IT202100011666A1 - HINGE FOR THE REVOLVING MOVEMENT OF A DOOR, SASH OR SIMILAR - Google Patents

Description

HINGE FOR THE REVOLVING MOVEMENT OF A DOOR, ANTA OR SIMILAR

DESCRIPTION

Field of application

The present invention ? generally applicable to the technical sector of hinges, and has particularly for object a hinge for the rotational movement of a closure element, such as a door, a leaf or the like, with respect to a support structure.

State of the art

Hinges are known for the rotational movement of a closing element, such as a door or leaf, in particular made of glass, with respect to a support structure.

These hinges typically comprise a fixed element anchored to the support structure and a movable element pivoted to the leaf, capable of reciprocally rotating with respect to each other.

? note the need to dampen the opening and/or closing of these glass doors, in order to avoid breakage of the same caused by knocks or forcing by an incautious user.

In this regard, hinges are known which allow for the simultaneous unwinding of a plurality of of functions including damping, brake, sprint or other functions as needed.

Such a need? generally satisfied using adjustment systems that are difficult to produce, typically acting on the internal mechanical part of the hinge. These hinges are particularly complex and difficult to assemble. Furthermore, these hinges allow the door to be moved only in certain predetermined ways, i.e. according to a so-called unique ?law of motion? predetermined.

? otherwise? notes the need to avoid unhinging or damaging the hinge in the event of instantaneous closure of the door, for example due to a gust of wind.

Further known need? to allow the so-called final shot, the cio? facilitate the rotation of the door in the last closing degrees in order to facilitate its closing.

For this purpose, known hinges comprise a plurality of of hydraulic circuits made in the hinge body with one or more? valves for controlling the flow of the working liquid and special ducts with pressure relief valves. In general, known hinges are particularly complex and can be improved according to different aspects.

Presentation of the invention

Purpose of the present invention? that of at least partially overcoming the drawbacks noted above, by making available a hinge for the rotational movement of a closure element having highly functional characteristics? and low cost.

Another object of the invention ? provide a hinge that allows damping of the opening and/or closing of the closure element.

Another purpose of the invention? make available a hydraulic hinged device with a pressure relief valve that is particularly simple to make and has reduced overall dimensions.

Another purpose of the invention? provide a hydraulic hinge device which allows the final release to be particularly simple to implement and of reduced dimensions.

Another purpose of the present invention ? that of making available an assembly for the revolving movement of a closing element having characteristics of high functionality? and low cost.

Other purpose? that of making available an assembly which allows the distance between the closing element and the stationary support structure to be varied.

Another purpose of the present invention ? that of making available a system for the revolving movement of a closing element having characteristics of high functionality? and low cost.

Another purpose of the present invention? that of providing a system which allows the closure element to be controlled in a particularly effective way.

Another object of the invention ? provide an easy-to-assemble hinge.

These purposes, as well as others that will appear more? clearly hereinafter, they are achieved by a hinge, by an assembly and by a system in accordance with what is described and/or claimed and/or illustrated herein.

Advantageous embodiments of the invention are defined in accordance with the dependent claims.

Brief description of the drawings

Further characteristics and advantages of the invention will become more evident in the light of the detailed description of some preferred but not exclusive embodiments of the invention, illustrated by way of non-limiting example with the aid of the attached drawings where:

FIG.1 ? a schematic front view of a system 1 comprising an assembly 10 with a hinge 100 and a lower assembly 9 with a hinge 200;

FIGS.2 and 3 are an exploded view of an assembly 10 and 9 respectively;

FIGS. 4, 5, 6 and 7 are schematic sectional views of the assemblies 9 and 10 in which the hinges 100 and 200 and the respective attachment elements 190 290 are in different operating phases, respectively with a mutual rotation angle of 0?, 30 ?, 60? and 90?;

FIGS. 8 and 9 are a sectional view of a different form of the system 1 in which the hinges 100, 200 respectively have an angle of 0? what about 90? with the respective attachment elements 190290;

FIGS. 10, 12 and 14 are a sectional view of the hinge 100 with a different embodiment of the valve means 181 in different operating positions, with in FIGS. 11, 13 and 15 an enlargement of some details of FIGS. 10, 12 and 14 respectively;

FIG.16 ? an exploded view of some details of the valve means 181 of the hinge 100 of FIG. 12;

FIGS. 17 and 19 are a sectional view of a different embodiment of the valve means 181, with in FIGS. 18 and 20 an enlargement of some details of FIGS. 17 and 19 respectively;

FIG.21 ? an exploded view of some details of the valve means 181 of the hinge 100 of FIG.17;

FIGS.22 and 23 are a sectional view of some enlarged details of the hinge 100 of FIG.4 with a different embodiment of the valve means 181;

FIGS. 24, 26 and 28 are a sectional view of a hinge 100 with a different embodiment of the valve means 181 in different operating positions, with in FIGS. 25, 27 and 29 an enlargement of some details of FIGS. 24, 26 and 28 respectively;

FIGS.30 and 32 are a sectional view of some details of the assembly 10 in which the hinge 100 and the attachment 190 are respectively in proximal and distal position, with in FIGS.31 and 33 an enlarged view respectively of FIG.30 and FIG.32.

Detailed description of some preferred embodiments With reference to the cited figures, a system 1 is described for the rotational movement of a closure element A, such as a wing, a door, or the like, with respect to a stationary support structure S, such as a wall, floor, frame or the like.

The present invention could include various similar or equal parts and/or elements. Where not otherwise specified, similar or equal parts and/or elements will be indicated with a single reference number, it being understood that the technical characteristics described are common to all similar or equal parts and/or elements.

Given that the stationary support structure ? in itself note, right? was illustrated in the accompanying figures. This element, in fact, does not form part of the invention claimed in the attached claims.

For simplicity?, in the continuation we will? reference to a frame S and to a?door To which potr? rotate between at least one closed position and at least one open position.

Essentially, system 1 will be able to understand a plurality of hinges 100 and 200 which will be able to cooperate to move the door A around a rotation axis X.

In particular, system 1 will be able understand a plurality of handling assemblies 9 and 10. Each of these last ones can? comprise an attachment element 190 and 290 and a hinge 100 and 200. In particular, the latter can be rotationally coupled to each other to rotate reciprocally about a respective axis X1 X2. Once installed, the axes X1 and X2 can coincide to define the axis of rotation X so that the attachment elements 190 and 290 and the hinges 100 and 200 rotate between at least the open position of the closing element and at least one position closed by the closing element.

In FIG. 1 ? shown is a pair of assemblies 9 and 10 in which the attachment elements 190, 290 are coupled with the frame S and the hinges 100 and 200 with the door A. It is understood that this embodiment is not? exclusive, in fact one or both of the hinges 100, 200 can be coupled with the frame S while one or both of the attachment elements 190, 290 can be coupled with the door A.

It is understood that door A will be able to also be handled by a single assembly, for example by assembly 10. For example, will it be possible? a movement system should be provided comprising the assembly 10 mounted at the bottom and an idle hinge mounted at the top.

Eventually, each of the hinges 100, 200 could? be an automatic and/or control hinge.

According to a particular aspect of the invention, the system 1 will be able therefore include a pair of hinges 100. For simplicity? in the figures from FIG. 4 to FIG. 7 and from FIG. 8 to FIG. 9 ? 100 indicates the hinge positioned above and 200 indicates the hinge positioned below.

Advantageously, the hinges 100 and 200 can be synchronized. In particular, both hinges 100 and 200 will be able to cooperate to control the movement of door A for one or more? sections of the movement of the latter between the open and closed position. Preferably, the hinges 100 and 200 will be able to cooperate to control the movement of the door A along the entire movement from the open to the closed position and/or vice versa.

Each of the hinges 100, 200 potr? then dampen or promote the rotation of leaf A between the open and closed position. Preferably, as better explained below, each of the hinges 100 200 can exert a different action along different sections of the rotation of leaf A.

Can the control of the movement of door A be able to? therefore be the result of the action of both hinges 100 and 200.

In other words, the so-called ?law of motion? of? door A can? be the combination of the ?motion law? of the individual hinges 100, 200.

It is therefore understood that the hinges 100, 200 may be of any type, without thereby departing from the scope of protection of the present invention.

Preferably, the hinges 100, 200 could comprise a pin 120, 220, which could be fixed to one of the door A and the frame S, and a hinge body 130, 230 which can be fixed to the other between door A and frame S.

The hinge body 130, 230 and the pin 120 200 can therefore be rotationally coupled to each other to rotate respectively around the axes X1 X2 between a respective operating position corresponding to the open or closed position of the closure element A and an operating position corresponding to the closed or open position of the closing element A.

In other words, system 1 will be able to include a pair of assemblies 9 and 10, each of which potr? allow the respective rotation of the respective hinge body 130, 230 and of the respective pin 120, 220 with respect to the respective axis of rotation X1 and X2. Once assemblies 9 and 10 have been installed, the X1 and X2 axes will substantially coincide to define the X rotation axis of leaf A.

In particular, in the non-limiting examples of the system 1 illustrated in the figures from FIG.4 to FIG. 9, both hinges 100, 200 have the pin 120, 220 fixed and the hinge body 130, 2330 rotating between the closed leaf position (FIG. 4 and FIG. 8) and the open leaf position (FIG.7 and FIG .9).

Preferably, the pin 120, 220 could? be anchored to the frame S by means of the coupling elements 190, 290 while the hinge body 130, 230 could be anchored to? Leaf A to rotate integrally with it in the same way? known.

Each of the hinges 100, 200 potr? comprising means 150, 250 for controlling the reciprocal rotation of the pin 120, 220 and of the hinge body 130, 230.

In general, the means 150, 250, which may be of the mechanical and/or hydraulic type, may be configured so as to dampen or promote the rotation of the hinge body 130, 230 with respect to the pin 120, 220 for at least a portion of the rotation of the ?leaf A between the open and closed position.

Preferably, the means 150, 250 will be able to act at least for the same rotation section of the wing A. For example, the attached figures show systems 1 in which the means 150, 250 act simultaneously during the closure of the wing A.

Even if not represented, it is understood however that the system 1 will be able? have different configurations. For example, the means 150, 250 could act along different sections of the closure, for example the means 150 at the beginning and the means 250 at the end. Possibly one of the means 150 and 250 will be able to act during the opening while the other means 150 and 250 will be able to act during the closing of the wing A.

On the other hand, the hinge 100 and the hinge 200 can be configured in such a way that the means 150 and/or 250 only act when the door A is rotated for a distance from one between the open position and the closed position at the ?other between the open position and the closed position and do not act when leaf A is rotated for the same distance from the other between the open position and the closed position to one of the open position and the closed position only act the means 250.

According to a preferred embodiment of the invention, the means 250 of the hinge 200 can be configured to promote the closure of the door A while the means 150 of the hinge 100 can be configured to dampen the closure of the door A.

In other words, when the door A closes, the hinge 100 opposes the action of the hinge 200.

It is understood that this configuration may be made using different types of hinges 100, 200 which may include different types of means 150, 250.

Preferably, the hinge 100 and the hinge 200 could comprise the hinge body 130, 230 which internally comprises a working chamber 135 defining a respective axis Y, Y? substantially perpendicular to the respective axis X1 and X2.

Furthermore, the hinge 100 and the hinge 200 could comprise a cursor element 140, 240 which can slide in the respective working chamber 135. In particular, the chamber 135 could include a pair of back walls 138, 138? opposite. The cursor 140, 240 will be able to then scroll along the respective Y axis, Y? between a position proximal to the bottom wall 138 and a position distal therefrom.

Conveniently, the pin 120, 220 could? be operatively connected with or include respective cam means 125, 225, while the cursor element 140, 240 could? be operatively connected with or include cam follower means 145, 245.

The cam means 125, 225 and cam follower 145, 245 can be operatively connected to each other so that the rotation of the hinge body 130, 230 corresponds to the sliding of the respective cursor 140, 240 between the distal and proximal positions.

Advantageously, the means 150 and 250 will be able to control the sliding of the cursor 140 and 240 and therefore control the rotation of the wing A.

Preferably, the control means 150 can be hydraulic and can be configured to dampen the sliding of the slider 140 at least when moving the door from the open position to the closed position. On the other hand, the control means 250 can be of the mechanical type and can be configured to promote sliding of the slider 140 at least when moving the door from the open position to the closed position.

For example, the means 250 could comprise a spring 251 interposed between the cursor element 240 and the back wall 138 so as to promote sliding of the cursor 240 from the proximal position to the distal position.

It will be understood that according to the configuration of the cam means 125 and cam follower 145 and of the control means 150 of the sliding of the cursor 140, so? as depending on the configuration of the cam means 225 and cam follower 245 and of the means 250 for controlling the sliding of the slider 240, the respective hinge 100, 200 will be able to control the rotation of leaf A in a different way.

Advantageously, as better explained below, the hinge 200 can promote the closure of door A, while the hinge 100 can? counteract the action of the hinge 200 so that the speed? closure of the leaf A along a predetermined stretch is substantially constant.

This trait can vary according to the configurations of the hinges 100, 200 as better explained below. For example, this angular section could be the trait between 0? and 90?, or between 10? and 90? (for example in case of final shot), or between 0? and 80? (in case of open leaf stop position), or between 10? and 80? (in case of stop and click).

In other words, as described above, the motion laws of the hinge 100 and of the hinge 200 can be combined to define the motion law of the leaf A. vary according to the configuration of the hinges 100, 200, preferably popr? allow the closure of? door A with a speed? constant.

Will we proceed? now to describe some preferred but not exclusive examples of the hinges 100 and 200 of the system 1 having the advantages described above.

The cam means 125 and the cam means 225 can be shaped differently from each other. In this way, the rotation of leaf A for at least one section during closure can correspond to a different sliding of the respective cursor 140 and 240.

Conveniently, the cam means 125, 245 can be configured to promote sliding of the cursor element 140, 240 in an opposite way. For example, when the door A is closed, the cursor 140 can scroll in one direction while the cursor 240 popr? swipe in the opposite direction.

In FIG.4 and in FIG.8 the slider 140 ? in a position proximal to the wall 138 and the cursor 240 ? distal to wall 138, while in FIG. 7 and in FIG. 9 the cursor 140 ? distal to wall 138 and cursor 240 ? proximal to the wall 138.

Preferably, the pin 120, 220 could? include an operating surface 126, 226 defining the cam means 125, 225, while the cursor element 140, 240 could? include respective surfaces 141, 241 able to interact with the surfaces 126, 226 thus defining the half cam follower 145245.

Preferably, the cursor 140, 240 will be able comprise a cylinder 142 having an axis substantially perpendicular to the axis Y, Y? which includes the respective surface 141, 241.

In this way, the action of the spring 251 will promote? the sliding of the slider 240 towards the distal position, the corresponding rotation of the pin 220, the corresponding rotation of the pin 120 and the corresponding sliding of the slider 140 towards the proximal position. The hydraulic means 150 will be able to dampen the sliding of the piston 140 from the distal position to the proximal position.

In case of closure of? Leaf A, the spring 251 will be able? not be constant, that is? can I be maximum with leaf A open and minimum with leaf A closed, while the hydraulic means 150, depending on the configuration, can dampen the closure of leaf A in a substantially constant manner.

Therefore, the surfaces 126 and 226 of the respective pins 120 and 220 can be shaped so as to compensate for these imbalances so that the leaf A has a speed? of substantially constant rotation.

Pi? in detail, the surface 126 of the pin 120 of the hinge 100 and the surface 226 of the pin 220 of the hinge 200 can therefore be shaped so as to present a non-constant shape.

In particular, the surface 126 of the pin 120 of the hinge 100 and the surface 226 of the pin 220 of the hinge 200 may comprise with an initial section 127, 227 a final section 129, 229 and a substantially convex intermediate operating section 128, 228.

The profile of the convex surfaces 128 and 228 could be mutually configured so that the non-constant action of the spring 251 upon rotation of the leaf A is compensated for by the action of the hydraulic means 150.

In particular, the surface 228 potr? be configured in such a way that as the door closes, a rotation angle of the pin 220 corresponds to a significantly greater sliding of the cursor 240. While the surface 128 can? be configured in such a way that during closing of the door the sliding of the cursor 140 remains substantially constant or varies slightly.

Will you describe? now the system 1 with particular reference to the figures from FIG.4 to FIG.7. In particular, the pin 120 potr? comprise the external surface 126 with the initial angular section 127, the convex operating section 128 and the final concave section 129, while the pin 220 could? comprising the external surface 226 with the initial concave section 227, the convex operating section 228 and the final concave section 229.

In FIG.7 the leaf A? in the open position and the cam 125 will be able to? be in correspondence with the concave section 129 while the cam 225 could? correspond to the concave section 229. In this case, door A? therefore stable in a stationary position. This position can correspond to the door open position at 90?.

When closing leaf A, FIG. 6 and FIG. 5, you can move the hinge body 130, 230 of both hinges 100, 200 so that the surface 141 is in correspondence with the convex section 128, while the surface 241 is in correspondence with the convex section 228.

Conveniently, sections 128 and 228 may have concavity? different so that the decreasing action of spring 251 is compensated and leaf A rotates with speed? constant or predetermined, as described above.

In FIG.4 the wing A can? be in the closed position. The hinge 100 can present the surface 141 in contact with the angular section 127, while the hinge 200 could have the surface 241 in contact with the concave portion 227. Door A can? therefore be in a stop position corresponding to the closed leaf position.

To overcome the open leaf stop position, you can rotate the door for about 10?. In this case, the rotation of leaf A can be controlled starting from 80?.

Similarly, with particular reference to FIG.8 (door closed) and FIG.9 door open, the surface 126 can comprise a convex section 127, a second convex section 128 and a substantially flat section 129, while the surface 226 could comprise a substantially flat section 227, a second convex section 228 and a slightly convex section 229.

When does leaf A ? in the closed position, the surface 241 ? in abutment with the flat surface 227 so that the hinge 200 is stable and therefore the door A remains in the closed position. On the other hand, when door A ? in the open position, the surface 241 will be able to be in abutment with the substantially convex portion 229 so that the hinge 100 returns to the closed position.

It is understood that what is described above for closing door A could be made similarly for the opening of door A.

Preferably, the pin 120 and/or 220 could be substantially symmetrical so that the hinges 100 and/or 200 are ambidextrous.

In general, it is understood that depending on the shape of the cam means 125 225, and of the control means 150, 250, the hinge 100 or 200 will be able to have a different behaviour, therefore a different law of motion and consequently the movement of leaf A can? be different.

Advantageously, you can modify the behavior of the hinge 100 or 200 simply by replacing the cam means 125225, for example by replacing the pin 120 or 220.

Also, similarly, you can create a system 1 for moving door A having different configurations according to preferences by arranging different pins 120, 220.

Thanks to these characteristics, system 1 will be able to be particularly versatile and at the same time simple, fast and cheap to make.

According to a particular embodiment of the invention, the assembly 10 will be able to be configured in such a way that the distance d between the hinge 100 and the attachment element 190 can? be variable. In other words, the assembly 10 will be able to? be mobile between a configuration in which the distance d ? minimum (FIG.30) and a configuration in which the distance d ? maximum (FIG.32).

The maximum distance d can? be greater than 5 mm, preferably about 8 mm, while the minimum d distance could? be less than 5 mm, preferably less than 1 mm.

In any case, the maximum variation of the operating distance will be able to be between 1 mm and 10mm, preferably potr? be about 7mm.

In particular, the hinge 100 and the attachment element 190 will be able to slide reciprocally along the X axis.

In this way, advantageously, you can install assembly 10 in case of small variations of the frame or the door. For example, if system 1 is set up, the assembly placed above will be able to be the assembly 10 so that the sliding of the hinge 100 and of the attachment 190 makes it possible to compensate for any play of the door A with respect to the frame S.

Pi? in detail, the hinge body 130 can comprise an upper wall 131 facing the attachment element 190. The latter can? include a plate 191. The maximum variation of the operating distance d potr? then be the distance between the upper wall 131 and the plate 191.

The set 10 could? comprise a pin 120 and a hinge body 130. The pin 120 could? be engaged with the hinge body 130 and can it? be fixed with the attachment element 190. On the other hand, the hinge body 130 could include a seat 110 for the pin 120.

The pin 120 and the hinge body 130 can be rotationally coupled to each other to rotate reciprocally around the axis X1 between at least one operating position corresponding to the open position of the closing element and one operating position corresponding to the closed position of the closing element .

Preferably the pin 120 potr? be integrally coupled with the attachment element 190. For example, the pin 120 could? include a portion d? extremity? 121? what can I be integrally coupled with the plate 191, for example by one or more? screws 192, while the hinge body 130 can be coupled with the closing element A.

Conveniently, the pin 120 and the seat 110 can be reciprocally configured in such a way as to slide reciprocally along the axis X. Preferably, the pin 120 and the hinge body 130 can slide for a distance substantially equal to the distance d.

For example, the? extremity? 121? of the pin 120 potr? protrude from the wall 131 of the hinge body 130 for a length equal to or greater than the maximum variation of the distance d. The pin 120 could? then be mobile between an extended configuration (FIG. 32) in which the distance d ? maximum and a retracted position (FIG.30) in which the distance d ? minimal.

Conveniently, the hinge body 130 can comprise a through opening 132 to allow the pin 120 to slide. in detail, wall 131 could include this through opening 132.

The pin 120 could? therefore comprising at least one portion 121 passing through the opening 132 and sliding therein between the retracted configuration and the extended configuration. Portion 121 can include the? extremity? 121?.

Preferably, when the 120 pin ? in the retracted configuration, the portion 121 and the part 131 may be substantially flush, and the minimum distance d may be be particularly small. For example, can be less than 1 mm. Possibly, when the pin 120 ? in the retracted configuration, the wall 131 and the plate 191 could be in contact and the distance d could be substantially equal to zero. In this case, the minimum distance d could? be small and what? close to zero, while the maximum operating distance d potr? be substantially equal to the maximum slip variation.

It is understood that the distance d could? be preferably considered among the surface 131? of the wall 131 in correspondence with the opening 132 and the surface 191? of plate 191.

The seat 110 and the pin 120 can be mutually configured to avoid mutual disengagement.

Conveniently, headquarters 110 will be able to include a pair of abutment surfaces 111, 111? opposite intended to act as a match for the pin 120. The latter can? include corresponding abutment surfaces 122, 122? opposite surfaces intended to abut with the corresponding surfaces 111, 111?.

When the 120 pin? in the retracted configuration, the surfaces 111 and 122 will be able to abut while the surfaces 111? and 122? can be spaced, while when the pin 120 ? in extended configuration, the surfaces 111 and 122 could be spaced while the surfaces 111? and 122? they may be batting.

Suitably, means could be provided for guiding the sliding of the pin 120 between the extended and retracted position and means for guiding the rotation of the same pin around the X axis.

Seat 110 will be able to comprising a portion 112 and a portion 113 able to guide the pin 120 in rotation and to guide the same in sliding with respect to the same X axis. comprise, or consist of, the opening 132. In other words, the side wall 132? of the latter can? define the sliding and rotating guide means of the portion 121 pin 120.

On the other hand, the 120 pin could? include a portion 123 opposite to the portion 121 which could? remain in correspondence with the portion 113 of the seat 110.

Preferably, the portions 121 and 123, so like the portions 112 and 113, they could be substantially cylindrical in shape and could have substantially the same diameter. In this way, the portions 121 and 123, 112 and 113 will be able to interact with each other to guide the pin 120 in rotation and translation with respect to the axis X1.

Preferably, the hinge 100 can be an automatic and/or control hinge.

In particular, the pin 120 potr? comprise cam means so that its rotation about the axis X1 promotes the sliding of a sliding element 140.

Conveniently, the hinge 100 can therefore comprising means for damping, promoting, hindering or freely allowing sliding of the sliding element 140.

The hinge 100 can be of a mechanical, hydraulic or potr? include both mechanical and hydraulic means. For example, in FIG. 30 and FIG. 30 ? shown is a hinge 100 with hydraulic means 150 for controlling and damping the sliding of the sliding element 140.

Conveniently, therefore, the pin 120 can? include a central portion 125 interposed between the portions 121 and 123 which could define cam means.

On the other hand, seat 110 will be able to comprising a corresponding central portion 115, interposed between the portions 112 and 113 to house the central portion 125.

Advantageously, this central portion 115 can include the abutment surfaces 111 and 111?. On the other hand, the central portion 125 of the pin 120 can including the respective abutment surfaces 122 and 122?.

Preferably, the surfaces 111 and 111?, 122 and 122? they can be substantially transversal or perpendicular to the X axis.

Advantageously, the distance between the abutment surfaces 111, 111? can I be greater than the distance between the surfaces 122 and 122?. In this way, portion 125 will be able to slide along the axis X1 inside the portion 115 of the seat 110.

Preferably, the difference between the distance between the abutment surfaces 111, 111? and the distance between the surfaces 122 and 122? can I define the maximum variation of the operating distance d.

Conveniently, the cursor element 140 can slide along a Y axis substantially perpendicular to the X1 axis. The cursor element 140 can comprising an operating surface 141 intended to interact with the portion 125 of the pin 120 so that the rotation of the latter promotes the sliding of the former and vice versa.

In other words, the surface 141 will be able to define the half cam followers 145.

Advantageously, the surface 141 will be able extend substantially parallel to the axis X1 for a length such that it interacts with the cam elements 125 in any operating position of the pin 120 between the retracted and extended positions.

Preferably but not exclusively, the system 1, as schematically illustrated in FIG. 1, may include the assembly 10 which allows the adjustment of the distance d and therefore the installation of the same in correspondence with irregularities.

The set 10 could? include any hinge, mechanical or hydraulic, as long as? allows the pin 120 to slide in the seat 110 as described above.

We will now describe some embodiments of a hinge 100 which can be used in the system 1 and/or in the assembly 10 or could it? be used in any way to move a closing element, for example a door A.

As better described below, the hinge 100 can be hydraulic and can? include a valve assembly 181 configured to open in the event of excessive pressure (so-called pressure relief valve), and/or to prevent the reflux of the working liquid (so-called non-return valve) and/or to allow an increase in the transit of the flow of liquid near of the closure of door A (so-called final click). In other words, advantageously, a single particularly compact valve assembly 181 can satisfy one or more of the functions described above.

The hinge device 100 can understand the hinge body 130 that could? include a working chamber 135. Preferably, the working chamber 135 could? comprising a portion 136 for housing the pin 120 thus defining the seat 110, and an elongated portion 137 defining the axis Y for housing a sliding cursor element 140.

In particular, room 135 could include a pair of back walls 138 138? opposite. Preferably, the portion 136 can understand wall 138? while the portion 137 could? understand the wall 138.

The cursor 140 will be able then scroll between a position distal to wall 138 (FIG. 7, FIG. 9, FIG. 14 and FIG. 28) and a position proximal to wall 138 (FIG. 4, FIG. 8, FIG. 10 and FIG. 24) .

The pin 120 could? understand the cam means 125 while the slider 140 could? include the cam follower means 145 so that the rotation of the former around the X1 axis promotes the sliding of the latter along the Y axis.

Conveniently can be provided a piston element 160 which could? slide in chamber 135 along the Y axis.

Possibly, the piston element 160 could? be connected with the cursor 140 so as to scroll with the latter. Possibly, the cursor 140 will be able to comprise or consist of the piston element 160.

In any case, the piston element 160 could? be operatively connected to the cam follower means 145 so that the rotation of the pin 120 promotes its sliding and vice versa.

On the other hand, resetting means acting on the piston 160 may be provided to promote its return from the proximal position to the distal position. For example, can such resetting means comprise a spring in itself? known.

According to a preferred but not exclusive embodiment, the piston element 160 can comprise a stem 161 operatively connected to the slider element 140 to slide with the same, and a head 165 sliding in the chamber 135.

The piston 160 and the cursor 140 could be integrally connected, for example by means of a pin, they could be forced against each other by elastic means or suitable means 149 could be provided for the operative coupling of the cursor 140 and the piston 160.

For example, this link can be made according to the teachings of the patent applications WO2018116275 and WO2020044143 in the name of the same applicant.

As shown in the attached figures, the cursor 140 can divide the chamber 135 into a first half-chamber 136 for the piston 120 and into a second half-chamber 137 for the piston 160.

Conveniently, the portion 137 of the chamber 135 can define a closed room that can? contain a working fluid, such as oil.

The piston element 160 could? then slide in the chamber 137 between an operating limit position in which the head 165 ? proximal to the back wall 138 and an opposite operating position in which the head 165 is distal from the bottom wall 138 corresponding to the positions distal and proximal to the wall 138 of the slider 140 described above.

The head 165 will be able to be inserted hermetically into the chamber 137 to divide the latter into at least a first and second compartment 176, 177 with variable volume.

In this way, when the piston element 160 ? in the proximal position, the compartment 176 can have maximum volume and the compartment 177 will be able? have minimum volume, while when the element piston 160 ? in the distal position the compartment 176 can have minimum volume and the compartment 177 will be able? have maximum volume.

The hinge 100 can then understand one or more? hydraulic circuits to allow the passage of the working fluid between the compartments 176, 177 upon sliding of the piston element 160 and therefore upon rotation of the hinge body 130 and of the pin 120 between the open and closed sash position .

In particular, the 100 hinge could comprise at least one circuit 171 for placing the compartments 176, 177 in fluid communication so that the fluid passes between the compartments 176 and 177 as the piston element 160 moves between the proximal position and the distal position, i.e. between the open and closed position of door A.

Preferably, this circuit 171 can be of type in s? known and can comprise at least one duct placed inside the hinge body 130 having an opening in the compartment 176 and an opening in the compartment 177.

Even if not shown in the attached figures, means 180 could be provided for controlling the flow of the working liquid inside the circuit 171. For example, it could? a calibrated opening should be provided so as to regulate the flow rate of the working fluid passing through and therefore the sliding of the piston element 160.

Advantageously, can moreover, a circuit 172 is provided for selectively fluidically connecting the compartments 176, 177 so that the working fluid passes from the compartment 177 to the compartment 176 when the piston element 160 passes from the distal to the proximal position, i.e. when closing door A.

Conveniently, this circuit 172 can be internal to the piston element 160. Preferably, this circuit 172 could? pass through the head 165 of the piston 160.

The hinge 100 can further comprising valve means 181 acting on the circuit 172 to selectively allow or prevent the passage of the working fluid through it.

Eventually, the head 165 potr? comprise both the circuit 172 and the valve means 181.

It is understood that in the event that this hinge 100 is used in the system 1 described above, the hydraulic circuit 171 and/or 172 thus? how the valve means 181 acting on them will be able to define the means 150 for controlling the sliding of the slider 140.

As better explained below, depending on the configuration of the valve means 181, the latter may act on the circuit 172 as a non-return valve, as a pressure relief valve and/or as a final trigger.

The figures from FIG.11 to FIG.29 show different configurations of the circuit 172 and of the valve means 181.

It is understood that these valve means 181 can be used in any hinge 100, and in particular, regardless of the configuration of the cam and cam follower means 125, 145 described above and/or regardless of the possible sliding of the pin 120 along its axis of rotation X1 .

Will you describe? now a particular embodiment of the valve means 181, for example illustrated in the figures from FIG. 10 to FIG. 15, and from FIG. 22 to FIG. 23, and from FIG. 24 to FIG.

29.

Circuit 172 will be able to include a conduit 173 that could? have an?opening 175? in correspondence with the compartment 177 and an opposite opening 175.

Preferably, the conduit 172 will be able understand the opening 175? fluidly connected with the compartment 177 and the opening 174?? fluidly connected with room 176.

The hinge 100 can furthermore comprise a disc-shaped element 166 with an internal through hole defining the duct 173 and a shutter 184, for example a ball, to act on the opening 175 at the end of the duct 173. Preferably, the opening 175 can? be circular and can have a smaller diameter than the ball 184.

Circuit 172 will be able to include a chamber 174. Preferably, the shutter 184 could? be placed in room 174.

In particular, the shutter 184 could? be mobile between a closed position in the vicinity? of the opening 175 in which it closes the latter and does not allow the passage of the working fluid through the conduit 173, and an open position distant from the opening 175 in which it allows the passage of the working fluid through the conduit 173.

Conveniently, means 189 can be provided configured to force the shutter 184 closed. The means 189 can for example comprise or be constituted by a spring.

In this way, the valve means 181 can be normally closed, and can the passage of oil from the compartment 177 to the compartment 176 through the circuit 172 can be prevented, thus defining a non-return valve.

Advantageously, can an annular element 185 placed in the chamber 174 and interposed between the shutter 184 and the spring 189 should be provided. Preferably, the annular element 185 could? be fitted on a cylindrical portion 166?? of the discoidal element 166.

Possibly, the annular element 185 could? be configured to drive the shutter 184 between the open and closed position. For example, the annular element could comprising a substantially cylindrical internal portion coaxial with the Y axis to guide the sliding of the shutter 184 along the same axis.

Room 174 could then understand a wall 174? abutment to act as a counterpart to the spring 189, while the annular element 185 could? include a corresponding annular projection 186. The spring 189 could? therefore remain interposed between the part 174? and the surface 186? of the projection 186 to force the annular element 185 against the ball 184 and therefore against the opening 175.

The annular element 185 could? then slide along the Y axis between a position distal to the opening 175 in which the shutter 184 allows the passage of the fluid and a position proximal to the opening 175 in which the shutter 184 does not allow the passage of the fluid.

Room 174 could include an?aperture 174?? to allow the passage of the fluid. In particular, the circuit 172 popr? therefore understand the duct 173 with the? opening 175? and 175, the chamber 174 and the opening 174??.

The annular element 185 could? cooperate with the sphere 184 to selectively prevent or allow the passage of the fluid through the circuit 172.

If the pressure inside the compartment 177 is particularly high, the fluid may enter conduit 173 and force against sphere 184. When is the force exerted ? greater than that exerted by the spring 189, the sphere 184 will be able to move away from the opening 175 and then allow the passage of the working fluid through the opening 175.

The fluid can then flow through the? opening 174?? in the compartment 176. This opening 174?? can I for example be made on the rod 161 of the piston 160.

In this case, the valve means 181 can then be configured to open when a predetermined pressure value is exceeded, thus acting as a pressure relief valve. This value of overpressure can? depend on the resistance of the spring According to a particular aspect of the invention, as illustrated in the figures from FIG.10 to FIG. 15, the disc-shaped element 166 could? understand one or more through openings 167, preferably a pair of through openings 167 intended to receive a corresponding pair of pins 168. The openings 167 may be substantially parallel to the axis Y and/or may be coaxial therewith.

The plugs 168 could have a? 169? intended to interact with the annular element 185 and one? opposite 169 intended to interact with the bottom wall 138. In particular, the pins 168 may have a substantially greater length than the thickness of the disc-shaped element 166.

The through holes 167 can be configured in such a way that once the pins 168 have been inserted therein, the ends? 169? are in correspondence with the surface 186?? of the protrusion 186 opposite the surface 186?.

In the embodiment illustrated in FIG. 11, FIG. 13 and FIG. 15, two pins 168 are present, passing through the peripheral openings 167. Preferably, the plugs 168 could have a diameter substantially equal to that of the openings 167 so that the oil only flows through the conduit 173.

Possibly the annular element 185 could? include a blind hole 185? for the? extremity? 169? of the plug 168. The blind hole 185? can I include surface 186??. In particular, the? Extremity? 169? of the plug 168 potr? be inserted in hole 185? by interference so that the pin 168 is coupled with the annular projection 185 and moves integrally with the same.

It is understood that any number of pins 168 and peripheral openings 167 can be provided. Preferably, three angularly equally spaced pins 168 may be provided so as not to promote rotation of the head 165 in a plane perpendicular to its sliding axis Y.

On the other hand, in the embodiment illustrated in FIG. 22 and FIG. 23 and in the one illustrated in FIG.25, FIG.27 and FIG.29 ? there is a single plug 168. In this case, the plug 168 will be able to? be passing through the duct 173 so that the end? 169? of the same is inside the duct 173 and is in contact with the ball 184 when the end? opposite 169 ? in contact with the wall 138. In other words, the conduit 173 will be able to then define the through openings 167.

In this case, plug 168 will be able to have a diameter substantially smaller than the diameter of the hole 173 so that the oil can seep into the interspace between the latter up to the opening 175. In other words, the circuit 172 will be able to? include this interspace.

In particular, in the embodiment illustrated in FIG.22 and in FIG. 23, the? extremity? 169? of the plug 168 ? fixed with the disc-shaped element 166, preferably at its annular portion 166??, so that the pin 168 slides with the head 165, while in the embodiment illustrated in FIG. 25, FIG. 27 and in FIG. 29, the? extremity? 169 of the plug 168 could? be fixed to the wall 138 so that the pin 168 remains substantially stationary when the head 165 slides.

The end? 169 can be fixed in the wall 138 so in itself? known, for example by interference.

On the other hand, according to a different embodiment it illustrates in FIG.18 and in FIG.

20, the stem 161 will be able include an annular projection 162 which could? then include the striking surface 174?? for the spring 189. Furthermore, the disc-shaped element 166 could? understand one or more peripheral through openings 167 for the pin 168. Eventually the annular element 185 could? include a blind hole 185? for the? extremity? 169? of the plug 168. The blind hole 185? can I include surface 186?? and can be in correspondence with one or more? through opening 167.

Conveniently, the plug 168 can? have a diameter substantially smaller than the diameter of the openings 167 so that the oil can seep into the space between the latter. In particular, when the annular element 185 is spaced from the disc-shaped element 166 (FIG. 20), the oil can? through the gap between the pin 168 and the through hole 167 and come out through the opening 174?? in the stem 161. On the other hand, when the annular element 185 ? in contact with the disc-shaped element 166 (FIG. 18) the oil cannot? flow from compartment 177 to compartment 176.

It is therefore understood that the circuit 172 could include both gap and conduit 173.

Therefore, when the? extremity? 169 of plug 168 ? in abutment with the wall 138, the pins 168 will be able to promote the removal of the annular element 185 from the discoidal element 166 and therefore will be able to allow the outflow of the oil from the compartment 177 to the compartment 176 through the circuit 172 thus defining the trigger function end of the valve means 181 as better described below.

Furthermore, in this case, the spring 189 could act both against the annular element 185, which could? then act as a shutter as described above, which against the ball 184. In this way it will be possible? obtain the non-return function of the valve means 181.

Finally, in the event of overpressure, the oil will be able to? flow in the duct 173 and force the ball 184 to open, thus allowing the overpressure function of the valve means 181.

In any case, when the piston 160 ? in a distal position from the wall 138, the valve means 181 can be normally closed thanks to the action of the spring 189 (FIG. 15, FIG. 18, FIG. 23 and FIG. 29).

Conveniently, when the valve means 181 are closed, the pins 168 will be able to have a portion 168? protruding from the disc-shaped element 166. In particular, will the pins 168 be able to protrude with respect to the surface 166? of the disc-shaped element 166 facing the back wall 138.

When moving the piston element 160 towards the bottom wall 138, the end? 169 of the plug or plugs 168 will be able to interact with the bottom wall 138, i.e. collide with the same.

This position of the piston element 160 could correspond to an angle ? predetermined. This angle? can I vary according to the length of the portion 168? plug 168 protruding from wall 166? of the discoidal element 166.

It will be understood that in the embodiment of FIG. 24, the portion 168? can I be the portion protruding from the back wall 138.

Possibly, by changing the length of the pins 168, it will be possible make a hinge 100 with a different shutter angle.

For example, in the illustrated figures the shooting angle ? about 10?. Therefore door A can? be checked on closing in 80? and 10?. It is understood that this angle could be any according to need?.

If the piston element 160 continues its stroke towards the back wall 138, the pins 168 will promote the opening of the valve means 181, for example the removal of the shutter 184 from the opening 175 or of the annular element 185 from the discoidal element 166, thus allowing the passage of the working fluid through the circuit 172 from the compartment 177 to the compartment 176, thus realizing the so-called final click up to the stroke end position of the piston 160 (FIG.11, FIG.20, FIG.22 and FIG.25).

In particular, in the latter configuration, in the embodiment from FIG. 4 to FIG. 7, the? extremity? 169 can be in contact with the back wall 138 while the? extremity? opposite 169? can I be in contact with the ball 184, in the embodiment of the figures from FIG.10 to FIG.16, the end? 169 can be in contact with the back wall 138 while the? extremity? opposite 169? can I be in contact with the surface 186?? of the annular boss 186, while in the embodiment from FIG. 17 to FIG. 21, the? extremity? 169 can be in contact with the back wall 138 while the? extremity? opposite 169? can I be in the blind hole of the annular element 185, while in the embodiment from FIG. 24 to FIG. 29, the? extremity? 169 can be fixed with the back wall 138 while the? Extremity? opposite 169? can I be in contact with the 184 ball.

Thanks to what has been described above, the head 165 of the piston 160 will be able to be configured to act as a non-return valve, as a pressure relief valve and as a final trip.

In this way the hinge 100 will be able to be particularly compact.

It is understood that the piston element 160 with the valve means 181 described above will be able to be used in any hydraulic hinge. Preferably, this hinge 100 can comprise a piston 160 with a head 165 hermetically inserted into a chamber 135 to divide the latter into the two compartments 176, 177.

The found ? susceptible to numerous modifications and variations, all of which are within the scope of the inventive concept expressed in the attached claims. All the details can be replaced by other technically equivalent elements, and the materials can be different according to requirements, without departing from the scope of protection of the invention.

Even if the found ? been described with particular reference to the accompanying figures, the reference numbers used in the description and in the claims are used to improve understanding of the invention and do not constitute any limitation to the claimed scope of protection.

Claims (10)

1. An assembly for the rotatable coupling around an axis of rotation (X) of a closure element (A), such as a wing, a door or similar, and a stationary support element (S), such as a frame , a wall or the like, the whole comprising: - an attachment element (190) which can be anchored to one of the stationary support structure (S) and the closing element (A), - a hinge device (100) which can be anchored to the other between the stationary support structure (S) and the closure element (A); wherein said attachment element (190) and said hinge device (100) are rotationally coupled to each other to rotate reciprocally around the axis (X) between at least one open position of the closing element and a closed position of the closing element closure (A); wherein when said attachment element (190) and said hinge device (100) are mutually engaged they exhibit a predetermined operating distance (d), said attachment element (190) and said hinge device (100) being mutually configured so that once they are engaged they slide reciprocally along the axis (X) to vary said predetermined operating distance (d). 2. Assembly according to the preceding claim, wherein said hinge device (100) includes a hinge body (130) and a pin (120) defining the axis (X), said hinge body (130) and said pin (120) being rotationally coupled to each other to rotate reciprocally around the axis (X) between at least one first operating position corresponding to the open or closed position of the closing element (A) and a second operating position corresponding to the closed or open position of the closing element closure (A), in which said pin (120) ? integrally coupled with said attachment element (190), said hinge body (130) comprising a seat (110) for said pin (120), said seat (110) and said pin (120) being mutually configured in such a way that the second is sliding along the axis (X) in the first, the sliding of said pin (120) in said seat (110) defining the maximum variation of said predetermined operating distance (d). 3. Assembly in accordance with the preceding claim, wherein said pin (120) comprises a portion (121) for integral coupling with said attachment element (190), said hinge body (130) having an upper wall (131) intended to remain facing said attachment element (190), said wall (131) comprising a through opening (132) for said coupling portion (121) of said pin (120), the latter being slidable through said through opening (132). 4. Assembly according to claim 2 or 3, wherein said hinge body (130) has a pair of first and second opposite abutment surfaces (111, 111?), said pin (120) comprising respective first and second abutment surfaces ( 122, 122?) intended to interact with said first and second abutment surfaces (111, 111?) of said hinge body (130), said pin (120) being movable between a retracted configuration in which said first abutment surfaces (111 , 122) of respectively said hinge body (130) and said pin (120) abut each other and said second surfaces (111?, 122?) of respectively said hinge body (130) and said pin (120) are spaced between them, and an extended configuration in which said first abutment surfaces (111, 122) of respectively said hinge body (130) and said pin (120) are spaced and said second surfaces (111?, 122?) of respectively said hinge body (130) and said pin (120) butt against each other. 5. Assembly according to the preceding claim, wherein the distance between said first surfaces (111, 122) of respectively said hinge body (130) and said pin (120) define the maximum variation of said operating distance (d). 6. Together according to one or more? of claims 2 to 5, wherein said maximum variation of operating distance ? between 1mm and 10mm, preferably about 7mm. 7. Assembly in accordance with any one of claims 2 to 6, wherein said hinge body (130) comprises a working chamber (135) defining a second axis (Y) substantially perpendicular to said axis of rotation (X) and a slider element (140) sliding in said working chamber (135), said pin (120) including cam means (125), said slider element (140) further comprising cam follower means (145) operatively connected with said cam means ( 125) so that the mutual rotation of said pin (120) and said hinge body (130) corresponds to the sliding of said cursor element (140). 8. Assembly according to the preceding claim, wherein said seat (110) comprises guide means (112, 113) for guiding said pin (120) in sliding along and in rotation with respect to said axis (X). 9. Assembly according to the preceding claim, wherein said pin (120) comprises a substantially cylindrical first operating portion (121) and a substantially cylindrical second operating portion (123), and a third operating portion (125) interposed between said first (121) ) and second portion (123) which includes said cam means, said seat (110) having corresponding fourth and fifth shaped portions (112, 113) intended to interact respectively with said first and second portions (121, 123) operative to guide these latest. 10. Assembly according to the preceding claim, wherein said seat (110) further comprises a sixth central portion (115) intended to house said cam means (125), said sixth portion (115) comprising said abutment surfaces (111, 111 ?) substantially perpendicular to said axis (X), said abutment surfaces (111, 111?) presenting a substantially greater distance than the height of said third portion (125) of said pin (120) so as to allow sliding of the latter along the axis (X) between said abutment surfaces (111, 111?).