Patent Description:
Closing hinges are known which comprise a box-shaped hinge body and a pivot reciprocally coupled to allow a closing element, such as a door, a shutter or the like, to rotate between an open position and a closed position.

Generally, these hinges include a hinge body and a pivot reciprocally coupled to allow the closing element to rotate between the open and the closed positions.

These known hinges further include a working chamber internal to the box-shaped hinge body that slidingly houses a plunger member.

Examples of said known hinges are known from documents <CIT>, <CIT> and <CIT>.

These hinges are susceptible to be improved, particularly with regard to their duration through time.

From <CIT> a hinge is known having all the features of the preamble of the independent claim <NUM>.

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

Another object of the invention is to provide a hinge having an extremely high duration through time.

Another object of the invention is to provide a low-bulkiness hinge.

Another object of the invention is to provide a hinge having high thrust force.

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

Another object of the invention is to provide a hinge capable to support even very heavy closing elements, without changing its behavior.

Another object of the invention is to provide a hinge having a minimum number of constituent parts.

Another object of the invention is to provide a hinge capable to maintain the exact closing position through time.

Another object of the invention is to provide an extremely safe hinge.

Another object of the invention is to provide a hinge extremely easy to install.

These objects, and others which will appear more clearly hereinafter, are fulfilled by a hinge in accordance with claim <NUM>.

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

Further features and advantages of the invention will appear more evident reading the detailed description of some preferred not-exclusive embodiments of a hinge <NUM>, which are shown as a non-limiting example with the help of the annexed drawings, wherein:.

With reference to the above figures, the hinge <NUM> is advantageously used for checking the rotatable movement of at least one closing element, such as a door, a shutter or the like, which can be anchored in a per se known manner to a stationary support structure, such as a wall, a floor, a frame or the like.

As non-limiting example, the hinge <NUM> may be used for glass doors, internal doors in wood, aluminum or PVC, shower shutters or cold room doors.

In the annexed figures the closing element and the stationary support structure have not been shown, as they are per se known. It is understood that both these elements are not part of the invention claimed in the appended claims.

Therefore, the hinge <NUM> comprises a box-shaped hinge body <NUM> anchorable to one of the stationary support structure and the closing element, and a pivot <NUM> anchorable to the other of the stationary support structure and the closing element.

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

However, it is understood that the box-shaped hinge body <NUM> may be anchored to the closing element, while the pivot <NUM> may be anchored to the stationary support structure without departing from the scope of the appended claims.

Suitably, the pivot <NUM> and the box-shaped hinge body <NUM> are reciprocally coupled to rotate around the axis X, which for example may be substantially vertical.

Advantageously, the axis X may also define the axis of rotation of the closing element.

The hinge <NUM> also includes a working chamber <NUM> defining an axis Y, which is substantially perpendicular to axis X, for example substantially horizontal. Within the working chamber <NUM>, which is internal to the box-shaped hinge body <NUM>, a plunger member <NUM> slides along the axis Y, whereon elastic counteracting means <NUM> may act.

In this way, the plunger member <NUM> slides along the axis Y between a position proximal to the bottom wall <NUM> of the working chamber <NUM> and a position distal from it. In the embodiments shown in the figures, provided for the sole purpose of illustration and not limiting of the invention, the proximal position may correspond to the position of closing element open, while the distal position may correspond to the position of closing element closed.

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

Depending on the configuration of the elastic counteracting means <NUM>, the hinge <NUM> may be a closing hinge or a checking hinge.

In fact, the elastic counteracting means <NUM> may include one or more thrust springs, that is susceptible to return the closing element in the closed position from the open one, or vice versa, or a return spring, susceptible to restore the original position of the plunger member <NUM> but not susceptible to return the closing element in the closed position from the open one, or vice versa.

In a preferred but not exclusive embodiment, the plunger member <NUM> may include a cylindrical body <NUM>, preferably sealingly inserted into the working chamber <NUM>.

The pivot <NUM> and the plunger member <NUM> may be mutually engaged so that the rotation of the first around the axis X corresponds to the sliding of the second along the axis Y between the proximal and the distal positions, and vice versa the sliding of the second along the axis Y between the proximal and the distal positions corresponds to the rotation of the first around the axis X.

To the object, the pivot <NUM> includes cam means <NUM> rotating around the axis X to return the plunger member <NUM> from the distal position to the proximal one.

On the other hand, cam follower means <NUM> are provided interacting with the cam means <NUM> and integrally coupled with the plunger member <NUM>, for example through the shaft <NUM>, to slide along the axis Y therewith between the proximal and the distal positions.

Suitably, the elastic counteracting means <NUM> may act on the plunger member <NUM> to return it from the proximal position to the distal one.

In a preferred but not exclusive embodiment, cam follower means <NUM> may include a rotatable element <NUM> rotating around an axis X' substantially parallel to the axis X and spaced apart thereto.

Advantageously, the rotatable element <NUM> may have a cylindrical shape. For example, it can be constituted of a wheel, which in its turn may provide a male member <NUM>' and a female member <NUM>" mutually overlapped and coupled. Due to this feature, the efforts resulting from the interaction with the cam means <NUM> are equally distributed between the male <NUM>' and female <NUM>" members, with an obvious benefit for the time duration of the hinge <NUM>.

Suitably, the wheel <NUM> may be rotatably housed in a seat of the end <NUM> of the shaft <NUM> to rotate around the axis X'.

To the object, the wheel <NUM> may have a central cylindrical portion <NUM> insertable into the seat <NUM> and two disk-shaped upper and lower portions <NUM>', <NUM>" of greater diameter than the central portion susceptible to come in contact engage with the cam means <NUM>.

Advantageously, the wheel <NUM> may rotate around the axis X' on bushings <NUM>, so as to minimize the friction.

The cam means <NUM> may include a first and a second abutment element <NUM>, <NUM> both susceptible to come into contact engage with the wheel <NUM>.

On the other hand, the wheel <NUM> may include a single disk-shaped portion without departing from the scope of the appended claims. It is understood, however, that the wheel <NUM> with the two overlapped disk-shaped portions ensures an optimum distribution of the efforts, and therefore in general an average life of the hinge <NUM> exceedingly high.

Advantageously, the first and the second abutment element <NUM>, <NUM> can both have at least one respective curved portion.

For example, in the embodiment shown in FIGs. from <NUM> to 3b, which does not fall within the scope of the present invention, they may be defined by a pair of cylindrical pins <NUM>, <NUM> defining respective axes X" and X‴ substantially parallel to the axis X and substantially perpendicular to the axis Y, which may be susceptible to selectively interact with the wheel <NUM>.

More particularly, the pins <NUM>, <NUM> may have respective side walls <NUM>, <NUM> susceptible to come into contact engage with the peripheral edge <NUM>', <NUM>" of the upper and lower portions <NUM>', <NUM>" of the wheel <NUM>.

On the other hand, in the embodiment of the present invention shown in FIGs. from <NUM> to 6b the first and the second abutment element <NUM>, <NUM> may be defined by at least an area of the respective convex curved portions of the ends <NUM>, <NUM> of the cam element <NUM> interposed between a concave portion <NUM>.

The areas of the convex curved portions of the ends <NUM>, <NUM> may be defined by one or more contact points with the peripheral edge <NUM>', <NUM>" of the upper and lower portions <NUM>', <NUM>" of the wheel <NUM>. On the other hand, the areas may be defined by a continuous portion more or less extended of the convex curved portions of the ends <NUM>, <NUM>.

Even in this case, the areas of the convex curved portions of the ends <NUM>, <NUM> may define respective axes X" and X‴ substantially parallel to the axis X and substantially perpendicular to the axis Y, and may be susceptible to come into contact engage with the peripheral edge <NUM>', <NUM>‴ of the upper and lower portions <NUM>', <NUM>" of the wheel <NUM>.

In this way, both upon the opening and the closing of the closing element, that is upon the rotation of the cam means <NUM> around the axis X, and in particular of the two abutment elements <NUM>, <NUM>, it corresponds to the rotation of the wheel <NUM> around the axis X', as well as to its translation along the axis Y.

More particularly, upon the opening and closing of the closing element, that is, upon the rotation of the pivot <NUM> around the axis X, the axes X" and X‴ eccentrically rotate with respect to the axis X itself between a rest position, shown for example in <FIG>, <FIG> and <FIG>, and defining the position of closing element closed, wherein the two axes X" and X‴ are spaced apart from the axis Y and equidistant thereto, and a working position, shown for example in <FIG>, <FIG> and <FIG>, and defining a position of closing element open, wherein the two axes X" and X‴ are aligned with the axis Y.

In the embodiments here shown the hinge <NUM> is configured so as that the closing element rotates between a closed position, shown for example in <FIG>, <FIG> and <FIG>, and two open positions opposite to each other with respect to the closed position, one of which is shown as an example in <FIG>, <FIG> and <FIG>.

From the figures it is evident that the wheel <NUM> is in contact engage with both the abutment elements <NUM>, <NUM> and steadily laid thereon when the closing element is in the closed position and is in selectively contact with only one of the abutment elements <NUM>, <NUM> when it is in each of the open positions.

At the same time, upon the opening and closing of the closing element, that is, upon the rotation of the pivot <NUM> around the axis X, it corresponds the translation of the axis X' defined by the wheel <NUM> along the axis Y between a position wherein the same axis X' is proximal to the axis X, shown for example in <FIG>, <FIG> and <FIG> and coincident with both the distal position of the plunger member <NUM> and with the position of the closing element closed, and a position distal from the same axis X, shown in <FIG>, <FIG> and <FIG> and coincident with both the proximal position of the plunger member <NUM> and with the position of the closing element open.

It is obvious that the rotation of the wheel <NUM> around the axis X' minimizes the friction between the parts in contact engage, that is essentially the same wheel <NUM> and the abutment elements <NUM>, <NUM>, so as to maximize the time duration of the hinge <NUM>.

The minimization of the friction between the parts in contact engage, in addition, also allow to maximize the thrust force of the elastic means <NUM>. As the latter, in fact, the hinge <NUM> develops a thrusting force much higher than that of the hinges of the prior art.

To further minimize the friction, the contact engage between the abutment elements <NUM>, <NUM> and the wheel <NUM> may occur in mutual tangency points P', P", P‴. This ensures that the contact occurs in a single point.

More particularly, the points P' and P" are the contact points between the abutment elements <NUM>, <NUM> and the wheel <NUM> in the position of closing element closed, as shown in <FIG> and <FIG>. On the other hand, the point P‴ is the contact point between the abutment element <NUM> and the wheel <NUM> in one of the positions of the closing element open, as shown in <FIG> and <FIG>.

It is understood that due to the rotation of the wheel <NUM> the point P‴ is different both from point P' and P".

It is understood that in the other position of the closing element open, opposite to that shown in <FIG>, the wheel <NUM> is in contact with the abutment element <NUM> in a further single contact point.

In a preferred but not exclusive embodiment, the abutment elements <NUM>, <NUM> may be mutually positioned so as the respective axes X" and X‴ define a plane π substantially parallel to the axes X and X' and substantially perpendicular to axis Y.

Suitably, also, the tangency points P', P" may define a plane π' that is also substantially parallel to the axis X and substantially perpendicular to the axis Y. The planes π and π' may be parallel to each other when the axis X' is in the proximal position, that is when the plunger member <NUM> is in distal position, as shown for example in <FIG> and <FIG>.

The hinge <NUM> may be mechanic or hydraulic.

In case of hydraulic hinge, the working chamber <NUM> may include a working fluid, generally oil, acting on the plunger member <NUM> to counteract the action, thus hydraulically checking the closing or opening movement of the closing element.

The cylindrical body <NUM> acts as separation element of the working chamber <NUM> into a first and a second variable volume compartment <NUM>, <NUM>. These latter, which are fluidly communicating with each other, are preferably adjacent.

Advantageously, the first variable volume compartment <NUM> and the second variable volume compartment <NUM> may be configured so as to have in correspondence with the closed position of the closing element respectively the maximum and the minimum volume. To the object, the elastic counteracting means <NUM> may be placed in the first compartment <NUM>.

Suitably, the cylindrical body <NUM> may be sealingly inserted in the working chamber <NUM>.

In the present text, with the expression "cylindrical body sealingly inserted" and derived it is meant that the cylindrical body <NUM> is inserted into the working chamber with minimum play, such as to allow it to slide therein but such as to prevent passages of the working fluid through the casing between the side surface of the cylindrical body and the inner surface of the working chamber.

In a preferred but not exclusive embodiment, the cylindrical body <NUM> may include at least one first passage <NUM> to allow the passage of the working fluid between the first and the second compartment <NUM>, <NUM> upon one of the opening or the closing of the at least one closing element.

To allow the passage of the working fluid between the first and the second compartment <NUM>, <NUM> upon one of the other between the opening or closing of the at least one closing element, a hydraulic circuit passing through the hinge body <NUM> may be provided.

In the preferred but not exclusive embodiments shown in the annexed figures, upon the opening of the closing element the working fluid passes from the first compartment <NUM> to the second compartment <NUM> through the opening <NUM>, while upon the closing of the closing element the working fluid passes from the second compartment <NUM> to the first compartment <NUM> through the hydraulic circuit.

It is understood, however, that upon the opening of the closing element the working fluid may pass from the first compartment <NUM> to the second compartment <NUM> through the hydraulic circuit, while upon the closing of the closing element the working fluid may pass from the second compartment <NUM> to the first compartment <NUM> through the opening <NUM> without departing from the scope defined by the appended claims.

It may also be provided that upon that opening of the closing element the working fluid may pass from the second compartment <NUM> to the first compartment <NUM> through one of the hydraulic circuit and the at least one opening <NUM>, whereas upon the closing of the closing element the working fluid may pass from the first compartment <NUM> to the second compartment <NUM> through the other of the hydraulic circuit and the at least one opening <NUM>, without departing from the scope defined by the appended claims.

It may also be provided an adjustment screw <NUM> to adjust the passage section of the hydraulic circuit, so as to regulate the return speed of the working fluid.

This allows to regulate the flow of the working fluid through the hydraulic circuit in a simple and rapid manner, with the maximum guarantee of constancy through time of the behavior of the closing element during the closing and / or opening movement.

More details on the particular configuration of the adjustment screw <NUM> are shown in the <CIT>, on behalf of the same Applicant, whereto reference is made for consultation.

Advantageously, the cylindrical body <NUM>, moreover, may include valve means, which can be constituted of a non-return valve <NUM>, interacting with the passing-through hole <NUM> to selectively prevent the passage of the working fluid therethrough upon the closing of the closing element, thus forcing the passage of the working fluid through the hydraulic circuit.

The non-return valve <NUM> may be further configured to selectively allow the passage of the working fluid through the passing-through hole <NUM> upon the opening of the closing element.

In a preferred but not exclusive embodiment, the non-return valve <NUM> may provide a stopper forced upon the closing by a small spring, as taught by the international application <CIT>, in the name of the same Applicant.

In a preferred but not exclusive embodiment, the shaft <NUM> may be connected to the cylindrical body <NUM> by a screw <NUM>.

More details on the configuration of these elements, and in particular regarding the configuration of the hole <NUM>, of the non-return valve <NUM> and of the mechanical connection between the cylindrical body <NUM>, the shaft <NUM> and the interface element <NUM>, are shown in the international application <CIT>, in the name of the same Applicant, whereto reference is made for consultation.

In a further preferred but not exclusive embodiment, the shaft <NUM> may be directly connected to the cylindrical body <NUM> through threading and counter-threading, as taught by the international application <CIT>, in the name of the same Applicant.

Thanks to these features, it is possible to effectively check the flow of the working fluid between the first and the second compartment <NUM>, <NUM> in both directions.

According to the invention, as shown for example in FIGs. from <NUM> to 6b, the pivot <NUM> consists of two half-portions <NUM>', <NUM>" assembled together.

To the object, means for coupling the same once assembled are provided, for instance a screw <NUM> and a pair of anti-rotation pins <NUM>', <NUM>". In this way, the two half-portions <NUM>', <NUM>" become mutually integral.

This allows to obtain cam element <NUM> of any form, and in particular the one shown in FIGs. from <NUM> to 6b. In this case, in fact, with an unitary pivot it would be extremely difficult to manufacture the concave portion <NUM> interposed between the convex curved portions of the ends <NUM>, <NUM>.

The pivot <NUM> constituted of the two half-portions <NUM>', <NUM>" results also more solid and long-lasting than the unitary pivot, as it allows a better distribution of the forces which develop during the interaction with the plunger member <NUM>.

In a preferred but not exclusive embodiment, shown for example in FIGs. from <NUM> to 6b, between the seat <NUM> of the hinge body <NUM> wherein the pivot <NUM> is inserted and the portion <NUM> of the latter facing thereto at least one bushing <NUM> may be interposed, made for example of polymeric material, for instance Teflon®. For example, the bushing <NUM> may be a bushing made of plastic material of high technology sold by IGUS.

The bushing <NUM> may include an outer surface <NUM>' reciprocally facing the substantially cylindrical seat <NUM> of the hinge body <NUM> and an inner surface <NUM>" reciprocally facing the portion <NUM> of the pivot <NUM>.

Advantageously, braking means acting on the areas <NUM>', <NUM>", <NUM>‴ of the outer surface <NUM>' of the bushing <NUM> may be provided to locally force the inner surface <NUM>' of the same bushing <NUM> against the portion <NUM> of the pivot <NUM>.

In a preferred but not exclusive embodiment, shown for example in <FIG>, the braking means may include, respectively may be constituted of, shaped portions <NUM>', <NUM>", <NUM>‴, for example flat, of the substantially cylindrical seat <NUM> of the hinge body <NUM> susceptible to act against the areas <NUM>', <NUM>", <NUM>‴ of the outer surface <NUM>' of the bushing <NUM>.

Suitably, the shaped portions <NUM>', <NUM>", <NUM>‴ may internally lie on a circumference C having its center on the axis X and radius r coincident with the radius of the substantially cylindrical seat <NUM> not taken in correspondence with the shaped portions <NUM>', <NUM>", <NUM>‴. For example, the radius r may be taken between the two consecutive portions <NUM>', <NUM>".

Consequently, the radius r' in correspondence with one of the shaped portions <NUM>', <NUM>", <NUM>‴ is less than the radius r not taken in correspondence with the shaped portions <NUM>', <NUM>", <NUM>‴.

In this way, the bushing <NUM> being locally deformed presses against the portion <NUM> of the pivot <NUM>, by braking the rotatable movement of the latter around the axis X and then by braking the rotation of the closing element.

It is understood that the hinge <NUM> may include any number of shaped portions <NUM>', <NUM>", <NUM>‴, for example one, two or more than three, without departing from the scope of the appended claims.

In another preferred but not exclusive embodiment, the braking means may include a pair of adjusting screws <NUM> passing through the hinge body <NUM> and placed on opposite sides with respect to a plane parallel to both axes X and Y.

Each of the adjusting screws <NUM> may have an operative portion <NUM>' accessible from outside by a user and a working portion <NUM>" susceptible to come in contact engage with the areas <NUM>', <NUM>", <NUM>‴ of the outer surface <NUM>' of the bushing <NUM> to locally force the inner surface <NUM>" against the portion <NUM> of the pivot <NUM>.

In this way, the user is able to brake in an adjustable manner the rotatable movement of the pivot <NUM> around the axis X. By acting on both the adjusting screws <NUM> it is possible to regulate the braking effect in a differentiated manner in the two directions of opening / closing of the closing element.

It is understood that the hinge <NUM> may also include only one of the adjusting screws <NUM>, or more than two without departing from the scope of the appended claims.

It is also understood that the hinge <NUM> may include both the above-mentioned braking means without departing from the scope of the appended claims.

From the above description, it appears evident that the hinge according to the invention achieves the intended objects.

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

Claim 1:
A hinge for the controlled rotatable movement of at least one closing element, such as a door, a shutter or the like, anchored to a stationary support structure, such as a wall, a floor, a frame or the like, the hinge comprising:
- a hinge body (<NUM>) anchorable to one of the stationary support structure and the at least one closing element and at least one pivot (<NUM>) defining a first axis (X) anchorable to the other of the stationary support structure and the closing element, said at least one pivot (<NUM>) and said hinge body (<NUM>) being reciprocally coupled so that the closing element rotates between at least one open position and at least one closed position;
- at least one working chamber (<NUM>) internal to said hinge body (<NUM>) defining a second axis (Y) substantially perpendicular to the first axis (X), said at least one working chamber (<NUM>) including a bottom wall (<NUM>);
- at least one plunger member (<NUM>) sliding within said at least one working chamber (<NUM>) along said second axis (Y) between a position proximal to said bottom wall (<NUM>) of said at least one working chamber (<NUM>) and a position distal therefrom;
wherein said at least one pivot (<NUM>) includes cam means (<NUM>) rotating around said first axis (X) to move said at least one plunger member (<NUM>) from the distal position to the proximal position, cam follower means (<NUM>) being further provided to interact with said cam means (<NUM>) integrally coupled with said at least one plunger member (<NUM>) to slide therewith along said second axis (Y);
characterized in that
said at least one pivot (<NUM>) consists of a first and a second mutually superimposed half-portion (<NUM>', <NUM>") to be assembled together, means (<NUM>, <NUM>', <NUM>") for the coupling of said first and second half-portions (<NUM>', <NUM>") once assembled being provided so as to make them reciprocally integral;
wherein said first and second mutually superimposed half-portions (<NUM>', <NUM>") once assembled form said cam means (<NUM>).