuvering portion (59) configured to allow positioning and / or locking the top cap (52) itself on said jacket (2), said maneuvering portion (59) comprising a hexagonal seat and / or cross shapes and / or star shapes and / or knurled portions.

In a 99th aspect in accordance with any of the preceding aspects, the jacket (2) is at least partially made of plastic material, in particular in which said jacket (2) is entirely made of plastic material.

In a 100th aspect in accordance with any of the 92nd to 99th aspects the top cap (52) is at least partially made of plastic, particularly in the top cap is entirely made of plastic. In a 101st aspect, a piece of furniture is provided, in particular a wardrobe, comprising: a fixed structure, at least one movable closing element relative to the fixed structure, at least one shock absorber (1), in accordance with any of the aspects from 1 ° to 100 °, interposed between the fixed structure and the closing element and which is configured to assist the movement of the closing element at least for a part.

In a 102 ° aspect in accordance with the previous aspect, the jacket (2) of the shock absorber (1) is connected to the fixed structure while the stem (9) is configured to receive the closing element in support .

In a 103 ° aspect in accordance with the 101 ° or 102 ° aspect the closing element is a sliding door.

In a 104 ° aspect a support device (100) for furniture items is provided, comprising: a support frame (101), which can be interposed between a fixed structure, for example a fixed structure of a wardrobe, and at least one mobile element , for example a sliding door, movable relative to the fixed structure to define in cooperation with the latter an opening and closing phase; at least one shock absorber (1) in accordance with any of the aspects from 1st to 100th engaged with said support frame (101) configured to contact, in the opening and / or closing phase of the mobile element, and apply on the latter is a damping force that allows to manage the approach or departure of the mobile element with respect to the fixed structure.

In a 105 ° aspect in accordance with the previous aspect, the device comprises a support element (109) engaged with the support frame (101) and with the shock absorber (1), said support element (109) being configured to receive the movable element, in the closing phase, and transmit the stress to the shock absorber (1), said support element (109) being furthermore configured to engage at least for a predetermined length and in the opening phase said movable element and exploit the movement of the latter to determine a condition for resetting the shock absorber (1).

In a 106 ° aspect in accordance with the 104 ° or 105 ° aspect the support frame (101) comprises a locking portion (102) adapted to engage said shock absorber (1), the locking portion (102) comprises at least one Opening (108) from which the rod (9) of the shock absorber (1) at least partially protrudes, adapted to engage said support element (109). In a 107 ° aspect in accordance with the previous aspect, the support frame (101) further comprises at least a guide portion (103) configured to engage and guide said support element (109), said portion guide (103) presenting at least a first section in which said support element (109) engages said mobile element and at least a second section in which the support element (109) is at least partially spaced from the mobile element allowing the The support element itself to disengage the mobile element.

BRIEF DESCRIPTION OF THE DRAWINGS

Some embodiments and some aspects of the invention will be described hereinafter with reference to the accompanying drawings, provided for indicative and therefore not limiting purposes only, in which:

> Figure 1 is a perspective view of a shock absorber, according to a first embodiment, partially sectioned in order to show the elements present inside;

> Figure 2 is a perspective view of a jacket of the shock absorber of figure 1;

Figure 3A and 3B are perspective views of a partially sectioned shock absorber according to a second embodiment;

> Figures 4 and 5 are exploded views of a sealing device;

> Figure 6 is a sectional view of a shock absorber according to a third embodiment;

> Figure 7 is a section view of a shock absorber according to a fourth embodiment;

> Figure 7 A is a detail of Figure 7;

> Figure 7B is a detail of Figure 7 which illustrates the passage of oil in the condition of rearming of the shock absorber;

> Figure 8 is a detail of the sectional view of Figure 6;

> Figures 9A-9B and 9C are views of an engagement element arranged throughout the shock absorber liner;

> Figures 10A and 10B are perspective views of a first mobile element arranged inside the shock absorber;

> Figures 11A and 11B are perspective views of a second mobile element arranged inside the shock absorber;

> Figure 12 is a partially sectioned front view of the shock absorber of Figure 1 in an initial condition;

> Figure 13 is a partially sectioned front view of the shock absorber of Figure 1 during a starting condition; > Figure 13 A is a detail of Figure 13;

> Figure 14 is a partially sectioned front view of the shock absorber of Figure 1 during an intermediate damping condition;

> Figure 14A is a detail of Figure 14;

> Figure 15 is a partially sectioned front view of the shock absorber of Figure 1 during a condition of maximum damping;

> Figure 15 A is a detail of Figure 15;

> Figure 16 is a partially sectioned front view of the shock absorber of Figure 1 in a limit switch condition;

Figure 17 shows a support device adapted to house a shock absorber of the preceding figures;

> Figure 18 shows an exploded view of the device of Figure 17;

Figure 19 shows a longitudinal section of the device of Figure 17 in a first working condition;

Figure 20 shows a longitudinal section of the device of Figure 17 in a second working condition;

Figures 21A, 21B show an auxiliary support element used in the device of Figure 17;

> Figures 22A, 22B show a support element used in the device of Figure 17.

> Figure 23 is a perspective view of a shock absorber according to a further embodiment;

> Figure 24 is a perspective view of the shock absorber of figure 23 partially sectioned in order to show the elements present inside;

> Figure 25 is a detail of a sectional view of the shock absorber in figures 23 and 24.

DETAILED DESCRIPTION

With reference to the figures cited with 1, a shock absorber has been indicated as a whole in accordance with the invention.

The shock absorber described below is particularly suitable for damping motion during the closing and / or opening phases of sliding doors, sliding doors, movable walls, drawers or in any case articles, generally of furniture, in which there is a element in motion with respect to a fixed frame and whose movement must be damped to avoid blows to the structure.

The shock absorber 1 first of all comprises a jacket 2 defining inside it a housing seat 6 which houses a fluid, generally an incompressible fluid, for example an oil. Alternatively, other liquids (and / or possibly also gases) can be used according to requirements. The fluid is designed to interact and cooperate with a piston 7 movable inside the jacket 2 to define the various motion conditions of the shock absorber itself. In particular, the piston 7 comprises a movable body 8 housed in the housing seat 6 and a stem 9 connected integrally to the movable body 8 and protruding at least partially from the jacket 2.

In the accompanying figures, a jacket 2 is shown sectioned along a plane parallel to the prevailing development direction 3 to allow the details arranged inside to be viewed. In particular, the jacket 2 has an elongated shape extending between a first and a second extremity 4, 5 along a prevalent development direction 3. In more detail, as can be seen from the accompanying figures, the jacket 2 is defined, in a non-limiting way, by a cylindrical tubular body, in particular having a cylindrical symmetry. Also with regard to the housing seat 6, it can be noted that also the latter has, in a non-limiting way, a substantially cylindrical shape developing along the prevailing development direction 3.

The jacket 2 has, at least on one of the two ends 4, 5, a main opening 2a which allows, during the assembly of the shock absorber 1, to insert the piston 7 and / or the fluid inside the seat housing 6. Figure 2 shows a preferential form of the shock absorber 1 in which the main opening 2a of the jacket 2 is arranged in correspondence with the first end 4 and places the housing seat 6 in fluid communication with the € ™ external environment.

As for the first end 4, also in correspondence with the second end 5 there is, in a non-limiting way, an auxiliary opening 2b useful for the introduction and / or emission of the fluid from the housing seat 6. In correspondence with the auxiliary opening 2b, the shock absorber 1 can comprise a top cap 52 configured to prevent, in use conditions, the leakage of fluid through said auxiliary opening 2b towards the external environment. The jacket 2, at the second end 2 comprises an abutment portion 2c adapted to cooperate with the upper cap 52 in order to prevent the leakage of fluid through said auxiliary opening 2b from the housing seat 6 towards the external environment. More in detail, the abutment portion 2c of the jacket is configured to cooperate with an abutment surface 57 of the top cap: these portions are at least partially counter-shaped so as to define a contact position defining a closed profile around the auxiliary opening 2b of the jacket 2, in this way the upper cap 52 can allow the fluid to be sealed inside the housing seat 6.

In a first embodiment schematized for example in Figure 7, the abutment portion 2c is substantially a transversal flat portion, in particular orthogonal, to the prevailing development direction 3. The abutment portion 57 of the top cap 52 also has it is a substantially flat configuration so as to define, in cooperation with the abutment portion 2c of the jacket 2, said contact area.

At least an internal portion of reduced section with respect to the abutment surface 2c is intended to be inserted with interference inside the access channel to the compartment containing the shock-absorbing fluid. To avoid leaks and / or leaks of the fluid, the cap 52 is welded (for example by heat or ultrasound) in an assembly station during the production phases of the shock absorber. In a further embodiment, shown schematically in figures 23, 24 and 25, the abutment positions 2c, 57 of the jacket 2 and the top cap 52 respectively have a conical shape. As can be seen from the accompanying figures, the jacket 2 also comprises a fixing portion 2d which allows the upper cap 52 to be constrained in correspondence with the second end 5 of the jacket 2. The fixing portion 2d of the jacket 2 can comprise, for example, threaded portions 58 In order to allow the connection by rotation of the top cap 57 to the jacket 2, the top cap itself comprises a maneuvering portion 59 configured to allow positioning and / or locking of the same on said jacket 2. In figures 23 and 25 the portion of maneuver 59 is, in a non-limiting way, a hexagonal seat able to engage with an Allen key. Alternatively, the maneuvering portion 59 can comprise other shapes suitable for allowing the cap to rotate, such as cross shapes, star shapes or knurled portions which can be engaged by means of a suitable tool (embodiments not shown in the accompanying figures).

The conical shape 57 of the cap 52 allows to increase the pressure which is generated in the closing phase of the cap 52 itself since rotations of the threaded portion 58 help to bring the cap closer to the jacket 2, increasing the tightness to the fluid.

By operating in this way it is possible to obtain the mechanical seal without welding, thus avoiding a critical phase of the production process; furthermore, the particular shape of the reciprocal coupling areas also allow the use of plastic materials for the jacket and for the cap 52.

Returning to the detailed description of the jacket 2, it is possible to observe that the housing seat 6 has, at the first end 4, a sealing area 47 intended to engage a sealing device 27 configured to prevent, in use conditions, the leakage of fluid through the main opening 2a towards the external environment. The sealing device 27 will be better described later.

More in detail, the sealing area 47 comprises a connection portion 48 configured to lock the sealing device 27 in a predetermined axial position along the prevailing development direction 3. For example, the connection portion 48 can comprise a threaded portion or a plug-in portion for quick coupling elements or to be used for bonding / (thermo) welding of the sealing system itself.

It should be noted that the jacket 2 includes, in a non-limiting way, a shoulder 36 suitable to act as a stop for the sealing device 27 and prevent the latter from moving along the prevailing development direction 3 of the jacket 2, in particular direct movements approaching the second extremity 5.

The connection portion 48 and the shoulder 36 substantially allow the sealing device 27 to be packed and prevent the latter from moving directly along the prevailing development direction 3.

Continuing to detail the housing seat 6, it is possible to note that the latter also comprises a compensation zone 49, adjacent to the sealing zone 47, arranged to engage at least one compensation element 25 configured to compensate for the volume variation generated by the rod 9 inside the housing seat 6 itself during the movement of rod 9.

To better understand the functioning of the compensation element 25 it is useful to describe the shock absorber in more detail in the operating condition. In fact, the latter, in conditions of use, works in a fluid-tight manner: the use of an incompressible fluid, such as oil, does not allow changes in volume inside the housing seat 6 and being the rod 9 connected solidly to piston 7, during the movement of the latter inside the housing seat, a volume variation is produced generated by the presence of a greater or lesser volume of the rod 9, depending on how much portion of the itself is housed inside the shirt, or is located outside the shirt itself.

The compensation element 25, as previously described, allows to compensate for the volume variation generated by the presence of the volume of the stem 9. The compensation element 25 can include, for example, but not limited to, a closed cell sponge which substantially has alveoli containing compressible fluid, such as for example air. As the stem penetrates inside the housing seat 6, the compression of the compressible fluid, such as air, present inside the alveoli allows precisely to compensate for the volume of the stem 9.

According to the compensation capacity of the sponge and the working conditions of the shock absorber 1, it is possible to insert only one or two or more sponges inside the compensation area 49 (condition shown in figures 3 A and 3B). The sponge allows the passage of oil, elastically compensating for the volume variations that are generated during motion.

Alternatively, even if with the addition of structural complication, it is possible to use various known compensation systems such as for example the insertion of dedicated compensation chambers containing compressible fluid.

In addition to this, the compensation element 25 is configured to absorb the shock generated by the fluid inside the jacket 2 at the beginning of the stress on the piston 7 by means of the external force Fs. As a matter of fact, as briefly described above, the sliding door, during the opening of the latter, contacts the rod 9 of the shock absorber 1: the moving door contacts the rod 9 and generates an impact on the latter.

The impact propagates inside the fluid until it reaches the walls of the housing 6. In particular, the impact could damage the closing elements of the housing located near the first and second openings 2a , 2b.

The compensation element 25 allows to at least partially dampen the shock wave that develops in the fluid and therefore to protect the closing elements, in particular the sealing device 27.

As can be seen in the accompanying figures, the compensation zone 49 is, in a non-limiting way, adjacent and subsequently disposed to the sealing zone 47, in particular between the sealing zone 47 and a stop portion 50.

The stop portion 50 is substantially defined by a protrusion emerging from the internal surface of the jacket 2. The stop portion 50 divides the compensation zone 49 from an operative zone 51 adjacent and subsequently arranged to the compensation zone itself and arranged towards the second end 5 (see figure 2). The operating area 51 represents the portion of the housing seat 6 in which the piston 7 operates directly. In particular, the operating area represents the portion of the housing seat 6 inside which the piston 7 operates. Inside the operative zone 51, the piston 7 cooperates with the housing seat 6 and interacts with the fluid in order to generate the damping force Fr.

From a geometric point of view, the operating area 51 has, in a non-limiting way, a circular section extending from the stop portion 50 to the second end 5 of the liner 2 thus defining an operating stroke C of the piston 7 useful for obtaining the action damping (see for example Figure 6).

As can be seen from the accompanying figures, the operating area 51 can comprise an unloading area 43 arranged at the end of the operating stroke C of the piston 7 and therefore arranged near the second end 5. The unloading area 43 has a substantially circular section, having a larger diameter with respect to the diameter of the section in correspondence with the operating area 51.

The housing seat 6 defines, in cooperation with the piston 7 and in correspondence with the discharge area 43, a gap greater than the gap defined by the cooperation between the housing seat 6 and the piston 7, in correspondence with the operating area 51 at the outside the unloading area 43. In the unloading area 43 a resisting force Fr is generated which is lower than the resistive force Fr generated by the piston inside the operating area outside the unloading area 43: in fact inside the discharge area 43, the interspace between piston 7 and housing seat 6 there is a greater leakage of fluid compared to the leakage that occurs in the operating area outside the discharge area. The unloading area 43 therefore allows a reduction in the resisting force Fr generated by the piston 7 at the end of the operating stroke in order to ensure that the piston 7 itself reaches the end-of-stroke position. Alternatively, as shown in figures 6 and 7, it is possible to increase the size of the interspace with respect to that of the operating area 51 by creating only one or more axial grooves extending along the prevailing development direction 3 (see figure 6) instead of increasing the whole section; alternatively, it is also possible to create a taper that allows to increase the circular section approaching the second end 5 (see figure 7).

In addition to the relief areas 43 illustrated, useful for reducing the resisting force Fr during the damping condition, it is possible to alternatively perform transverse grooves or a groove and helical development (both not shown in the accompanying figures).

As previously mentioned, the main opening 2a is adapted to receive a sealing device 27 which, as can be seen from the accompanying figures 3A, 3B, 4 and 5, is constituted by a closing element 28 which comprises once a connection portion 28a adapted to couple directly with the connection portion 48 in the sealing area 47.

The connection portion 28a can comprise, as shown in Figure 3A, a threaded plug having a threaded portion 29a and an abutment portion 29b.

Alternatively, the closing element 28 can comprise, as shown in figure 3B, a snap coupling by adopting an annular rib 29 intended to engage in a corresponding counter-shaped seat of the liner (see also figure 2).

The connection portion 28a allows the sliding of the closing element 28 to be blocked along the prevailing development direction 3 of the jacket 2.

The closing element 28, as visible in figure 5, has a substantially cylindrical hollow shape extending along the prevailing direction of development and comprising a central seat 30 able to house and allow the passage of the stem 9.

In more detail, as shown in figure 4, the closing element 28 comprises a disk-shaped base 53, in which the central seat 30 is present. Along the external perimeter of the closing element 28 emerge some lateral support walls 54 which externally abut the housing seat 6 while inside they define a cavity 55 (visible in figure 5) of the closing element 28 itself.

The sealing device 27, as can be seen from the accompanying figures, also comprises a gasket 31 arranged in contact with the closing element 28. The gasket 31 has a substantially discoidal shape which also has a passage opening 32 to allow the passage of the rod 9. The gasket 31 comprises a scraping portion 33 able to adhere to the rod 9 to prevent oil leaks from the housing seat 6. More specifically, the gasket 31 comprises a support base 3 able to contact the end part of the lateral support wall 54 of the closing element 28.

From the base 3 la emerges a coupling wall 3 lb directed towards the closing element 28 and able to fit inside the cavity 55 of the latter. On the extremity of the coupling wall 3 1b a sealing wall 3 le extends, extending transversely to the prevailing development direction 3 and having an inward direction with respect to the housing seat 6. The sealing wall 3 le, in the assembled condition of the Shock absorber 1, counted the base 54 of the closing element 28. As can be seen in figure 4, the passage opening 32 of the gasket is arranged on the sealing wall 3 le.

The scraping portion 33 extends transversely from the sealing wall 31c, which, as previously mentioned, contacts the rod 9 of the piston 7, preventing the leakage of oil from the side wall of the rod 9 itself. As can be seen from the accompanying figures, the scraping portion 33 of the gasket 31 has, in longitudinal section, at least one deformable fin 40 capable of acting under pressure on the stem 9 and having a free end 41 elastically abutting to the stem 9. Fin 40 developing from a first end 42 placed at a predetermined distance from the stem 9 up to the free end 41 abutting the stem 9.

As visible from the sectional views of Figures 6 and 7, the gasket 31 can comprise a sealing element 39 emerging from the sealing wall 3 l and towards the closing element 28. In particular, the sealing element 39 substantially defines a closed ring around the stem 9 (visible in figure 4) which abuts to a respective sealing seat 28b of the closing element itself. The sealing element 39 is configured to prevent, in conditions of use, the leakage of the fluid arriving from the jacket 2 and passing between the gasket 31 and the closing element 28.

The gasket 31 is generally made of a soft material (softer than the material defining the further elements 34 and 54.

The gasket 31 is generally made of natural or synthetic rubber or similar materials suitable for fluid sealing.

The sealing device 27 further comprises a retaining element 34 arranged in contact with the gasket 31 and arranged on the opposite side to the closing element 28 with respect to the gasket 31 itself.

Figures 4 and 5 show a preferential shape of the retaining element 34 which presents, in a non-limiting way, a substantially discoidal shape also presenting a central seat 35 suitable for allowing the passage of the stem 9. The retaining element 35 comprises a base 35a adapted to cooperate with the corresponding shoulder 36 of the jacket 2 and configured to determine a resting condition for the retaining element 34 itself. In more detail, the retaining element 34 rests on one side against the shoulder 36, on the other it contacts the support base 3 la of the gasket 31. In this way, the retaining element 34 and the closure 28 allow packing the gasket 31 and preventing the latter from axial movements along the prevailing development direction 3. As can be seen from the accompanying figures, the retaining element 34 has a thrust portion 37 which, in conditions of Use, it is designed to ensure the correct positioning of the gasket 31 between the closing element 28 and the retaining element itself, as well as to guarantee the contact between the coupling wall 3 lb of the gasket 31 with the internal surface of the cavity 55 of the ™ closing element 28.

In particular, the thrust portion 37 emerges from the base 35a transversely, in particular orthogonally, to the latter in the direction of the gasket 31. The thrust portion 37 has a substantially cylindrical shape, substantially conical, with a taper turned towards said gasket 31.

Continuing to analyze the components present inside the housing seat 6, it is possible to note that the latter includes, but is not limited to, the compensation element 25, the characteristics of which have been previously described. As can be seen from the accompanying figures, the compensation element 25 is interposed between the entertainment element 34 and a stop element 56 engaged inside the stop portion 50.

The stop element 56 is, in a non-limiting way, a disc having axial openings extending along the prevailing development direction 3 which allow the passage of fluid through the stop element 56 itself. The stop element 56, resting on the stop portion 50, prevents movement of the compensation element 25 along the prevailing development direction 3 approaching the second end 5. In particular, it is the stop element that it separates the compensation zone 49 from the operative zone 51, in particular it separates the compensation element 25 from the piston 7.

Inside the operative area 51 there is the piston 7 which comprises a movable body 8 defining inside the operative area 51 a first and a second chamber A, B in fluid communication with each other. The piston 7, as previously mentioned, also comprises said rod 9 which is integrally connected with the movable body 8 and at least partially protruding from the jacket 2.

The piston 7 is movable by sliding relative to the jacket 2 along the prevailing development direction 3 of the same and is configured to define a damping condition in which, following the stress on the rod by means of an external thrust force Fs having an inward direction in said housing seat 6, the mobile body 8 moves in a first direction of travel and, interacting with the fluid, allows the passage of the latter, from the first to the second chamber A, B generating a resisting force Fr which opposes to the external thrust force Fs. In other words, when the piston 7 is pressed towards the inside of the housing seat 6, or approaching the second end 5, the oil contained in it increases in pressure and begins to leak, with resistance from piston foramina: the leakage dissipates energy and allows to cushion the possible closing of a sliding element with respect to a fixed frame.

The piston also defines a reset condition, in which the latter moves in a second direction of travel opposite to the first direction of travel and generating a reset force Fa which, as for the damping condition, opposes the motion of the piston 7.

More in detail, the piston 7 in the reset condition, is in interaction with the fluid and guarantees the latter to flow from the second chamber to the first chamber with consequent displacement of the rod 9 in the outgoing direction from the housing seat 6.

Both in the damping condition and in the reset condition the fluid can flow from one chamber to the other from one or more openings on the mobile element 8, arranged, in a non-limiting way, in the central part of the latter. In addition to flowing from said openings, there is a slight lateral leakage of the fluid between the external lateral surface of the mobile body 8 and the internal surface of the jacket 2.

More in detail, during the reset condition there is the passage of fluid substantially only through the central openings of the mobile body, while during the damping condition there is a reduced passage of fluid from the central openings of the mobile body 8 and a lateral leakage.

The various forces involved and the different conditions generated by the movable body 8 will be better described once the elements that make up said movable body have been analyzed in detail.

Analyzing the structure of the stem 9 (see for example Figure 6), it is possible to observe that the latter has a substantially elongated shape comprising a first and a second end 9a, 9b. The stem 9 having, at the first end 9a, a connection portion 9c which allows engagement with the movable body 8.

Similarly, on the second end 9b there is a thrust portion 9d configured to receive and transmit to the mobile body 8 the external thrust forces Fs.

More specifically, the connection portion 9c can comprise a threaded portion adapted to abut a respective connection portion of the movable body 8. Alternatively, it is possible to glue or press-fit the stem 9 into the connection portion of the movable body 8 in a manner that the stem can be rigidly constrained to the mobile body 8.

The piston 7 also comprises an engagement element 16 integrally carried by the rod 9 and which engages said movable body 8 (Figure 8). More specifically, the engagement element 16 constrains the mobile body 8 to itself, allowing the latter to slide inside the housing seat along the prevailing direction 3 for the predetermined stroke C and to move relative to the stem 9.

More in detail (see figures 9A - 9C), the engagement element 16 is constituted by a base 16a, having a substantially cylindrical shape, which extends along the prevailing development direction 3 between a lower surface 16b, facing towards the first end 4 of the jacket 2, and an upper surface 16c, facing the second end 5 of the jacket 2. The base 16a comprises a connection portion 16m adapted to abut the connection portion 9c of the stem 9.

The engagement element 16 further comprises a body 16d integrally connected with the base 16a and emerging transversely, in particular orthogonally, from the upper surface 16c of the latter.

More in detail, the body 16d of the engagement element 16 also has a substantially cylindrical shape with a smaller diameter than the diameter of the base 16a. The body 16d is configured to engage said movable body 8 and, as previously mentioned, allow the latter to move relative to the stem 9, in particular relative to the base 16a of the engagement element itself.

Even more in detail, the body 16d comprises a first portion 16e having a substantially cylindrical shape and connected with the base 16a of the engagement element 16 and a second portion 16i connected with the first portion 16e and subsequently arranged along the latter. the prevailing development direction 3. As can be seen from the accompanying figures, the first portion 16e has a smaller diameter than the base diameter while the second portion 16i has, in a non-limiting way, a smaller diameter than the first portion 16e.

The body 16d of the engagement element 16 comprises a guide 24 extending along the prevailing development direction 3 of the liner 2 and which is configured to receive in engagement said movable body 8 and to guide the latter in sliding along a predetermined operating stroke CI. As can be seen from the accompanying figures, the guide 24 is arranged on the second portion 16i of the body 16d of the engagement element 16.

The guide 24 is, in a non-limiting way, a groove, in particular a groove passing through said body 16d and which extends for a portion of the second portion equal to the extension of the operating stroke C1 of the mobile body 8.

The through grooves of the guide 24 made on the second portion of the body 16d define two lateral shoulders 161 joined at the tops, facing the second end 5, by a stop portion 19. As can be seen from the top view of figure 9B, the shoulders and the relative portion of the stop 19 define a substantially â € œHâ € profile.

The engagement element 16 includes, but is not limited to, a predetermined number of axial grooves 26 extending along the prevailing development direction 3 and which define, in cooperation with the housing seat 6 and / or with the Mobile element 8 a passage port configured to allow the passage of fluid between the two chambers during the damping and resetting condition.

In more detail, as can be seen from the accompanying figures, the axial grooves 26 are arranged partly on the base 16a and partly on the body 16d of the engagement element. In particular, the axial grooves 26 comprise notches 16f arranged on the first portion 16e of the body 16d having, in a non-limiting way, a "V" shape developing, in a non-limiting way, along the entire development of the first portion 16e. The axial grooves 26 further comprise perimeter through openings 16g and internal through openings 16h.

The perimeter through openings 16g are arranged in correspondence with the outer perimeter of the base 16a and which substantially shape the perimeter of the base 16a.

As for the internal through openings 16h, the latter are arranged inside the base 16a and define a closed profile. As can be seen from the accompanying figures, the perimeter openings 16g are arranged, in a non-limiting way, facing each other to allow, during the damping and reset conditions, a symmetrical passage of fluid from one chamber to the other. other than the engagement element 16. In the same way, the internal openings 16h are also arranged facing each other to allow, during the damping and reset conditions, a symmetrical passage of fluid from a chamber other than the commitment element 16.

More specifically, the base 16a includes two perimeter through openings 16g facing each other and two internal through openings 16h also facing each other.

From the geometric profile, the perimeter through openings 16g have a circular arc profile while the internal through openings 16h have a substantially circular sector shape.

The axial grooves 26, as previously mentioned, facilitate the passage of fluid from one chamber to the other both in the damping condition and in the reset condition.

As previously mentioned, the movable body 8 is bound to the engagement element and movable relative to the latter. More in detail, the movable body 8 comprises a predetermined number of elements engaged with the body 16d of the engagement element 16 and which are both movable by sliding and independently of each other along the prevailing development direction 3 of the liner 2 relative to the Engagement element 16. In this way the elements engaged with the body 16d can assume a plurality of different operating conditions of the shock absorber 1.

More in detail, as can be seen from the accompanying figures, the mobile body 8 comprises a first and a second element 10, 11.

The first element 10 is at least partially counter-shaped to the housing seat 6 of the jacket 2. In particular, the first element 10 has a substantially cylindrical shape extending along the prevailing development direction 3 between a lower surface 10a of the first element 10, facing towards the first end 4 of the jacket 2, and an upper surface 1 Ob of the first element 10, facing the second end 5 of the jacket 2 (figs. 10A, 10B).

The first element 10 also comprises an external lateral surface 12 which mates with the housing seat 6 and which in cooperation with the latter defines a lateral leakage opening 13 (fig. 8).

The first element 10 also comprises a through seat 17 which, in a non-limiting way, has a substantially cylindrical shape extending along the prevailing development direction 3 and passing through said first element 10. The through seat 17 allows to receive the body 16d of the engagement element 16. As can be seen from the accompanying figures, the first element 10 comprises, in a non-limiting way, two projections 23 substantially arranged in correspondence with the upper surface 10b of the first element 10 and emerging from the latter transversely to the prevailing direction of development 3 of the jacket 2 in a direction entering with respect to the through seat 17 of the first element 10.

The projections 23 engage inside the guide 24 of the engagement element 16: in this way the guide 24 allows the first element 10 to be guided and therefore allows the relative sliding between the first body 10 and the commitment 16.

The protrusions 23 are, in a non-limiting way, substantially facing each other and define a correspondence of the protrusions themselves an opening having a substantially â € œHâ € shape suitable for accommodating the shoulders 161 of the engagement element 16. The abutment portion 19 is configured to ensure the engagement of the first element 10 with the body 16d of the engagement element 16.

As can be seen from the sectional view of figure 7, the two protrusions 23 define two substantially inverted "L" portions symmetrical with respect to the axis of the first element 10 itself and facing each other. The part extending along the prevailing development direction 3 abuts externally to the housing seat and internally is configured to abut the first portion 16e of the body 16d. The part of the â € œLâ € transversal to the prevailing development direction 3 forms a portion of the upper surface 10b of the first element 10 useful for supporting said second element 11.

The seat 17 has a substantially cylindrical shape counter-shaped to the first portion 16e of the engagement element 16. More specifically, the seat 17 has a diameter greater than the diameter of the first portion 16e of the engagement element 16 to allow, during the cooperation between the first element 10 and the engagement element 16, to define a meatus in which there is a leakage of fluid.

More in detail, the seat 17 of the first element 10, during the damping step, abuts the first portion 16e and allows to reduce the passage of fluid between the two chambers and substantially allow the leakage of said fluid between the lateral surface 12 of the first element 10 and the housing seat 6.

During the reset phase, the seat 17 and the first element 10 are distant and, as shown in figure 7, the fluid can flow throughout the seat 17 and easily pass through the slots 16f and the axial grooves 26 of the commitment 16. The fluid dynamics analysis will be better analyzed later in the description.

As can be seen from the accompanying figures, the first element 10 further comprises a predetermined number of projections 21 emerging from the lower surface 10a of the first element 10 itself.

More specifically, the projections 21 have, in a non-limiting way, a cone shape with the base connected to the lower surface 10a of the first element 10. The projections 21 are configured to allow, both in the damping condition and in the reset condition, to distance the first element 10 from the engagement element 16. More in detail, the projections 21 allow the upper surface 16c of the engagement element 16 to be spaced from the lower surface 10a of the first element 10: in this way the contact between the surfaces and the cohesion of the two due to the â € œsuckerâ € effect.

The first element 10 also comprises, in a non-limiting way, a closing body 10c arranged on the lower surface 10a of the first element itself and emerging transversely from said lower surface 10a. The closing body 10c is configured to abut the internal through openings 16h of the engagement element 16 so as to reduce the passage of fluid during the damping condition of the piston 7, a condition which will be better detailed hereinafter.

It should be noted that the closing body 10c does not contact the internal surface of the through openings 16h, but defines a small meatus from which the fluid can flow. In this way it is possible to avoid a suction effect which would be established between the first element 10 and the engagement element 16 during the movement of the piston 7.

As for the first element, also the second element 11 is at least partially counter-shaped to the housing seat 6 of the jacket 2. In particular, the second element 11 has a substantially cylindrical shape extending along the prevailing development direction 3 between a lower surface 11a of the second element 11, facing the first end 4 of the jacket 2, and an upper surface 11b of the second element 11, facing the second end 5 of the jacket 2 (see Figures 11A and 11B).

The second element 11 has an external lateral surface 14 which mates with the internal surface of the housing seat 6 to define a lateral leakage opening 15.

The second element 11 comprises a substantially cylindrical through seat 18 which extends along the prevailing development direction 3 and passes through said second element 11.

The through seat 18 allows to receive the body 16d of the engagement element 16. As can be seen from the accompanying figures, the second element 11 comprises, in a non-limiting way, two protrusions 20 arranged substantially in correspondence with the lower surface 11a of the second element 11 and emerging from the latter transversely to the prevailing development direction 3 of the jacket 2 in a direction entering with respect to the through seat 18 of the second element 11.

The projections 20 engage inside the groove 24 of the engagement element 16 which allows said second element 11 to be guided during motion.

The projections 20 are substantially facing each other and define in correspondence with the projections themselves an opening having a substantially â € œHâ € shape.

The projections 20 of the second element 11, in addition to allowing the engagement of the second element itself with the groove 24 of the engagement element 16, are configured to abut, during the reset condition, to the stop portion 19: in this in this way the projections 20 prevent the disengagement of the second element 11 with the body 16 and consequently prevent the disengagement of the first element 10 from the body 16 as well.

As can be seen from the sectional view of figure 7, the two protrusions define two substantially inverted â € œLâ € portions symmetrical with respect to the axis of the second element 11 itself and facing each other. The portion of the â € œLâ € extending along the prevailing development direction 3 abuts externally to the housing seat 6 while internally it accommodates the body of the engagement element 16. The portion of the â € œLâ € extending transversely with respect to the development direction prevailing element 3 forms a portion of the lower surface 11a of the second element 11 useful for supporting said second element, first element and useful for engaging the abutment portion 19 and acting as a limit switch.

As can be seen from the accompanying figures, the second element 11 comprises, in a non-limiting way, a predetermined number of projections 22 emerging from the lower surface 11a of the second element itself.

More specifically, the projections 22 have, in a non-limiting way, a cone shape with the base connected to the lower surface 11a of the second element 11. The projections 22 are configured to distance the second element 11 from the first element 10 both in the damping condition is in the reset condition. In greater detail, the reliefs 22 allow the upper surface 10b of the first element 10 to be spaced from the lower surface 11a of the second element 11: in this way, contact between the surfaces and the cohesion of the two due to the â € œsuckerâ € effect are prevented.

Before moving on to the description of the different configurations of the first and second element 10, 11 during the damping and rearming condition, it is possible to provide some quantitative data concerning the geometry of the mobile body 8.

First of all, it is possible to observe in the detail of figure 8, that the lateral leakage opening 13 of the first element 10 is lower than the leakage opening 15 of the second element 11. In this way, the first element 10 is able to develop a force resistant, due to the leakage of the fluid between the housing seat 6 and the external lateral surface 12 of the first element itself, greater than the damping force, due to the leakage of the fluid between the housing seat 6 and the external lateral surface 14 of the second element 11 itself. In particular, it is relevant for the purposes of evaluating the resistive force to consider the extension of the lateral surfaces of leakage of the two elements.

As can be seen from the accompanying figures, the external lateral surface 12 of the first element 10 has an extension, along the prevailing development direction 3, greater than the extension of the external lateral surface 14 of the second element 11.

In particular, the ratio between the extension of the external lateral surface 12 of the first element 10 along the prevailing development direction and the extension of the external lateral surface 14 of the second element along the prevailing development direction is greater than 1, in particular higher than 1.4, even more particularly higher than 1.6.

In an embodiment variant, not shown in the accompanying figures, it is possible to attribute the same leakage opening to the first and second element and play on the extension of the lateral surfaces to allow differentiation of the resisting forces of the two elements.

In another construction variant, not shown in the accompanying figures, it is possible, in order to differentiate the resisting forces of the two elements, to attribute different leakage openings to the first and second element and to maintain the same extension of the lateral surfaces.

Obviously, as in the present case, also a combination in the sizing differences of the leakage opening and the extension of the lateral surfaces can lead to the desired effects of variation of resistance to the passage of fluid.

The fluid, in addition to flowing from the passage openings defined by the cooperation between the lateral surfaces 12, 14 with the housing seat, passes through the seats 17, 18 of the first and second element 10, 11. In fact, the fluid passage from said seats it helps to define (regulate) the resisting force of the first and second element.

More in detail, it is possible to define a resisting force FI of the first element 10 which is generally higher than the resisting force F2 of the second element 11. In particular, the ratio between the resisting force FI of the first element 10 and the resisting force F2 of the second element Il and higher than 1, in particular higher than 1.2, even more particularly higher than 1.5.

The shape and size of the first and second elements 10, 11 make it possible to determine, during the damping condition, several different conditions.

Figures 1 and 12 show an initial condition, in which the first and second elements 10, 11 are close together and in which the second element 11 is in contact with the abutment portion 19 of the engagement element 16.

By stressing the piston 7 with the external force Fs having an inward direction with respect to the housing seat 6, the first and second elements 10, 11 are configured to define a damping condition in which said first and second element respectively generate a first force FI and a second force F2 which contribute to the generation of the resisting force Fr. In particular, the first and second elements are configured to move relatively to each other and relative to the stem 9.

More in detail, the first and second elements 10, 11 are configured to define a first condition in which they move relative to each other and with respect to the rod 9 and in which they generate a first overall resisting force Frj.

In this last condition described, the two elements are in the initial condition and after the stress imparted by the force Fs the two elements begin to move along the prevailing development direction approaching the first end 4 of the jacket 2. In the first condition, represented in figure 13 and in the detail of figure 13 A, the fluid initially passes from the seats 17, 18 respectively of the first and second element 10, 11 and then from the axial grooves of the engagement element 16. Once the seat 17 of the first element abuts to the first portion 16 and of the engagement element 16 the fluid is no longer able to pass easily from the seat 17 and therefore begins to leak through the leakage opening 13 of the first element.

As regards the second element 11, the latter easily allows the passage of fluid from the seat 18. In fact, in the first condition the first element 10 immediately generates a resistant force FI of leakage while the second generates a resistant force F2.

By adding the contribution of the two resisting forces of the first and second element 10, 11, in the first condition, an overall resisting force Frj is obtained which opposes the external force Fs generated on the piston 7.

By analyzing the movement of the mobile body 8, it is possible to say that the first element 10 moves towards the first end 4 of the jacket 2 with a speed relative to the piston 7 greater than the relative speed of the second element 11. This is because the resistance to motion developed by the first element 10 is such as to keep it substantially stationary with respect to the jacket 2, thus allowing it to move faster than the second element 11 with respect to the engagement element 16. The second element 11 develops a lower resistance and therefore is it moves with respect to the jacket 2 more easily than the first element 10, ie it moves with a speed lower than the speed of the first element relative to the engagement element 16.

Once the first element 10 comes into contact with the upper surface 16c of the engagement element 16, the first and second elements 10, 11 are arranged in a second condition in which the first element 10 moves integrally with the stem 9, while the second element 11 moves relative to the first element 10 (see figure 14 and detail of figure 14 A).

In this case the second element 11 continues to develop the resisting force F2 having the same (or substantially the same) intensity with respect to the same developed in the first condition. As regards the first element 10, on the other hand, the latter in the second condition develops a damping force FI greater than the force FI developed in the first condition. The resisting force FI is greater in the second condition because the first element 10 abuts against the base 16 and in cooperation the two bodies substantially occlude all the passage channels of the fluid (oil); in this situation the fluid to flow towards the second chamber B is forced to pass through the meatus 13 defined between the internal surface of the jacket 2 and the external circumferential surface of the first element 10, generating a corresponding greater resistance to motion which translates into a greater high dissipation and therefore in an increase of resistive force FI. In fact, the resting of the lower surface 10a of the first element 10 on the upper surface 16c of the engagement element 16 allows to generate a force FI greater than that generated in the first condition.

In other words, the seat 17 abutting to the first portion 16e of the engagement element 16 decreases the flow passing from the seat 17 inside the first element with a noticeable increase in the pressure in the chamber A and therefore with a consequent increase in the overall resisting force.

In this way the first and second elements 10, 11 develop an overall resisting force Fr2 greater than the resisting force Fri (Fr = Fl + F2).

By continuing to urge the piston 7 with an external force Fs having an inward direction with respect to the housing seat 6, the first and second elements 10, 11 are configured to arrange themselves in a third condition (see figure 15 and detail of figure 15 A) in which the first and second elements 10, 11 are close together and both move integrally with the stem 9.

In this condition the force FI developed by the first element is equal to the force FI developed by the first element itself during the second condition. As regards the second element 11, the latter, in the third condition, develops a damping force F2 greater than the force F2 developed by the second element 11 itself in the second condition.

In the third condition, the first and second elements 10, 11 are configured to develop an overall resisting force Fr3 greater than the overall resisting force Fr2 developed in the second condition.

Even more in detail, the lower surface 11a of the second element 11 meets the upper surface 10b of the first element 10. In this case, the second element can no longer slide relative to the piston 7 which allows to further increase the pressure in chamber A and therefore to increase the overall resisting force. The force F2 is substantially given by the leakage of the fluid from the lateral surface 14 of the second element 11.

In the third condition, the compacting of the first and second elements 10, 11 at the base 16a of the engagement element 16 generates a reduction in the flow of fluid passing through the entire mobile body 8: in this way we have a strong increase in the pressure in the chamber and consequently an increase in resistance to fluid leakage.

In other words, during the damping condition, the first and second elements allow to develop an ever greater resistant force Fr during the movement of the piston 7 towards the second end 5. Advantageously in the case of moving a leaf at high speed The shock absorber reacts by developing a first overall resistance to the movement of the Fri leaf in a first moment; after an instant the first element 10 abuts against the base 16 and the overall resisting force passes to a value Fr2; if the impact is of considerable intensity, after a short time the second element 11 hits the first element 10 and the overall resisting force passes to a value of Fr3.

Obviously the transition times between the reactions Fri, Fr2 and Fr3 will depend on the impact force and in fact the shock absorber reaction will adapt automatically, generating the necessary damping forces.

Then when the piston 7 reaches the discharge zone 43, the meatus defined between the external surface of the piston 7 and the internal surface of the jacket 2 increases, instantly reducing the resistance to motion.

In this way, in the last portion of the stroke of the shock absorber, the resistance to motion is reduced, thus guaranteeing optimal closing / opening of the sliding element.

Note that this last feature is extremely advantageous and important regardless of the specific configuration of the piston 7. As regards the reset condition, the piston 7 moves towards the first end 4 (see figure 7 and detail of figure 7B ). In this condition, the first and second elements 10, 11 are close together and the second element 11 is in contact with the stop portion 19. In this condition, visible in detail in figure 7B, the fluid passes freely from the through seats 17 and 18 of the first and second element 10, 11. In particular, in this condition the through seat 17 of the first element is spaced from the first portion 16e of the engagement element 16 and therefore does not limit in any way the passage of fluid inside the movable body 8.

In addition to this, the distance present between the mobile body 8 and the engagement element 16 allows the full passage of fluid from all the axial grooves 26 present on the engagement element 16.

The fluid pressure inside the two chambers is considerably lower in the reset condition than the pressure in the chambers in the damping condition.

The mobile body 8 generates a reset resistance Fa which is much lower than the damping force Fr which develops in the damping condition.

With the same force applied, therefore, the motion from the configuration of figure 13 to that of figure 15 is much slower than that of the condition of figure 8.

As can be seen from the accompanying figures 17 - 22, the “shock absorber 1 can be engaged with a support device 100 which can be interposed, in a non-limiting way, for example between a fixed structure of a piece of furniture and a mobile element. The support device 100 allows the engagement of the shock absorber 1 and therefore to support the latter during the damping and rearming phase described above.

As will become clearer in the following description, the support device 100 is configured to cooperate with the mobile element and facilitate the movement of the latter.

The support device 100 comprises a support frame 101 from which it is possible to distinguish a locking portion 102 adapted to engage the shock absorber 1 and a guide portion 103.

The locking portion 102, as visible from figure 18 comprises, in a non-limiting way, a cavity 104 extending along a direction of development 105 and defined between a first and a second end 105a, 105b. As can be seen from the accompanying figures, the development direction 105 of the cavity 104 is substantially coincident with the prevailing development direction 3 of the jacket 2.

The cavity 104 comprises at the first end 105a a first abutment portion 106 adapted to contact the first end 4 of the jacket 2 while at the second end 105b of the cavity 104, the latter has a second abutment portion 107 adapted to contact the second end 5 of the liner 2.

The first and second abutment portions 106, 107 substantially allow to lock said shock absorber 1 along the development direction 105 of the cavity 104 so that the latter can perform the damping and resetting step.

As can be seen, the first abutment portion 106 has an opening 108 which allows the stem 9 to come out at least partially from the cavity 104 and to contact a support element 109 which will be better described hereinafter.

The cavity 104 has, in a non-limiting way, a substantially cylindrical shape having a diameter greater than the diameter of the jacket 2 of the shock absorber 1. In this way the cavity 104 embraces the jacket 2 and prevents the latter from moving transversely to the direction of development 105 of cavity 104.

The guide portion 103 is integrally connected to the locking portion, in particular subsequently arranged to the first abutment portion 106. The guide portion 103 extends substantially parallel to the prevailing direction of development of the cavity 104.

The guide portion 103 comprises a through cut 110 which extends transversely, in particular orthogonally, to the direction of development 105 of the cavity 104. The through cut 110 accommodates the support element 109 inside it and allows this to be kept aligned. ™ last to the development direction 105 of the cavity 104.

The guide portion 103 further comprises a guide 111 configured to engage the support element 109 and allow the latter to move along a predetermined operating path.

More specifically, the guide 111 comprises a first substantially rectilinear section 112 which extends parallel to the development direction of the cavity 104 and therefore parallel to the prevailing development direction 3 of the jacket 2 of the shock absorber 1. The rectilinear section 112 extends substantially from the first stop portion 106 away from the latter.

The rectilinear section 112 ends with a second section or terminal section 113 extending transversely with respect to the first section 112, in particular in which said second section is, in a non-limiting way, an arched section.

As can be seen from the accompanying figures, the guide 111 is a groove that allows the engagement of relative projections of the support element 109. Alternatively, the guide 111 can be a projection which fits inside a respective seat of the support element 109.

As regards the support element 109, on the other hand, the latter has a substantially plate-like body 114 which is inserted inside the through cut 110.

The body 114 of the support element 109 comprises a thrust portion 115 arranged on one end of the same body facing the first abutment portion 106 of the support frame 101. The thrust portion 115 develops transversely, in particular orthogonally to the development direction of the cavity 104. The thrust portion 115 comprises a support portion 116 which is aligned with the rod of the shock absorber 1 along the prevailing direction of development of the jacket 2 and substantially arranged on one end of the body itself facing the first abutment portion 106 of the support frame 101.

The thrust portion 115 is configured to support the sliding door and therefore transmit the thrust of the latter to the shock absorber 1.

The thrust portion 115 also comprises a pulling portion 117 spaced from the support portion 116 of the body 114 itself and which is configured to receive in engagement an elastic element 118, for example a spring, connected integrally to the support frame and the which is configured to exert a force on the body having an inward direction with respect to the cavity 104 containing the shock absorber 1. In the accompanying figures, the elastic element 118 has been schematized with a line.

As can be seen, the firing portion 117 is, in a non-limiting way, a through hole which extends along the direction of development of the cavity 104.

The body 114 also comprises a support portion 119 which extends transversely to the thrust portion 115 of the body itself. The support portion 119 has, in a non-limiting way, a substantially arched shape. As can be seen from the accompanying figures, the support portion 119 comprises a coupling portion 120 opposite to the thrust portion 115.

The hooking portion 120 extends transversely with respect to the development direction 105 of the cavity 104 and directed towards the cavity 104 itself.

The body 114 comprises at least one guide element 121 adapted to engage with the guide 111 of the support frame 101. The accompanying figures show a preferential form of the object in which the guide elements 121 are protruding pins which engage with € ™ inside of a groove defined by the guide. In the preferential form, it is possible to note that the body 114 comprises two pins aligned along the prevailing direction of development of the liner 2. A first pin 122 is arranged on the thrust portion 115 of the body 114 and interposed between the support portion 116 and the pulling portion 117. A second pin 123 is instead arranged on the support portion 119, in particular substantially arranged in correspondence with the coupling portion 120. During the movement of the support element, the pins slide throughout the guide 111 During the engagement with the rectilinear section of the guide, the two pins keep the body aligned with the development direction of the cavity.

In this condition the thrust portion is configured to receive the sliding door in support while the hooking portion is configured to engage on the sliding door itself.

Once the second pin 123 has reached the arcuate portion, at the end of the predetermined operating path, it allows the hooking portion 120 to rotate slightly and arrange itself in a condition of stable charge. In this condition, the hooking portion 120 disengages from the sliding leaf and allows the latter to free itself from the support device 100. The operating path defined by the guide is sized so that only the second pin 123 engages the arched portion.

In this way it is possible to keep the support portion 116 of the thrust portion 115 aligned with the rod 9 of the shock absorber 1.

The accompanying figures show a preferred form of the support element, in which the latter comprises an auxiliary support element 125 interposed between the support element 109 and the rod 9 of the shock absorber 1. The element auxiliary support 125 comprises a first connection portion 125a adapted to engage with a respective connection portion 109a of the support element 109 arranged on the thrust portion 115. The first connection portion 125a, in the preferential form shown in the accompanying figures, It is a pin which extends transversely, in particular orthogonally, to the development direction of the cavity 104 and which engages inside the connection portion of the support element 109 which in the preferential form is represented by a seat . The two connection portions of the support element and the auxiliary support element define, in cooperation with each other, a hinge-type constraint.

The auxiliary support element 125 also comprises a second connection portion 125b adapted to engage with the rod 9 of the shock absorber 1. The auxiliary support element 125 comprises a guide element 126 able to engage with the guide of the support frame 101. The guide element 126 allows the auxiliary support element to remain constrained to the guide 111 of the guide portion 103 and to slide inside the latter for at least a portion of the predetermined path operating.

The guide element 126, as shown in the accompanying figures, is a protrusion having a parallelepiped shape which engages with the groove defined by the guide 111.

Figures 19 and 20 show the different working conditions of the shock absorber and of the various components of the support device 100. In particular, figure 20 shows a starting condition in which the second pin 123 is engaged inside the curved section 113 of the operational path. In this condition the rod 9 is in the condition of maximum excursion ready to receive the stress force exerted by the sliding door and the hooking portion 120 allows the latter to pass along the direction of development of the cavity.

The support device 100 is positioned in such a way that the sliding door contacts the support portion 116 of the thrust portion 115. In this way the door allows the second pin 123 to come out of the arched section and to engage the € ™ same door. The leaf pushes the support element 109 which in turn pushes the auxiliary support element 125 which stresses the rod 9 of the shock absorber 1.

Shock absorber 1, as previously described, allows you to manage the movement of the leaf. In particular, the shock absorber 1 exerts on the door a resistant force Fr which prevents the door from abruptly hitting the fixed structure of the cabinet.

Instead, by moving the leaf away from the shock absorber 1, it is possible to reset the latter. In particular, thanks to the engagement of the coupling portion 120, it is possible, by moving the leaf away from the shock absorber 1, to retrieve the latter.

Once the second pin 123 reaches the arched portion, the coupling portion 120 moves away from the leaf to allow the support element to be released from the leaf itself.

The components of the support device are, in a non-limiting way, made of plastic material in order to reduce the production costs of the various components and consequently the overall cost of the device. Alternatively, part or all of the components of the support device can be made of metallic material.

The invention achieves important advantages.

First of all, the particular configuration in two elements of the piston 7 allows to have an extremely simple geometry and reduced production costs.

The movement of the first and second elements 10, 11 guarantees a modulation of the resisting force during the motion of the piston. Therefore, the described configuration allows to increase (automatically as a function of the stress) the resisting force so as to considerably reduce the impacts to the associated sliding components.

The coupling between the engagement element and the first and second element prevents misalignments or vibrations of the rod 9 guaranteeing improved handling compared to that of the state of the art.

Furthermore, the presence of an end portion with an increased section of the housing seat guarantees the achievement of the desired closing / opening conditions of the movable element with respect to the fixed frame substantially in any operating condition and avoids the annoying behavior of shock absorbers in accordance with the state of the art that do not allow the complete closing / opening of the mobile structure requiring a second intervention by the operator.

LEGEND

1 Shock absorber

2 Shirt

2nd Main opening

2b Auxiliary opening

2c Rebate portion of the jacket 2 2d Engagement portion of the jacket 2 3 Prevailing development direction 4 First end

5 Second end

6 Housing seat

7 Piston

8 Mobile body

A First room

B Second bedroom

C Piston stroke 7

CI Operating stroke of the mobile body 8 9 Stem

9a First end of the stem

9b Second end of the stem

9c Connecting portion of the stem 9d Thrust portion

Fs Thrust force

Fr Resistant strength

Fri First force resist overall Fr2 Second force resist overall

Fr3 Third force, resist overall

10 First element

10a Lower surface of the first element

1 Ob Upper surface of the first element

1 Oc Closing body

1 Od First passing light

11 Second element

IIa Lower surface of the second element

I lb Upper surface of the second element

I I c Second passageway

FI Resistant force of the first element

F2 Resistant force of the second element

12 Lateral surface of the first element

13 Lateral leakage opening of the first element 14 Lateral surface of the second element

15 Lateral leakage port of the second element 16 Engagement element

16th Base

16b Lower surface

16c Upper surface

16d Body

16e First portion

16f Burglary

16g Perimeter pass-through openings

16h Through internal openings

16i Second portion

161 Side shoulders

16m Connection portion of the engagement element 16 17 Pass-through seat of the first element

18 Pass-through seat of the second element

19 Portion of stop

20 Projection

21 Reliefs first elements

22 Second element findings

23 Projection of the first element 10

24 Guide to the commitment element

25 Compensation element

26 Axial grooves

27 Sealing device

28 Closing element

28a Portion of connection

28b Seal seat

29 Side flange

29a Threaded portion

29b Portion of the stop

30 Headquarters

31 Gasket

31 a Support base

3 lb Wall mating

3 1 c Sealing wall

32 Passage opening

33 Portion of scraping

34 Restraint element

35 Headquarters

35a Base of the retaining element 36 Shoulder

37 Thrust portion

39 Sealing element

40 Alletta

41 Free end

42 First end

43 Unloading area

44 Cavity

47 Sealing area

48 Portion of connection

49 Compensation area

50 Portion of retainer

5 1 Operational area

52 Top cap

53 Base

54 Side support walls

55 Cavity

56 Retaining element

57 Rebate portion of the top cap 52 58 Fixing portion of the top cap 52

59 Maneuvering portion of the top cap 52

100 Support device

101 Support frame

102 Locking portion

103 Portion of guide

104 Cavity

105 Direction of development of the cavity 104

105a First end

105b Second end

106 First portion of measure

107 Second portion of measure

108 Opening of the first stop portion

109 Support element

109a Connection portion of the support element 110 Through cut

111 Guide portion guide

112 First section

113 Second section

114 Support element body 109

115 Thrust portion

116 Supporting portion

117 portion of shot

118 Elastic element

119 Support portion

120 Portion of coupling

121 Portion of guide

122 First pin

123 Second pin

125 Auxiliary support element

125a First connection portion of the auxiliary support element 125b Second connection portion of the auxiliary support element

126 Guide element of the auxiliary support element

Claims (11)

CLAIMS 1. Shock absorber (1) for articles of furniture, comprising: > a jacket (2) having a substantially elongated shape extending along a prevalent development direction (3) and having a first and a second end (4, 5), said jacket (2) defining inside it a housing seat (6 ); > at least one fluid disposed inside the housing seat (6); > at least one piston (7) comprising a movable body (8) engaged inside the housing seat (6) and which defines a first and a second chamber (A, B) within the latter fluid between them, said piston (7) further comprising a rod (9) integrally connected with said movable body (8) and at least partially protruding from said jacket (2), said piston (7) being movable by relative sliding with respect to the jacket (2) along the prevailing development direction (3) of the same, said piston (7) being configured to define a damping condition in which, following the stress of the rod (9) by means of an external thrust force (Fs), in with a particular direction entering said housing seat (6), the mobile body (8) moves in a first direction of travel and, interacting with the fluid, allows the passage of the latter, from the first to the second chamber, generating a resistent force and (Fr) opposing the external thrust force (Fs), characterized in that said movable body (8) comprises a first and a second element (10, 11) movable relatively to each other which, during the damping condition, are both configured to move, at least for a distance, relative to the stem ( 9) along the prevailing development direction (3) and generate respectively a first and a second resisting force (FI, F2) which contribute to the formation of the resisting force (Fr) of the mobile body (8). 2. Shock absorber according to claim 1, wherein said first and second elements (10, 11), during the damping condition, are configured to move relative to each other and with respect to the stem (9) between at least a first condition in which they generate a first overall resisting force (Fri), a second condition in which they generate a second overall resisting force (Fr2), said second overall resisting force (Fr2) being greater than the first overall resisting force (Frj), and a third condition in which they generate a third overall resisting force (Fr3), said third overall resisting force (Fr3) being greater than the second overall resisting force (Fr2). 3. Shock absorber according to claim 2, wherein said piston (7) comprises an engagement element (16) connected and carried integrally by the piston rod (9), said first and second element (10, 11), in the first condition , being spaced with respect to said engagement element (16) while in the second condition the first element (10) is substantially in contact with the engagement element (16) and the second element (11) is spaced from the first element (10), said first element (10), in the third condition, being substantially in contact with the engagement element (16) and the second element (11) being substantially in contact with the first element (10). 4. Shock absorber according to claim 2 or 3, wherein said first element (10) has a first passage opening (10d), optionally internal, to allow a passage of fluid coming from the first chamber (A) and directed towards the second chamber (B), said second element (11) presenting a respective second passage opening (He), optionally internal, to allow a passage of fluid coming from the first chamber (A) and directed towards the second chamber (B), in the first condition the first passage opening (10d) of the first element (10) and the second passage opening (Ile) of the second element (11) allow the passage of fluid, in the second condition and in the third condition the first passage opening (10d) of the first element (10) is substantially occluded, increasing the resistance to the passage of fluid. 5. Shock absorber according to claim 2 or 3 or 4, wherein said housing seat (6) has a prismatic shape, in particular substantially cylindrical, said first and second element (10, 11) being at least partially counter-shaped to the housing seat ( 6) of the jacket (2), said first element (10) having an external lateral surface (12) which in cooperation with the housing seat (6) defines a lateral leakage port (13) which allows the fluid to leak, in particular an incompressible fluid such as oil, from the first to the second chamber (A; B), and in which said second element (11) has an external lateral surface (14) which in cooperation with the housing seat ( 6) defines a lateral leakage port (15) which allows the fluid to leak from the first to the second chamber (A, B), in the first condition the first port of the first element (10) and the second port of the second element ( 11) allow the passage of fluid, in the second condition the first passage port (10d) of the first element (10) is substantially occluded and the fluid leaking through said lateral leakage port (13), in the third condition the first passage (10d) of the first element (10) is substantially occluded, the second element (11) being substantially in contact with the first element (10) and the fluid leaking through said lateral leakage port (13) of the first element (10 ) and through said lateral leakage opening (15) of the second element (11), in particular said lateral leakage opening (13) of the first element (10) presenting an area, according to a cross section to the prevailing development direction ( 3), equal to or less than the area of the lateral leakage opening (15) of the second element (11) and characterized by the fact that said first and second element (10, 11), during the passage from the first to the second condition , are configured to slide, relative to the stem (9) and along the prevailing development direction (3), respectively with a first and a second sliding speed. 6. Shock absorber according to any one of the preceding claims, in which said housing seat (6) has a substantially cylindrical shape, the external lateral surface of the first and second element (10, 11) presenting respectively, according to a cross section to the direction of development prevalent (3), a substantially circular shape, the shape of the first element (10) having a diameter greater than or equal to the diameter of the shape of the second element (11) and in which an external lateral surface (12) of the first element (10) it has an extension, along the prevailing development direction (3), equal to or greater than the extension of an external lateral surface (14) of the second element (11). 7. Shock absorber according to any one of the preceding claims, in which said piston (7) is configured to define a reset condition in which the piston (7) itself, in motion in a second direction of travel opposite to the first direction of travel and in interaction with the fluid, it allows the latter to pass from the second to the first chamber (B; A) with consequent displacement of the stem (9) in the direction outgoing from said housing seat (6) and in which said first and second element (10, 11), in the reset condition, generate a resetting force (Fa) which opposes the sliding of the piston (7), said resetting resisting force (Fa) being lower than the resisting force (Fr) generated from the first and second element (10, 11) in the damping condition, said first and second element (10, 11), in the reset condition, allowing a passage of fluid from the second to the first chamber (B; A) greater than the passage of fluid d to the first to the second chamber (A; B), during the damping condition. 8. Shock absorber according to any one of claims 3 to 7, wherein said engagement element (16) comprises a base (16a) which extends along the prevailing development direction (3) between a lower surface (16b), facing towards the first end (4) of the liner (2), and an upper surface (16c), facing the second end (5) of the liner (2), said engagement element (16) further comprising a connected body (16d) with said base (16a) and emerging transversely, in particular orthogonally, from the upper surface (16c) of the latter, said first and second element (10, 11) presenting respective through seats (17, 18) suitable for allowing the Engagement of said first and second element (10, 11) to the body (16d) of the engagement element (16), said first and second element (10, 11) being able to slide along said body (16d) for the predetermined stroke , said engagement element (16) comprising an abutment portion (19) arranged on a € ™ end of said body (16d) facing the second end (5), said upper surface (16c) and said abutment portion (19) of the engagement element (16) defining the predetermined stroke of the first and second element (10, 11), in particular, during the passage from the first to the second condition, said first element (10) is configured to move between the base (16a) of the engagement element (16) and said second element (11 ) while said second element is configured to move between the stop portion (19) and the second element (11), and in which, during the passage between the second and third condition, said first element (10) moves integrally to the stem (9) while said second element (11) moves between said first element (10) and said abutment portion (19). 9. Shock absorber according to any one of the preceding claims 3 to 8, wherein said engagement element (16) comprises a predetermined number of axial grooves (26), said movable body (8), in particular said first element (10), comprising at least one closing body (10c) capable of abutting, during the damping condition, to at least one of the axial grooves (26) of the engagement element (16), the abutting of the closing body (10c) with at least one of the axial grooves (26) of the engagement body (16) limiting the passage of fluid inside the mobile body (8) with respect to the passage of fluid in the reset condition, seats (17, 18) of the first and second element (10, 11) defining in cooperation with the engagement element (16) a passage opening which is configured to allow the passage of fluid between the two chambers during the damping and / or rearming condition , said first and second elements (10, 11) being configur to allow the dimensional variation of said passage opening during the relative movement of said first and / or second element (10, 11) with respect to the engagement element (16), the dimensional variation of the passage opening causes a variation of the resisting force of passage of the fluid between the two chambers, in which during the damping condition the passage opening is at least partially occluded while during the reset condition the passage opening is totally free, in particular said engagement element (16) comprising a first portion (16e) connected to the base (16a) of the engagement element itself, said first portion (16e) having a substantially cylindrical shape extending parallel to the prevailing development direction (3) of the jacket (2) and having a diameter (DI) smaller than the diameter of the base (16a), said engagement element (16) further comprising a second portion (16i) connected to the first portion (16e) of the engagement element (16) itself, said second portion (16i) having a substantially cylindrical shape and extending parallel to the prevailing development direction (3) of the jacket (2) and having a diameter ( D2) smaller than the diameter of the base (16a), in particular smaller than the diameter (DI) of the first portion (16e), said first and / or second portion (16e, 16i) being configured to abut the through seat of the first and / or second element (10, 11) during the damping condition to allow a variation of the fluid passage inside the mobile body (8) and consequently allow a variation of the damping force of the piston (7). Shock absorber according to any one of claims 3 to 9, wherein said engagement element (16), in particular the body (16d) of the engagement element, comprises at least one guide (24), for example a groove, in particular a through groove passing through the body (16d) of the engagement element (16), extending along the prevailing development direction (3) of the jacket (2), said guide (24) being configured to receive said first and second element (10, 11) and being configured to guide the latter in sliding along the predetermined stroke, in which said first element (10) comprises at least one projection (23) adapted to engage with said guide (24) which guides in the motion said first element (10) and said second element comprises at least one protrusion (20) adapted to engage with said guide (24) which guides said second element (11) in motion, optionally said first element (10) comprising two protrusions ( 23) arranged in c correspondence of the through seat (17) and having an incoming direction with respect to the latter, said protrusions (23) being substantially facing each other and defining, in correspondence with the protrusions themselves, an opening having a substantially â € œHâ € shape , optionally also said second element (11) comprising two protrusions (20) arranged in correspondence with the through seat (18) and having an inward direction with respect to the latter, said protrusions (20) being substantially facing each other which define, in correspondence of the protrusions themselves, an opening having a substantially â € œHâ € shape 11. Shock absorber according to any one of claims 3 to 10, wherein said first element (10) comprises a predetermined number of projections (21) emerging from a lower surface (10a) of the latter, said projections (21), during the damping condition, in particular during the second and third condition, by contacting an upper portion (16c) of the engagement element (16) and allowing the lower surface (10a) of the first element (10) to be spaced from the upper surface (16c) of the engagement element (16) and / or in which said second element (11) includes a predetermined number of ridges (22) emerging from a lower surface (11a) of the latter, said projections (22), during the damping and / or rearming condition, contacting an upper surface (10b) of the first element (10) and allowing the upper surface (10b) of the first element (10) to be spaced from the lower surface (11a ) of the second element (11).