MECHANICAL HINGE

The present invention relates to a mechanical hinge of the type as recited in the preamble of the first claim.

In particular, it relates to a device binding two elements (such as a window and its frame) to each other allowing a reciprocal rotation of the elements along a predetermined rotation axis.

As known, mechanical hinges are frequently used to constrain a mobile element to a support structure at an access aperture thereof to an inner compartment and to rotate the mobile element relative to the structure, defining a closed position in which the mobile element superposes the opening preventing access to the compartment and an open position in which the element is moved away from the opening allowing access to the compartment.

Hinges, due to their cheapness and simplicity, have many applications. For example, they are used to constrain and rotate a door in relation to a piece of furniture, a window or a door with respect to a frame, shutters against a wall.

Such hinges are made up of a first butt hinge which can be constrained to the mobile element and a second butt hinge which can be constrained to the support structure; and a flap hinge hinging the butt hinges to each other an axis of mutual rotation.

The prior art mentioned above has several significant drawbacks.

A first important drawback is to be identified in the fact that the hinge, by defining an idle constraint between the mobile element and the support structure, does not permit the locking of the mobile element.

This drawback is relevant in any application of a hinge. For example, in the case of a window/cabinet, it often happens that the mobile element, pushed by the wind or by an accidental collision of a person, bangs, possibly violently, against the support structure, breaking or even against a person, injuring them,

!n addition, this drawback also manifests itself when a person, applying too much force or torque to the mobile element causes it to open abruptly and strike a wall damaging itself.

To resolve these issues relating to windows/doors, catches are often provided. Such catches, in the case of windows, have a first fiat plate perpendicular and integral with the wall; and a second flat plate perpendicular to the first plate and defining an abutment for the mobile component; and a catch, hinged to the first flat plate, so that the operator, by pressing on it, can turn it, tightening and clamping the mobile element against the abutment.

In the case of doors, the stops are dowels glued on the ground so as to limit the stroke and rotation of the mobile element.

Such stops, while defining an improvement, do not solve the problem definitively. In fact, such stops, besides not being aesthetically attractive, only block the stroke upon reaching the fully open position.

Moreover, the catches for windows, being almost always located on the outer side of the wail and far from the opening, can be very difficult to use if not downright impossible for children or people of short stature.

This difficulty is determined by the distance of the catch from the opening which, in the case of people of small stature, makes it impossible to reach the abutment and thus activate the latch.

A further drawback of door stops is that with time, they detach from the ground and are not able to perform their function. !n this situation the technical purpose of the present invention is to devise a mechanical hinge able to substantially overcome the drawbacks mentioned.

Within the sphere of said technical purpose one important purpose of the invention is to have a mechanical hinge which makes it possible to avoid the application of unwanted forces, for example by impact or wind, leading to unwanted rotation of the mobile part.

Another important purpose of the invention is to have a hinge which is able to block the mobile element in relation to the support structure.

A further purpose is to have hinges which make the use of catches or stops unnecessary.

The technical purpose and specified aims are achieved by a mechanical hinge as claimed in the appended Claim 1 .

Preferred embodiments are evident from the dependent claims.

The characteristics and advantages of the invention are clearly evident from the following detailed description of preferred embodiments thereof, with reference to the accompanying drawings, in which:

Fig, 1 shows a sagittal cross-section of the mechanical hinge in use;

Fig, 2 shows the mechanical hinge in cross-section in Fig. 1 in a different position;

Fig, 3 presents, in an exploded and sagittal cross-section, the mechanical hinge according to the invention;

Fig. 4 shows, in sagittal cross-section, a mechanical hinge in use;

Fig, 5 shows, in sagittal cross-section, the mechanical hinge in Fig. 3 in a different position;

Fig, 6 shows, in an exploded and sagittal cross-section, the mechanical hinge in Figs. 4 and 5;

Fig, 7 shows, in axonornetry, some details of the mechanical hinge in Figs. 4-

6;

Fig, 8 presents, in an exploded and sagittal cross-section, a portion of the mechanical hinge according to the invention;

Fig, 9 shows a detail of the mechanical hinge;

Fig, 10a illustrates another part of the mechanical hinge;

Fig. 10b is a different view of the component in Fig. 10a;

Fig, 10c represents a detail of the component of figs. 10a-10b;

Fig, 11 a shows an alternative to the component of figs. 10a-10c;

Fig. 11 is a different view of the component in Fig. 1 1 a;

Fig, 11 c shows a detail of the component in figs. 1 1 a-1 b;

Fig, 12a shows, in sagittal cross-section, a mechanical hinge assembly according to the invention in use;

Fig, 12b shows the assembly in Fig. 12a in a different configuration.

Herein, the measures, values, shapes and geometric references (such as perpendicularity and parallelism), when used with words like "about" or other similar terms such as "approximately" or "substantially", are to be understood as except for measurement errors or inaccuracies due to production and/or manufacturing errors and, above ail, except for a slight divergence from the value, measure, shape or geometric reference which it is associated with. For example, said terms, if associated with a value, preferably indicate a divergence of not more than 10% of said value.

In addition, where used terms such as "first", "second", "upper", "lower", "main" and "secondary" do not necessarily refer to an order, a priority relationship or relative position, but may simply be used to more clearly distinguish different components from each other.

With reference to said drawings, reference numeral 1 globally denotes the mechanical hinge.

It is adapted to hinge a first element 11 to a second element 12 defining a reciprocal axis of rotation 1a between the elements.

For example, the mechanical hinge 1 is designed to be used in a window frame 10 to hinge a first static element 1 1 (such as a frame or a wall) to a second mobile element 12 identifiable in a window, a panel, a door, a hatch. Alternatively, it is usable, for example in a window frame 10, for hinging together two mobile elements 1 1 and 12 such as, for example, two panels.

The mechanical hinge 1 comprises at least a first unit 2 binding to the first element 1 1 comprising a first housing 2a extending along the rotation axis 1 a; at least a second unit 3 binding to the second element 12 comprising a second housing 3a extending along the axis 1 a; and a pin 4 adapted to be at least partially inserted in the housings 2a and 3a.

The first binding unit 2 can be integrally constrained to the first element, for example by means of screws or glue.

It comprises a first constraint plate 21 to the first element 1 1 ; and a first hollow cylinder 22 defining the first housing 2a and a first extension axis substantially coinciding with the axis of rotation 1 a.

The first cylinder 22 and, therefore, the first housing 2a suitably have one open and one closed base.

The first plate 21 and the first cylinder 22 are joined together and, in particular, the first binding unit 2 is in one piece. !n some cases, the first cylinder 22 may comprise an annular body defining the first housing 2a and a cap designed to engage, from the other side the second binding unit 3 and, for example, through a threaded coupling, the annular body closing the first housing 2a.

The second binding unit 3 can be integrally constrained to the second element 12, for example by means of screws or glue.

It comprises a second constraint plate 31 to the second element 12; and a second hollow cylinder 32 defining the second housing 3a and a second extension axis substantially coinciding with the axis of rotation 1 a.

The second plate 31 and the second cylinder 32 are integral with each other. In detail, the second binding unit 3 is in one piece.

The second cylinder 32 defines a through cavity allowing the pin 4 to position itself in both housings 2a and 3a.

Appropriately, the second binding unit 3 may comprise an additional cylinder 33 extending along said second extension axis and adapted to place itself at least partially and, specifically, almost entirely in the first housing 2a engaging the binding units 2 and 3.

The additional cylinder 33 is hollow so as to define a housing for part of the pin 4 and thus, being available in the first housing 2a, accommodating said part 4 of the pin in the first housing 2a.

Appropriately, the additional cylinder 33 has a closed bottom 33a of said housing. The additional cylinder 33 has a substantially smaller cross-section 32 so as to define, between them, an inner abutment 3b for the pin 4 and, appropriately, an outer abutment 3c for the first cylinder 22. In particular, the additional cylinder 33 has a cross section substantially 50% smaller than the cross section of the second cylinder 32.

The cylinders 32 and 33 and the second plate 31 are joined together and, preferably, the second binding unit 3 is in one piece.

The hinge further comprises the pin 4, placed at least partially inside the housings 2a and 3a.

The pin 4 comprises a button 41 adapted to position itself, preferably in part, in the second cylinder 32; and preferably a cylindrical block 42 defining an extension of the button 41 and adapted to position itself inside the first cylinder 22.

The cylindrical block 42 has a cross-section smaller than the button 41 so to define between them, an abutment ledge 4a for the inner abutment 3b. Substantially it has a cross-section less than half the cross-section of the button 41 .

The button 41 has cross-section counter-shaped to the second cylinder 32 so as to position itself inside it.

It has an axial length substantially at least equal and, in particular, substantially greater than the axial length of the second cylinder 32 so as to allow the pin 4 to protrude from the second housing 3a.

It should be noted that the term axial indicates, throughout the document, a length, a stroke, a force, a displacement and/or a sliding along the rotation axis 1 a. In the same way the term radial indicates, throughout the document, a length, a stroke, a force, a displacement and/or a sliding perpendicular to the rotation axis 1 a.

The cylindrical block 42 has a cross-section counter-shaped to the additional cylinder 33 so as to position itself inside if.

!n some cases, the cylindrical block 42 may be at least partially made of elastomeric material so as to oppose an excessive axial sliding of the pin 4 compressing it axially. The button 41 and the cylindrical block 42 are joined together and, in particular, the pin 4 is made in one piece.

Advantageously, the mechanical hinge 1 comprises a first rotational constraint 5 adapted to prevent a mutual rotation between the pin 4 and the first binding unit 2 around the rotation axis 1 a; and a second rotational constraint 6 adapted to prevent a mutual rotation between the pin 4 and the second binding unit 3 around the rotation axis 1 a.

More advantageously, at least one of the rotational constraints 5 and 6 is resolvable so to define, for the mechanical hinge 1 , at least one stop configuration (Fig. 2 and 5) between the units 2 and 3 and, thus, between the elements 1 1 and 12 and at least one mobile configuration (Figs. 1 and 4) between the binding units 2 and 3 and, consequently, between the elements 1 1 and 12.

In particular, in the at least one stop configuration the rotational constraints 5 and 6 block the rotation between the pin 4 in relation to each binding unit 2 and 3 preventing a rotation between said units 2 and 3. Preferably, the at least one stop configuration is stable i.e. such that the rotational constraints 5 and 6 block the mutual rotation of the pin 4 in relation to each binding unit 2 and 3 unless at least one of the constraints 5 and 6, and preferably the first constraint 5, breaks.

In the at least one mobile configuration, at least one of the rotational constraints 5 and 6, appropriately only one of the constraints 5 and 6, is loose, allowing a mutual rotation between the pin 4 and at least one binding unit 2 and/or 3 and hence a reciprocal rotation between the units 2 and 3.

Preferably, only the first constraint 5 is resolvable. Accordingly, in the stop configuration the pin 4 is rotationaily integral with both binding units 2 and 3 preventing a reciprocal rotation of the elements 1 1 and 12, while, in the mobile configuration, the pin 4 is rotationaily integral with the second unit 3 only and rotationaiiy mobile in relation to the first unit 2 permitting a reciprocal rotation of the elements 1 1 and 12.

The first rotational restraint 5 is adapted to prevent a mutual rotation between the pin 4 and the first unit 2. In detail, if is adapted to prevent a mutual rotation between the pin 4 and the first binding unit 2 and allows the pin 4, preferably exclusively, to slide axially with respect to said first binding unit 2.

The first rotational constraint 5 comprises at least a first interlocking element joined to the pin 4 and at least one second interlocking element joined to the first binding unit and adapted to engage at least a first interlocking element realizing the rotational constraint 5.

!n particular, the pin 4 is adapted to translate along the axis of rotation 1 a so as to reciprocally move, preferably along an axial and/or radial direction, the interlocking elements and thus selectively define the stop configuration pulling together and engaging said contrast elements and the mobile configuration moving away and thus mutually disengaging said contrast elements.

In detail, the at least one first interlocking element may comprise, as shown in Fig. 3, at least one reference 51 tooth protruding radially from the axis 1 a and appropriately joined to the pin 4.

In particular, the at least one first interlocking element may comprise a plurality of reference teeth 51 (preferably four) roughly angularly equally spaced from each other.

Each reference tooth 51 protrudes from the cylindrical block 42 and preferably is integral with the block 42 and placed at the end of the cylindrical block 42 proximal to the bottom 33a so as to be adapted to position itself in the first housing 2a. The at least one second interlocking element may comprise, as shown in Fig. 3, at least one contrast tooth 52 placed in the first housing 2a, radially protruding from the axis 1 a and appropriately integral with the first binding unit 2.

!n this case, the pin 4 is adapted to translate along the rotation axis 1 a so as to reciprocally move the teeth 51 and 52, preferably in an axial direction. Thus, the axial translation of the pin 4 is adapted to selectively define the stop configuration mutually axially translating the teeth 51 and 52 and thus arranging them in mutual contact; and the mobile configuration mutually moving the teeth 51 and 52 away from each other to disengage them.

The at least one contrast tooth 52 is adapted to abut with the at least one reference tooth 51 preventing a mutual rotation of the pin 4 and the first binding unit 2, i.e. forming the first rotational constraint 5.

Appropriately, at least a second interlocking element may comprise several contrast teeth 52 roughly equally angularly spaced from each other so that between them a sliding slot extending substantially parallel to the axis of rotation 1 a is defined for each reference tooth 51 .

Said sliding slot allows the pin 4 to move axially in relation to the first binding unit 2 defining an axial sliding between the teeth 51 and 52 so as to selectively create or dissolve the first rotational constraint 5. In particular, the pin 4 moves the teeth 51 and 52 in relation to each other so that, in the stop configuration, they are in contact along a direction tangential to the axis 1 a preventing a reciprocal rotation between the units 2 and 3 and, in the mobile configuration, they are placed axially far apart so as not to be in contact with each other along said tangential direction allowing a reciprocal rotation between the units 2 and 3.

The reference teeth 51 may be integral with the cylindrical block 42. The contrast teeth 52 may be integral with the first cylinder 22.

Alternatively, they may be axially mobile with respect to the first cylinder 22. In this case, shown in Fig. 8, the first constraint 5 comprises a mobile ring 53 integrally rotationaliy constrained to the first cylinder 22 and on which the contrast teeth 52 are made; and preferably axially movable by an elastic element 54, appropriately a compression spring, placed between said ring 53 and the bottom of the first housing 2a.

The first constraint 5, in order to have the mobile ring rotationaliy constrained and axially movable with respect to the first cylinder 22, comprises at least one recess 55 made on the first cylinder 22 and extending parallel to the axis of rotation 1 a; and at least one raised section 56 radially protruding from the ring and adapted to slide in the recess 55 making the mobile ring 53 rotationaliy constrained and axially mobile with respect to the first cylinder 22.

The axial length of the recess 55 and thus the axial stroke 53 of the mobile ring is at least equal, and preferably substantially greater than the maximum axial length of the teeth 51 and 52 so as to enable the mechanical hinge 1 to vary its configuration between the stop and mobile configurations.

In order to prevent said mutual rotation between the pin 4 and first unit 2, the reference 51 and contrast teeth 52 define, respectively, at least one reference surface and at least one contrast surface not perpendicular to the axis of rotation 1 a so as to come into contact with each other preventing said reciprocal rotation. In particular, each reference tooth 51 defines at least one reference surface not perpendicular and preferably substantially parallel to the axis of rotation 1 a. More specifically, it defines two reference surfaces opposite each other and substantially parallel to the axis of rotation 1 a. Each contrast tooth 52 defines at least one contrast surface preferably substantially parallel to the axis 1 a, In particular, it defines two opposite contrast surfaces preferably substantially parallel to the axis 1 a.

Preferably, each reference tooth 51 defines at least one reference surface substantially parallel to the axis of rotation 1 a; and each contrast tooth 52 defines at least one contrast surface substantially parallel to the axis 1 a and thus to at least a reference surface of the reference teeth 51 so as to prevent the mutual rotation of the pin 4 and first binding unit 2 in at least one direction of rotation (that of drawing together the contrast and reference surfaces) so as to define said at least one stop configuration of a stable type in said direction of rotation.

More preferably, each reference tooth 51 defines two reference surfaces substantially parallel to the axis of rotation 1 a; and each contrast tooth 52 defines two contrast surfaces substantially parallel to the axis 1 a and, accordingly, to the two reference surfaces of the reference teeth 51 thereby preventing the mutual rotation of the pin 4 and first binding unit 2 in both directions of rotation and, therefore, defining said at least one stable stop configuration in said both directions of rotation. Even more preferably, the angular distance between contrast surfaces of adjacent contrast teeth 52 and thus the angular extension of the sliding groove is practically equal to the radial thickness of a reference tooth 51 .

Alternatively, at least one contrast tooth 52 has a contrast surface substantially parallel to the axis 1 a to prevent, in a first direction, said reciprocal rotation; and the other surface transversal to the axis 1 a to prevent, in an opposite direction to the previous, said reciprocal rotation except in the case of forcing, !n a further alternative, each contrast tooth 52 has both contrast surfaces transverse to the axis of rotation 1 a so as to prevent, in both directions, said reciprocal rotation except in the case of forcing.

The expression "prevent said reciprocal rotation except in the case of forcing" indicates how the mutual contact between the teeth 51 and 52 prevents a mutual rotation between the pin 4 and first binding unit 2 unless the constraint is forced, i.e. unless a force/torque greater than that given by the friction between the teeth 51 and 52 is applied to an element 1 1 or 12 and hence to a binding unit 2 or 3. The contrast surface, when transverse to the axis of rotation, 1 a, defines with respect to it an angle of inclination between 30° and 60° or alternatively, substantially less than 10°.

The second rotational restraint 6 is adapted to prevent a mutual rotation between the pin 4 and the second binding unit 3. In detail, it is adapted to prevent a mutual rotation between the pin 4 and the second binding unit 3 and allow the pin 4, preferably exclusively, to slide axially with respect to the first binding unit and in detail with respect to the second binding unit 33.

The second rotational constraint 6, comprises, inside the second housing 3a, at least one guide 61 made on the second cylinder 32 and extending substantially parallel to the axis of rotation 1 a; and at least one slider 62 integral with the button 41 and adapted to engage the guide 61 preventing the mutual rotation of the pin 4 and the second binding unit 3 and, preferably, a mutual axial sliding between said pin 4 and the second binding unit 3.

In particular, the second rotational constraint 6 comprises several guides 61 (preferably four) roughly equally angularly spaced; and several sliders 62 (preferably four) substantially equally angularly spaced.

The slider 62 protrudes from the button 41 radially to the axis of rotation 1 a (Fig. 3). Alternatively, the slider 62 protrudes from the cylindrical block 42 (Fig, 9). The guide 61 is identifiabie in a throat extending substantially along the axis 1 a and made on the second cylinder 32,

It has an extension almost equal to said axial stroke so as to allow the slider 62 to slide on the guide for at least said axial stroke.

Alternatively to the slider 62 and to the guide 61 , the second rotational constraint 6 comprises, for each reference tooth 51 at least one slot 63 made on the additional cylinder 33 and adapted to house the reference tooth 51 defining said second rotational constraint 6.

!t can be seen how, in the case in which the second rotational constraint 6 has no slider 62 and 62 and thus comprises exclusively one or more slots 63, the pin 4 may be integral with the second cylinder 32 and optionally be made in one piece with the second cylinder 32.

In particular, the slot 63 is a through slot allowing the reference tooth 51 to protrude from the additional cylinder 33 and engage the contrast tooth 52 defining the first rotational constraint 5 and thus placing the mechanical hinge 1 in the stop configuration.

It extends practically parallel to the axis of rotation 1 a and, appropriately, has a length such as to define for the pin 4, said axial stroke.

In a further alternative, the second rotational constraint 6 comprises prominences 62, the sliding channels 61 and the through slots 63.

The mechanical hinge 1 may comprise elastic means 7 adapted to work in opposition to an axial displacement of the pin 4 and thus defining mutual movement of the teeth 51 and 52. They are therefore suitable to work in mutual axial opposition between the teeth 51 and 52.

In particular, the elastic means 7 are adapted to oppose an axial shift moving the teeth 51 and 52 apart and so as to keep the reference teeth 51 in contact with the contrast teeth 52 and thus activate the first rotational constraint 5, Consequently they are adapted to maintain at least the first rotational constraint 5 active, i.e. the reference teeth 51 in contact with the contrast teeth 52 working, therefore, in opposition to an axial force moving the teeth 51 and 52 apart.

The elastic means 7 are placed in the first cylinder 22 between the second binding unit 3 and the pin 4 and, specifically, between the base 33a and the cylindrical block 42.

They comprise a spring, appropriately, a compression spring.

Lastly, the mechanical hinge 1 may comprise stop means 8 adapted to block the axial sliding of the pin 4, at least with respect to the second cylinder 32, so as to block the mechanical hinge 1 in at least one of the stop and mobile configurations and, preferably, in the mobile configuration only.

The stop means 8 (Fig. 2) comprise at least one cavity 81 , appropriately, a through cavity, made on the second cylinder 32 and facing the pin 4; and an insert 82, made on the pin 4, adapted to block the axial sliding of the pin 4 inserting itself in the cavity 81 when the mechanical hinge 1 is in the mobile configuration.

The insert 82 may comprise a ball adapted to engage/disengage from the cavity 81 by forcing or, alternatively, by pressing a compression spring.

Optionally, as shown in Fig. 9, the insert 82 can be constrained to a leaf spring. Said leaf spring is identifiable in a rod extending substantially parallel to the axis of rotation 1 a, having one end interlocked to the pin 4 and presenting, integral with it and close to the other end, the insert 82 which can therefore translate substantially perpendicular to the axis of rotation 1 a, flexing the leaf spring.

Alternatively, the stop means 8 may comprise the insert 82 mobile with respect to the pin 4 and, in detail, integral with the second cylinder 32; and a cam 83 for the insert 82 appropriately made in bas-relief on the pin 4,

The insert 82 is thus mobile with respect to the pin 4. It protrudes, almost perpendicular to the axis of rotation 1 a, inside the second housing 3a so as to engage the cam 83. Therefore, when an axial force is applied to the pin 4 drawing together the teeth 51 and 52, the insert 82 slides in the cam 83 commanding the passage of the mechanical hinge 1 between the stop and mobile configurations. In detail, the sliding of the insert 82 in the cam 83 causes a rototranslation of the pin 4 which thus slides axially, varying the axial distance of the teeth 51 and 52 and simultaneously rotates about the axis of rotation 1 a varying the angular distance between said teeth 51 and 52.

More specifically, the cam 83 is shaped so that the insert 82, upon cessation of the axial force on the pin 4, stably blocks the axial sliding of the pin 4 and thus of the mechanical hinge 1 in the stop and mobile configuration.

To this end, the cam 83 defines for the pin 4 at least one high stop position and at least one low stop position. It is thus appropriately segmented defining a path inclined with respect to the axis of rotation 1 a (Figs. 10a, 10b, 10 c, 1 1 a, 1 1 b and 1 1 c show two examples of pins 4 with possible examples of shaping of the cam 83 and the corresponding two plane extensions of the cam 83).

In a second embodiment of the mechanical hinge 1 , the button 41 and the second rotational constraint 6 may vary while the other elements (the first constraint 5, the binding units 2 and 3, the elastic means 7 and stop means 8 and the rest of the pin 4) remain substantially the same as those described above except for the differences described below.

For example, the button 41 , as shown in Figs. 4-7, comprises a pressure body 411 adapted to protrude from the second cylinder 32 so as to be actuated by the operator; a mobile body 412 integral with the cylindrical block 42 and adapted to be operated by the pressure body 41 1 commanding a variation of mechanical hinge 1 configuration; and an annular body 413 interposed between the bodies 41 1 and 412.

The bodies 41 1 , 412 and 413 are substantially circular having as their preferred extension axis the axis of rotation 1 a.

The pressure body 41 1 and the annular body 413 are loosely constrained to each other so as to reciprocally idly rotate around the axis of rotation 1 a and translate along the axis of rotation 1 a. Consequently, the annular body 413 has a first reference pin 413a, appropriately cylindrical, inserfable in a first hole 411 a of the mobile body.

The first pin 413 and the first hole 41 1 a have main extension axes practically coinciding with the axis of rotation 1 a.

Similarly to the bodies 41 1 and 413, the mobile body 412 and annular body 413 are loosely constrained so as to mutually idly rotate around the axis 1 a and translate along the rotation axis 1 a. To such purpose the annular body 412 has a second reference pin 412a, appropriately cylindrical, insertable in a first second hole 413b of the annular body 413.

The first reference pin 412a and the first hole 413b have main extension axes practically coinciding with the axis of rotation 1 a.

In this case, the second constraint 8 is made between the second cylinder 22 and the pressure body 41 1 which is thus rotationaily integral and axiaiiy mobile relative to the second binding unit 3.

Therefore, the second constraint 6 includes a first sliding groove 64 made on the second cylinder 32 and extending substantially parallel to the axis of rotation 1 a; and a first relief 65 protruding radially to the axis of rotation 1 a from the pressure body 41 1 and suitable to engage the first sliding groove 84 making the pressure body 41 1 rotationaily integral and axia!ly mobile relative to the second binding unit 3,

Appropriately, the first sliding groove 64 is of such a length as to define, for the first relief 65 and, therefore, for the pin 4 an axial stroke at least equal and preferably substantially greater than the maximum axial length of the teeth 51 and 52,

The second rotational constraint 6 is moreover made between the second cylinder 32 and the mobile body 412 which is thus rotationaily integral and axially mobile relative to the second binding unit 3.

It thus comprises a second sliding groove 66 made on the second cylinder 32 and extending substantially parallel to the axis of rotation 1 a; and a second relief 67 protruding radially to the axis of rotation 1 a from the mobile body 412 and suitable to engage the second sliding groove 66 making the mobile body 412 rotationaily integral and axially mobile relative to the second binding unit 3,.

In the same way as the first groove 64, the second sliding groove 66 is of such a length as to define, for the pin 4, the above defined axial stroke.

The annular body 413 is appropriately free to rotate and translate with respect to the second unit 3,

To force the activation/release of the first rotational constraint 5, the pressure body 41 1 is adapted to command, by its own axial sliding, an axial sliding of the mobile body 412 and thus of the cylindrical block 42 mutually coupling/ spacing the teeth 51 and 52. In particular, the pressure body 41 1 is adapted to command, sliding axia!ly relative to the second cylinder 32, both an axial sliding of the bodies 412 and 413 and a rotation around the axis of rotation 1 a of the annular body 413 having appropriately, a predetermined angular breadth.

To this end, the hinge 1 comprises a retractable mechanism 9 of the type found in retractable pens.

This retractable mechanism 9 comprises a first contact face 91 integral with the pressure body 41 1 ; a second contact face 92 integral with the annular body 413 and adapted to come into contact with the first face 91 ; at least one stop 93 integral with the second cylinder 32 and adapted to abut with the second contact face 92 blocking the axial sliding of the bodies 413 and 412, and thus of the reference teeth 51 with respect to the contrast teeth 52 ; and at least one raceway 94, shown in Fig. 7, for the movement of the stop 93 made on the annular body 413.

The contact faces 91 and 92 are counter-shaped so that the faces 91 and 92 engage with each other transforming an axial sliding of the pressure body 41 1 in an axial sliding of the annular body 413 and of the mobile body 412 in a rotation around the axis of rotation 1 a of the annular body 413 only.

The advancement of the annular body 413 and its simultaneous rotation put the stop 93 in contact with the second contact face 92 blocking the axial sliding of the bodies 413 and 412 and keeping the mechanical hinge 1 in the stop configuration. Alternatively, these two simultaneous movements of the annular body 413 put the stop 93 in a raceway 94 allowing an axial sliding of the bodies 412 and 413 such as to move the teeth 51 and 52 away from each other and have the hinge 1 in the mobile configuration.

The contact faces 91 and 92 have, to this end, a spiral extension and, in particular, a saw-tooth, i.e. characterised by a surface transverse to the axis 1 a and by a surface parallel to the axis 1 a.

The second contact face 92 is divided into sectors by one or more raceways 94. !n particular, each raceway 94 divides the second contact face 92 into areas of extension substantially equal to the wavelength of the helical extension so as to allow the stop 93 to stop permanently in a valley of the profile, i.e. at a minimum distance from the bottom 33a. More specifically, each raceway 94 splits the second contact face 92 into areas comprising a saw tooth and preferably two saw teeth so as to allow the stop 93 to stop permanently between said two teeth.

As described above, the stop 93 is adapted to block the axial sliding of the annular body 413 and of the mobile body 412 keeping in reciprocal contact with each other the teeth 51 and 52 and thus keeping active the first constraint 5.

For this purpose the second contact face 92 has a radius greater than the first face 91 so as to define a portion of the second face 92 protruding from the first face 91 and, therefore, engageable by the stop 93.

It is to be noted how, in this case, the elastic means 7 are adapted to keep the first rotational constraint loose, i.e. to move the reference teeth 51 away from the contrast teeth 52 working, as a result, in opposition to an axial force pulling the teach 51 and 52 together.

!n addition, the first constraint 5 may have the reference teeth 51 made at the end of the cylindrical block 42 distal from the bottom 33a.

While the second rotational constraint 6 may have slots 63 made on a portion of the second cylinder 32, in addition to the additional cylinder 33, so as to allow the teeth 51 to position themselves both at the additional cylinder 33 in the stop configuration and, at least partially, at the second cylinder 32 in the mobile configuration.

The mechanical hinge 1 may be applied, for example, to a door or window 10, The door or window 10 comprises a first element 1 1 preferably defining a through opening and identifiable, for example, in a fixed frame, a wall; a second element 12 identifiable, for example, in a panel or a door; and at least one mechanical hinge 1 adapted to rotate the second mobile element 12 with respect to the first mobile element 1 1 defining at least one closed position in which the second element 1 1 superposes the opening and at least one open position in which the second element 12 is rotationally integral with the first element 1 1 and away from the opening.

In particular, the door or window 10 may comprise a first element 1 1 ; a second element 12; a single mechanical hinge 1 ; and one or more mechanical hinges of a known type.

Said hinges of a known type described above consist of a first butt hinge which can be constrained to the first element 1 1 ; a second butt hinge which can be constrained to the second element 12; and a flap hinge hinging the elements 1 1 and 12 to each other so as to define an idle axis of rotation substantially coinciding with the axis 1 a.

The functioning of a mechanical hinge, described above in a structural sense, is as follows.

Initially, the mechanical hinge 1 is in a stop configuration (Fig. 2) and prevents the mutual rotation of the elements 1 1 and 12 and the door or window 10 for example, is in the closed position.

The operator, when he decides to move the window or door 10 into an open position, acts on the mechanical hinge 1 releasing at least one of the rotational constraints 5 or 6, preferably the first constraint 5 only, and allowing a mutual rotation of the elements 1 1 and 12.

To do this, the operator presses the portion of button 41 protruding from the second cylinder 32 so that the pin 4, guided by the second constraint 6, moves axially moving closer to the bottom 33a.

Said axial sliding of the pin 4 compresses the elastic means 7 and, above ail, distances the reference teeth 51 from the contrast teeth 52 disengaging the reference surfaces from the contrast surfaces and thereby loosening the first rotational constraint 5 and bringing the mechanical hinge 1 into the mobile configuration (Fig. 1 ).

Now the first binding unit 2 and, thus, the first element 1 1 are rotationaily idle/mobile with respect to the pin 4 and, thus to the second binding unit 3 and the second element 12.

In addition, the movement of the pin 4 superposes the insert 82 over the cavity 81 which thus enters the cavity 81 blocking the axial sliding of the pin 4 with respect to the units 2 and 3 and, therefore, keeping the hinge 1 in the mobile configuration.

Once the desired position has been reached, the operator disengages the insert

82 from the cavity 81 releasing the axial sliding of the pin 4 with respect to the units 2 and 3 and thus allowing the hinge 1 to return to the stop configuration.

!n fact, the disengagement of the insert 82 from the cavity 81 makes the pin 4 axially idle and thus allows the elastic means 7 to return the mechanical hinge 1 to the stop configuration.

!n particular, the elastic means 7 press on the pin 4 making it slide axially until the slider 62 reaches the end of the guide stroke 61 distal from the bottom 33a.

Said sliding of the pin 4 pulls together the teeth 51 and 52 and, most importantly, places the reference surfaces in contact with the contrast surfaces in a direction tangential to the axis of rotation 1 a blocking a reciprocal rotation of the units 2 and 3 and, thus, of the elements 1 1 and 12.

The invention achieves important advantages.

A first important advantage is that the mechanical hinge 1 , is able to selectively activate or loosen one of the rotational constraints 5 and 6 and thus allow or prevent the mutual rotation of the elements 1 1 and 12. It is therefore possible to keep the door or similar in a fixed position even in the presence of external forces such as wind or the like, or, choose to move said door freely.

Another advantage is that the door or window 10 or other similar structure with the mechanical hinge 1 is able to block the rotation between the elements 1 1 and 12 without using stops or other clamping devices. It is therefore more compact and aesthetically more attractive,

A further advantage is that it is possible to change the configuration of the mechanical hinge 1 simply by acting manually on the pin 4 without using screwdrivers or other tools.

One important advantage is obtainable by tilting one or both contrast surfaces defined by each contrast tooth 52.

In fact, this particular solution allows you to block, in one direction or both directions, the substantially idle rotation, between the elements 1 1 and 12 and, then, to allow such relative rotation merely by forcing a mutual sliding between the contrast surfaces defined by each contrast tooth 52 and the reference surfaces of the reference teeth 51.

Another advantage which may be obtained by tilting the contrast surfaces 52 with respect to the axis 1 a and to the reference surfaces of the reference teeth 51 , is that the operator, forcing the mechanical hinge 1 and, specifically, a relative rotation between the units 2 and 3, determines a discrete rotation and, in particular, preferably at steps of a substantially constant breadth between the elements 1 1 and 12.

This advantage is determined by the fact that the operator, forcing a reciprocal rotation between the binding units 2 and 3, causes the reference tooth 51 to slide along the contrast surface of the tooth 52 causing said mutual rotation of the units 2 and 3. The reference tooth 51 , once it has reached the top of said contrast surface (i.e. the point at maximum distance from the bottom 33a), goes past the tooth 52 and presents itself at the bottom of the contrast surface of the next tooth 52 making a small jump along the rotation axis 1 a defining, in conclusion, an stepped advancement for the hinge 1 .

It is to be noted how said step could determine, in relation to the first binding unit 2, an axial shift of the pin 4 and, optionally, of the second unit 3. Such axial displacement is avoided in the case in which, as described above, the contrast teeth 52 are made on a ring which being integrally rotationally constrained to the first cylinder 22 and axiaily adjustable by a spring in relation thereto, moves downwards absorbing said axial shift.

An added bonus is determined by the fact that, unlike the known catches, the hinge 1 not only makes it possible to lock a door/window in a position of maximum opening or closing but also in any intermediate position.

In fact, thanks to the presence of several teeth 51 and 52, the mechanical hinge 1 is able to rotationally lock the elements 1 1 and 12 regardless of their separation by simply changing the pairs of teeth 51 and 52 mutually engaged.

Another advantage of no less importance is that the hinge 1 , being hinged between the elements 1 1 and 12 is extremely simple to use and, in particular, does not require the operator to lean dangerously out.

Further advantages of no less importance are to be identified in that the mechanical hinge 1 makes the known catches superfluous and does not require any changes to the window or door 10, is easy to apply even to windows and doors already in use.

Variations may be made to the invention without departing from the scope of the inventive concept described in the independent claims and in the relative technical equivalents. In said sphere ail the details may be replaced with equivalent elements and the materials, shapes and dimensions may be as desired.

In a first variant the pin 4 may be composed of several mutually assembled elements in order to make the fitting of the hinge 1 easier.

For example, the pin 4 may comprise the button 41 and the cylindrical block 42 made in two separate parts to be constrained, preferably integrally, to each other. Said constraint between the button 41 and cylindrical block 42 is achievable, for example, by providing a cylindrical block 42 provided with a housing 421 which faces the button 41 and a pin 4 comprising a T cylinder adapted to engage in the housing through a hole 414 made on the button 41 so as to clamp the button 41 and cylinder block 42 to each other.

!n addition, the button 41 may comprise two separate pieces to be constrained, preferably integrally, to each other. For example, it may comprise a concave body 415 and a closing body 416 suitable to be constrained, for example by means of a threaded coupling to the concave body 415.

It is to be noted how said hole 414 may be made on the concave body 415.

Additionally, the insert 81 may be made on a separate element with respect to the concave body 415 and closure body 416 and be adapted to be interposed between said bodies 415 and 416 so as to be integrally, constrained, appropriately by clamping, to them when the bodies 415 and 416 are mutually engaged,

!n another variant (Figs. 10a, 10b, 10c, 1 1 a, 1 1 b and 1 1 c) the at least one first interlocking element may not be integral with the block 42 and, preferably, comprises at least one ball 57 and, in particular, several balls 57 preferably having the same diameter and suitably roughly equally angularly spaced. Said balls 57 may be four in number.

!n this case the at least one second interlocking element may comprise the at least one contrast tooth 52 described above.

In this case, the at least one slot 63 is substantially counter-shaped to the balls 57 so as to allow them to slide, preferably almost exclusively, perpendicular to the axis of rotation 1 a so that in the at least one stop configuration the bails 57 protrude, through the slots 63, from the second binding unit 3 and, specifically, of the additional cylinder 33 by engaging the at least one contrast tooth 52 and, in the at least one mobile configuration, the balls 57 protrude to a lesser extent from the slots 63 disengaging from the at least one contrast tooth 52,

To this end, the pin 4 and, specifically, the cylindrical block 42 may comprise a throat 43 made at the end proximal to the bottom 33a and adapted to at least partially house the balls 57 in the at least one mobile configuration.

In this case, the pin 4 is adapted to translate along the rotation axis 1 a so as to reciprocally move, preferably in a radial direction, the interlocking elements, namely the balls 57 and the at least one contrast tooth 52. Consequently, the axial translation of the pin 4 selectively defines the stop configuration radially drawing together and mutually engaging the balls 57 and the at least one contrast tooth 52 and the mobile configuration by radially distancing and, thereby mutually disengaging the bails 57 and the at least one contrast tooth 52,

Specifically, when the pin 4 slides axially to bring the hinge 1 into the stop configuration (Fig. 12a), the throat 43 is moved away from the slots 63. As a result, the balls 57, being engaged to the slots 63, cannot slide axiaiiy and, thus, protrude from the throat 43. As a result, the balls 57 go to rest on a portion of the cylindrical block 42 which, having a larger diameter than the throat 43, increases the portion of the bails 57 protruding from the slots 63. By virtue of this increase the balls 57 engage the contrast teeth 52.

Preferably, at least the portion of the cylindrical block 42 on which the balls slide 57 is made of elastomer so as to deform elasticaliy, decreasing its diameter. This reduction in diameter results in a smaller portion of bail 57 protruding from the slots 63 and, therefore, in a possible disengagement thereof from the contrast teeth 52.

Specifically, when the pin 4 slides axially to reach the mobile configuration (Fig. 12b), the throat 43 is moved towards the slots 63. As a result, the balls 57, being engaged in the slots 63, move back into the throat 43 disengaging from the contrast teeth 52.

It is to be noted how, in the case of the first interlocking elements comprising at least one ball 57, the at least one stop configuration may be of the stable type in a direction of rotation and, thus prevent the mutual rotation between the pin 4 and the first binding unit 2 in said direction of rotation thanks to the contrast teeth 52 each of which having at least one contrast surface for the bails 57 substantially parallel to the axis of rotation 1 a.

While, again in the case of the first interlocking elements comprising at least one ball 57, the at least one stop configuration may be of the stable type in both directions of rotation and, thus prevent the mutual rotation between the pin 4 and the first binding unit 2 in both directions of rotation thanks to the contrast teeth 52 each of which having two contrast surfaces for the balls 57 roughly parallel to the axis of rotation 1 a. Preferably, the angular distance between the contrast surfaces of adjacent contrast teeth 52 is roughly equal to the dimensions of the portion of the balls 57 available between said adjacent contrast teeth 52.