DESCRIPTION

Field of Invention

The present invention is generally applicable to the technical field of the closing or checking hinges, and it particularly relates to a hinge for the rotatable movement of a door, a shutter or the like.

Background of the Invention

Closing hinge are known including a box-shaped hinge body and a pivot reciprocally coupled to allow the rotation of a closing element, such as a door, a shutter or the like, between a closed position and an open position.

Generally, these hinges include a box-shaped hinge body and a pivot reciprocally coupled to allow the rotation of the closing element between the closed and open position.

These known hinges include a working chamber within the box-shaped hinge body which slidably seats a plunger element.

Examples of these known hinges are known from documents EP0756663, US5867869 and EP2148033.

These hinges can be improved. In fact, in case of sudden closure of the door, there is the danger that the same door impacts against the frame which supports it, thus becoming damaged.

Summary of the invention

Object of the present invention is to at least partially overcome the above mentioned drawbacks, by providing a hinge of high functionality and low cost.

Another object of the invention is to provide a hinge which allows to check the closing element when closing or opening.

Another object of the present invention is to provide a hinge which allows to dampen the shock of the turning movement of the closing element in proximity of the closing and/or opening position.

Another object of the invention is to provide a space-saving hinge.

Another object is to provide a hinge that ensures the automatic closing of the closing element from the position of open door.

Another object is to provide a hinge that is able to maintain over time the exact closed position.

Another object is to provide an extremely safe hinge.

Another object is to provide a hinge that is extremely easy to install.

Such objects, and others that will appear more clearly hereinafter, are fulfilled by a hinge according to what is herein described, claimed and / or shown.

Advantageous embodiments of the invention are defined in according to the appended claims.

Brief description of the drawings

Further features and advantages of the invention will become more apparent by reading the detailed description of some preferred but not exclusive embodiments of a hinge 1, shown as non-limiting example with the help of the annexed figures, wherein:

FIGs. la, lb and lc are side section views of an embodiment of the hinge 1 respectively in the open position, intermediate position in proximity to the closed position and in the closed position;

FIGs. 2a, 2b and 2c are side section views of another embodiment of the hinge 1, respectively in the open position, in an intermediate position in proximity to the closed position and in the closed position;

FIGs. 3a, 3b and 3c are side section views of another embodiment of the hinge 1 respectively in the open position, in an intermediate position in proximity to the closed position and in the closed position;

FIGs. 4a, 4b and 4c are side section views of another embodiment of the hinge 1 respectively in the open position, in an intermediate position in proximity to the closed position and in the closed position;

FIGs. 5a, 5b and 5c are side section views of another embodiment of the hinge 1 respectively in the open position, in an intermediate position in proximity to the closed position and in the closed position;

FIG. 6 is a section view of a preferred but not exclusive embodiment of the adjusting element 110.

Detailed description of some preferred embodiments

With reference to the above mentioned figures, the hinge 1 can be advantageously used for the controlled rotatable movement of at least one closing element, such as a door, a shutter or the like, which may be, in a per se known way, anchored to a stationary support structure, such as a wall, a floor, a frame or the like.

As a non-limiting example, the hinge 1 may be used for glass doors, interior doors made of wood, aluminium or PVC, shower doors or refrigerator doors.

As per se known, in the annexed figures neither the closing element nor the stationary support structure are shown. It is intended that both elements are not part of the invention claimed in the appended claims.

Preferably, the hinge 1 can be anchored to the stationary support structure in any way and lies above the floor level underlying the closing element. In other words, the hinge 1 is preferably not configured as a traditional floor door closer, of the type insertable in the floor through break-in works.

In a preferred but not exclusive embodiment, the hinge 1 may include the box- shaped hinge body 10 which may be anchored to one of the stationary support structure and the closing element and a pivot 20 which may be anchored to the other of the stationary support structure and the closing element.

However, it is understood that the hinge 1 may also be free of the pivot 20, as taught for example in the international application PCT/IB2015/052183 on behalf of the same Applicant, which is referred to for consultation. In such case, the operational connection between the movable part and the fixed one of the hinge is ensured by a group of levers.

In all embodiments shown in the annexed figures, the box-shaped hinge body 10 may be anchored to the stationary support structure, while the pivot 20 may be anchored to the closing element. Therefore, the box-shaped hinge body 10 is fixed, while the pivot 20 is rotatable.

However, it is understood that the box-shaped hinge body 10 may be anchored to the closing element, while the pivot 20 may still be anchored to the stationary support structure without exceeding the scope of protection of the annexed claims.

Suitably, the pivot 20 and the box-shaped hinge body 10 may be reciprocally coupled in order to rotate around the axis X, which, for example, may be substantially vertical.

Advantageously, the axis X can define the rotation axis of the closing element.

The hinge 1 may also include an operating chamber 13 defining a axis Y, which may be substantially perpendicular to the axis X, for example substantially horizontal. Within the operating chamber 13, which may be inside the box-shaped hinge body 10, a plunger element 50 may slide along the axis Y, on which counteracting elastic means 30 can operate.

In such a way, the plunger element 50 may slide along the axis Y between one end- stroke position, corresponding to one of the opening position and the closing position of the movable element 10, and a second end-stroke position, corresponding to the other position between the opening position and the closing position of the movable element 10.

Suitably, the operating chamber 13 may include a bottom wall 14 so that in the first end-stroke position, the plunger element 50 may be in a position proximal to the bottom wall 14, while in the second end-stroke position the same plunger element 50 may be in a distal position from the bottom wall 14.

In the embodiments shown in the figures, provided just as non-limiting illustration of the invention, the proximal position may correspond to the closed position of the closing element, while the distal position may correspond to the open position of the opening element.

On the other hand, the proximal position may correspond to the maximum elongation of the counteracting elastic means 30, while the distal position may correspond to the maximum compression of the same.

On the basis of the configuration of the counteracting elastic means 30, the hinge 1 may be a closing hinge or a checking hinge.

In fact, the counteracting elastic means 30 may include one or more thrust springs, used for leading back the closing element in the closed position from the open position or, conversely, a restore spring, used for restoring the initial position of the plunger element 50, but not used for leading back the closing element in the closed position from the open one or conversely.

In a preferred but not exclusive embodiment, the plunger element 50 may include a cylindrical body 55, preferably airtight inserted in the operating chamber 13.

The pivot 20 and the plunger element 50 may each other be engaged so that the sliding of the latter along the axis Y between the proximal and distal positions corresponds to the rotation of the former around the axis X and, conversely, the rotation of the former around the axis X corresponds to the sliding of the second along the axis Y between the proximal and distal positions. Such mutual engagement may be accomplished through known movement transmission means, for example through a shaft 53 as better explained hereinafter.

For example, the pivot 20 can include cam means 20' rotating around the axis X in order to move the plunger element 50 between the distal and proximal positions.

On the other hand, cam follower means 53" can be provided, interacting with the cam means 20' and integrally coupled with the plunger element 50, for example through the shaft 53, in order to slide along the axis Y between the distal and proximal positions, as taught in the international patent application PCT/2015/052792.

Suitably, the counteracting elastic means 30 can operate on the plunger element 50 in order to lead it back to from the proximal position to the distal one.

According to a different embodiment, not represented in the figures, the shaft 53 may be not connected to the cam means 20' and /or to the cam follower means 53' and, more in general, to the transmission means of the hinge movement.

In a preferred but not exclusive embodiment, the shaft 53 may be connected to the cylindrical body 55 through threading and counterthreading, as taught in the international application PCT/IB2015/052183, on behalf of the applicant herself. In particular, the shaft 53 may be telescopically coupled with the abutment surface 14, in order to move jointly with the cylindrical body 55.

In another embodiment, the mechanical connection between the cylindrical body 55 and the shaft 53 may occur in agreement with the teaching of the international application PCT/IB2012/051006, on behalf of the applicant herself, to which is referred for consultation.

The hinge 1 may also comprise damping means 40 for the reduction of the rotation speed of the movable element 10 when the plunger element 50 is in proximity of at least one of the first and the second end-stroke positions. Preferably, such damping means 40 reduce the speed of the movable element 10 used for the closure of the closing element.

In particular, depending on the configuration of such damping means 40, as better explained hereinafter, the hinge 1 may have a damping action of the exclusively mechanical type, exclusively hydraulic type or hydraulic and mechanical type.

In case of mechanical hinge, in order to contrast the action of the plunger element 50, the damping elements 40 may include counteracting elastic means 41 interposed between the plunger element 50 and the bottom wall 14. In such case, the latter may therefore define a abutment surface for the same counteracting elastic means 41.

In particular, the counteracting elastic means 41 may have a first end 42 towards the plunger element 50 and a second end 42' towards the bottom wall 14 and intended to go in beat against the same. On the other hand, the plunger element 50 may have a front portion 51 intended to go in beat with the end 42 of the counteracting elastic means 41.

According to an aspect of the invention, the counteracting elastic means 41 may pass from an unloaded position in which the first end 42 thereof ranges from the front position 51 of the plunger element 50, shown for example in FIG. la, to a position of load start in which the latter is in contact with the first for loading the same means, shown for example in FIG. lb.

From such position of load start, the counteracting elastic means 41, under the thrust of the plunger element 50 promoted by the action of the elastic means 30, may pass from the position of load start to a position of load end, shown for example in FIG. lc, in which they are completely loaded in order to mechanically dampen the speed of the rotation of the movable element 10.

For example, the elastic means 41 may include a spring, representing a first end 42 susceptible to interact with the front portion 51 and the opposite end 42' in beat with the bottom wall 14.

More in particular, the counteracting elastic means 41 may contrast the thrust of the plunger means 50 only for a section of its stroke. For example, the plunger element 50 may slide along a first section between the second end-stroke position, shown for example in FIG la, and an intermediate position, shown for example in FIG. lb, corresponding to the position of load start of the contrast means 41 without that the latter operate on the plunger element 50.

The latter, furthermore, may slide along a second section between the intermediate position here above and the first end-stroke position of the plunger element 50, shown for example in FIG. lc, corresponding to the position of load end of the counteracting elastic means 41, along which the plunger element 50 itself undergoes the action of the counteracting elastic means 41.

In other words, when the plunger element 50 advances from the intermediate position to the first end stroke position, this may correspond to the compression of the counteracting elastic means 41 which may be configured in order to operate a contrast action on the plunger element 50, the more compressed they are, the stronger the contrast action is. In such a way, the strongest contrast action is in correspondence with the first end- stroke position of the plunger element 50 to which the maximum compression of the elastic means 41 may correspond.

Thanks to such features, it can mechanically checked, the closing or the opening of the closing element.

By suitably choosing the features of the counteracting elastic means 41, it is possible to obtain a more or less intense mechanical damping action.

For example, the counteracting elastic means 41 may include at least a compression spring, for example a spiral spring.

In particular, the spring 41 may also be put on the shaft 53.

Suitably, in order to house the spring 41, the cylindrical body 55 may have an elongated adjunct 55"extending itself coaxially to the shaft 53 towards the abutment surface 14 in order to define between the same a ring-shaped seat 5 . The latter may be used to house the counteracting elastic means 41 when the latter are in start load position, in order to guide the compression.

Suitably, the plunger element 50 may also include a abutment surface 52 faced towards a corresponding abutment surface 14' of the operating chamber 13 and aimed at interacting with the latter in order to define the end-stroke of the former. In particular, the surfaces 52, 14' may be in mutual beat when the plunger element 50 is in the first end- stroke position and they may be mutually spaced when the plunger element 50 is in the second end-stroke position.

In this way, advantageously, also in case that the plunger element 50 is pushed with high force towards the bottom wall 14, the surfaces 52, 14' can be in mutual beat in order to preserve the counteracting means elastic 41.

Besides this, such features allow to the hinge 1 to keep over time its exact closing position.

In case of hydraulic hinge, the operating chamber 13 may include a working fluid, generally oil, acting on the plunger element 50 in order to contrast its action, checking hydraulically in this way the closure and/or opening of the closing element. It is understood that also just one portion 15 of the operating chamber 13 can include a working fluid without departing in this way from the scope of protection of the annexed claims.

In particular, the plunger element 50 can divide the operating chamber 13 in a first and second adjustable-volume spaces 18, 19. The latter, each other fluidically communicating, may be preferably adjacent.

Advantageously, the first and second adjustable-volume spaces 18, 19 can be configured in order to have, at the closed position of the closing element, the maximum and minimum volume, respectively. For such purpose, the counteracting elastic means 30 can be placed in the first space 18.

Suitably, the cylindrical body 55 can be airtight inserted in the operating chamber 13 so that the same can be the separation element of the portion 15 in the first and second adjustable-volume spaces 18, 19.

In the present document, with the definition "airtight inserted cylindrical body" and related ones it is understood that the cylindrical body 55 is inserted in the operating chamber 13 with minimum play, so that it is allowed to slide within the same, but preventing the working fluid from leaking through the cavity between the side surface of the cylindrical body itself 55' and the internal surface of the operating chamber 13.

In a preferred but not-exclusive embodiment, it can be foreseen at least a first hydraulic circuit 60 for allowing the passage of the working fluid between the first and second compartments 18, 19 upon the other of the opening and closure of at least one closing element, at least one second hydraulic circuit 70 can be foreseen.

According to a particular embodiment not represented in the figures, the hydraulic circuit 60 and the hydraulic circuit 70 can substantially coincide.

For example, the oil may pass from the first compartment 18 to the second compartment 19 during the opening of the closing element through the hydraulic circuit 70 and may pass from the second compartment 19 to the first compartment 18 during the closure of the closing element through the same hydraulic circuit 70.

On the other hand, in a preferred but not-exclusive embodiment, shown in the annexed figures, at the opening of the closing element the working fluid passes from the first compartment 18 to the second compartment 19 through the first hydraulic circuit 70, while at the closure of the closing element the working fluid passes from the second compartment 19 to the first compartment 18 through the second hydraulic circuit 70.

However, it is understood that at the opening of the closing element the working fluid may pass from the first compartment 18 to the second compartment 19 through the second hydraulic circuit 70, while at the closure of the closing element the working fluid may pass from the second compartment 19 to the first compartment 18 through the first hydraulic circuit 60 without departing from the scope of protection of the annexed claims.

It may also be foreseen that at the opening of the closing element the working fluid may pass from the second compartment 19 to the first compartment 18 through one of the second hydraulic circuit 70 and the first hydraulic circuit 60, while at the closure of the closing element the working fluid may pass from the first compartment 18 to the second compartment 19 through the other of the second hydraulic circuit 70 and the first hydraulic circuit 60, without departing from the protection scope defined in the annexed claims.

In particular, both the first and second hydraulic circuits 60, 70 may be configured so that to predetermine the quantity of oil passing from the first compartment 18 to the second compartment 19 and conversely in order to operate a contrast action on the plunger element 50. In particular, due to this configuration, it can be predetermined a maximum movement speed of the plunger element 50 and, therefore, a rotation speed of the movable element 10.

According to an aspect of the invention, the hydraulic circuit 60 can at least include a first passage 58 in order to put in fluidic communication the first and second compartments 18, 19, so that at the opening of the closing element there is passage of the working fluid from the compartment 18 to the compartment 19.

However, it is understood that the reverse movement may take place, that is the passage of the working fluid from compartment 19 to compartment 18, and/or the passage may take place at the closing of the closure element, without departing from the protection scope of the annexed claims.

The hydraulic circuit 60 can be manufactured according to the teaching of the international patent application PCT/IB2014/063556 or the international patent application PCT/IB2015/052183, to which is referred for consultation.

In particular, the hydraulic circuit 60 can comprise an operating element 56 cooperating with the cylindrical body 55 for defining a valve seat 57 inside which there is a lock 57'.

The shaft 53, the cylindrical body 55 and the operating element 56 each may comprise a respective hole, therebetween fluidically connected in order to define the passage 58.

The valve seat 57 and the respective lock 57', besides this, may be predisposed in correspondence with the passage 58 in order to define a non-return valve. In particular, it selectively avoids the passage of the working fluid through the same passage 58 upon one of the opening or the closure of the closing element, by forcing in this way the passage of the working fluid through the second hydraulic circuit 70.

As shown in the annexed figures, the non-return valve may be configured in order to allow selectively the passage of the working fluid from the first compartment 18 to the second compartment through the passage 58 upon the opening of the closing element, and for avoiding it upon the closure.

In a preferred but not exclusive embodiment, the non-return valve may foresee the lock forced in closure by a small spring, as taught in the international application PCT/IB2015/052183, on behalf of the applicant herself.

According to an aspect of the invention, the damping means 40 may comprise at least one or more channels having a predetermined section in order to check the quantity of oil passing through.

In a preferred but not exclusive embodiment of the hinge, shown for example in the FIG. from la to lc, the channel may be single, since also counteracting elastic means 41 are foreseen.

On the other hand, as shown for example in the FIGS, from 5a to 5c, there may be a couple of damping channels cooperating with the counteracting elastic means 41.

In such a way, the damping action of the damping means 40 is both mechanical and hydraulic.

In other preferred but not exclusive embodiments of the invention, shown for example in the FIGs. from 2a to 4c, the damping means 40 may foresee two channels without any counteracting elastic means.

In this way, the damping action of the damping means 40 is exclusively hydraulic. In any case, the second hydraulic circuit 70 may comprise at least one channel 43. The latter may have a first inlet 44 in the second compartment 19 and a first outlet 44' in the first compartment 18.

In particular, the first inlet 44 and the first outlet 44' may be fluidically decoupled from the plunger element 50 for the whole stroke thereof.

According to a particular embodiment, the channel 43 may comprise a helical groove 47 formed on the inner surface 15' of the operating chamber 13. In particular, the outer surface 55' of the cylindrical body 55 may be aimed at interacting with the inner surface 15' and with the helical groove 47 in order to define a helical channel.

In such case, the quantity of the working fluid passing from a compartment to the other is fixed and predetermined, depending from the dimensions of the groove 47.

As a possibility, according to a different embodiment, the channel 43 may be realized through the hinge body 10 outside the working chamber 13. In such case, the channel 43 may comprise one element 110 for adjusting the flow of the working fluid inside thereof, in order to regulate the flow of the passing fluid through the channel 43 and so the extent of the hydraulic damping of the rotation speed of the movable element 10.

According to a preferred but not exclusive embodiment shown in the FIGs. la, lb and lc, the hinge 1 may comprise the counteracting elastic means 41, the hydraulic circuit 60 and hydraulic circuit 70. In particular, the latter may comprise at least one channel 43 having one or more characteristics described above comprising one element 110 for adjusting.

In this way, the counteracting action on the plunger element 50 practiced by the damping means 40 may be at the same time of mechanical and hydraulic type in order to exploit the synergic effect of the two actions and to obtain a more effective damping.

The element 110 for adjusting may comprise an adjusting screw 111 of the known type for adjusting the passage section of the channel 43, in order to regulate the return speed of the working fluid.

For example, the regulation screw may comprise one first frustoconical operational end in correspondence of the channel 43 and one second operational end accessible from outside by a user for adjusting the hydraulic damping of the rotation speed of the movable element 10.

According to a preferred but not exclusive aspect of the invention, the element 110 for adjusting may comprise one adjusting screw 115, which may be realized according to the teaching of the international patent application PCT/IB2014/063556, on behalf of the applicant herself.

In particular, as shown in the FIG. 6, the special adjusting screw 115 may have a first upper threaded end 116' which may be screwed in one corresponding first upper counterthreaded connecting portion 11' of the hinge body 10 and one second lower end 116" slidably inserted in one corresponding second lower guide portion 11" of the hinge body 10.

For this purpose, the second lower end 116" of the special adjusting element 115 may have at least one portion 117', 117" of the outer surface 118 placed in beat against at least one corresponding portion 12', 12" of the inner surface 12 of the second lower guide portion 11' of the hinge body 10.

In such a way, the vertical slide of the special adjusting element 115 is always guided, annulling totally the danger of misalignment thereof.

Advantageously, the second lower end 116" may include one hollow seat 119 for housing one substantially frustoconical seat 120 coaxially inserted therein.

The special adjusting element 115 may include a first opening 121 for the inlet/outlet of the working fluid, placed preferably in correspondence with one substantially central portion thereof.

Suitably, the inner surface 122 of the hollow seat 119 may be towards the external surface 123 of the substantially frustoconical element 120 for defining an interspace fluidically connected to the first opening 121 and to the hydraulic circuit 70, and interposed therebetween.

In order to adjust the flow of the working fluid, the interspace may have a variable volume.

For such purpose, the hollow seat 12 may have a substantially cylindrical shape, while the substantially frustoconical element 120 may have the end with the smaller diameter towards the first opening 121.

In such a way, the reciprocal distancing/approaching of the substantially frustoconical element 120 and of the special adjusting element 115, with the consequent variation of the interspace volume, corresponds to the screwing/unscrewing of the first upper end 116' of the special adjusting element 115 from/in the first upper connection portion 1 of the hinge body 10.

This allows to adjust the flow of the working fluid through the hydraulic circuit 70 in a simple and rapid way, with the maximum guarantee of repeatability over time of the closing element performance during the closing and/or opening movement.

The special adjusting element 115 allows therefore to adjust the flow of the working fluid through the hydraulic circuit 70, and more in particular in the channel 43, in a simple and rapid way, with the maximum guarantee of repeatability over time of the closing element performance during the closing and/or opening movement.

According to a different embodiment, the damping elements 40 may include, in addition to channel 43, also one second channel 45, which can be provided with another inlet 46 in one of the first 18 and the second compartment 19 and one second outlet 46' in one of the first 18 and the second compartment 19.

The first 43 and the second channel 45 may be fluidically independent from each other. In particular, they can fluidically connected only through the variable volume compartments 18, 19.

According to a preferred but not exclusive embodiment, one of the first and the second inlet 44, 46, for example inlet 44, can be fluidically decoupled from the plunger element 50 for the whole stroke thereof in order to let the oil drain away through the inlet 44 itself. On the other hand, the other of the first and the second inlet 44, 46, for example inlet 46, can be fluidically decoupled from the plunger element 50 for a first section of the stroke of the plunger element in order to let the oil drain away and fluidically connected to the plunger element 50 for a second section of the stroke thereof in order to avoiding the outflow of the oil.

In particular, the outer surface 55' of the cylindrical body 55 can be aimed at capping one of the inlets 44, 46, for example inlet 46, to create the coupling of the piston element 50 with the latter and, therefore, in order to avoid the outflow of the oil from the compartment 19 through the same inlet 46.

More specifically, as shown for example in FIGs 2a, 2b and 2c, when the plunger element 50 is in the distal position from the bottom wall 14 of the operating chamber 13 (FIG. 2a), both inlets 44, 46 of channels 43, 45 may be decoupled from the plunger element 50, while when the plunger element 50 is in the end-stroke position proximal to the bottom wall 14 (FIG. 2c), inlet 46 of channel 45 may be coupled with the plunger element 50 so that the oil does not drain away through the channel 45 itself.

In other words, the oil may drain away through channels 43, 45 for a first section of the stroke of the plunger element 50, namely from the second end-stroke position (FIG. 2a) to an intermediate position (FIG. 2b), and through only one of the two 43, 45 for a second section of its stroke, namely from the intermediate position (FIG. 2b) to the first end-stroke position (FIG. 2c).

In this way, the counteraction of the damping elements 40 can have a different intensity upon the advancement of the plunger element 50 and, more specifically, the counteraction can be higher when the plunger element 50 is in the second section and can be lower when it is in the first section of its stroke, by damping the counter-action itself.

Thanks to this feature, the plunger element 50, and therefore the closing element, can be better braked in the closing phase in proximity to the first end-stroke position of the plunger element itself 50, corresponding, for example, to the closed position of the closing element.

According to a particular aspect of the invention, when the plunger element 50 is in the intermediate position, the pivot 20 may be rotated by about 20° with respect to the Axis X, preferably about 18°.

The second channel 45 may have one or several features of one of the above- described embodiments of channel 43. In other words, the first and second channel 43, 45 may be substantially equal or may have different features.

For example, both channels 43, 45 can have a helical shape. In particular, according to the embodiments shown in FIGs. 3a, 3b and 3c, channels 43, 45 may comprise one respective helical hollow 47, 47', which may have a substantially equal pitch, misaligned so that the two channels 43, 45 are fluidically independent from each other.

As a possibility, the helical hollows 47, 47' may have different depths so that the quantity of oil which drains away from the relevant channels 43, 45 may be different to obtain a counter-action of different entity on the plunger element 50 following its movement from the second to the first end-stroke position.

On the other hand, according to a different embodiment shown in FIGs. 4a, 4b and 4c, one of the two channels 43, 45 may comprise a helical hollow, while the other may be of known type.

According to another aspect of the invention, at least one of the channels 43, 45 may comprise an adjusting element 110 with one or more of the above-described features.

For example, as shown in the FIGS. 2a, 2b and 2c both channels 43, 45 may comprise a respective adjusting element 110 comprising one adjusting screw 111 for the flow of the oil.

On the other hand, according to a different embodiment shown in the FIGS. 5a, 5b and 5c, the channels 43, 45 may comprise, respectively, one first adjusting element 110 comprising the adjusting screw 111 and one second adjusting element 110 comprising the special adjusting element 115.

Even though not represented in the annexed figures, each of the channels 43, 45 may comprise one adjusting element 110, the latter may comprise the special regulation element 115.

From the above description, it is evident that the invention fulfils the intended objects.

The hinge according to the invention is susceptible of numerous modifications and variations all falling within the inventive concept expressed in the appended claims. All the details may be replaced with other technically equivalent elements, and the materials may be different according to requirements, without departing from the scope of the invention.

Although the hinge has been described with particular reference to the annexed figures, the reference numbers used in the description and in the claims are used to improve the intelligence of the invention and do not constitute any limitation to the scope of protection claimed.