Patent Grant
9926731
The present invention generally relates to closing hinges, and more particularly relates to a closing hinge device for closing a closing element, such as a door, a shutter, a gate or the like, anchored to a stationary support structure, such as a wall, a frame, a supporting pillar and/or a floor.
As known, closing hinges generally comprise a movable element, usually fixed to a door, a shutter or the like, pivoted on a fixed element, usually fixed to the frame thereof, or to a wall and/or to the floor.
Hinges are known from documents U.S. Pat. No. 7,305,797, US2004/206007 and EP1997994, in which the action of the closing means that provide for the return of the shutter to the closed position is not counteracted. A door closing device is known from document EP0407150, which includes hydraulic damping means for counteracting the action of the closing means.
All these prior art devices are more or less bulky, and have, therefore, an unpleasant visual appeal.
Moreover, these prior art devices do not allow adjusting the closing speed and/or the latch closing of the door, or in any case they do not allow a simple and quick adjustment.
Further, these prior art devices have a large number of constructive parts, which makes them difficult to manufacture as well as comparatively expensive, and require a frequent maintenance.
Other prior art hinges are known from documents GB19477, U.S. Pat. No. 1,423,784, GB401858, WO03/067011, US2009/241289, EP0255781, WO2008/50989, EP2241708, CN101705775, GB1516622, US20110041285, WO200713776, WO200636044, WO200625663 and US20040250377.
These known hinges can be improved in terms of bulkiness, reliability, and/or performance.
A main object of this invention is to overcome, at least in part, the above drawbacks by providing a hinge device having high performance, simple construction and low cost properties.
Another object of the invention is to provide a hinge device that has an extremely low bulk.
Another object of the invention is to provide a hinge device which ensures the automatic closing of the door from the open position.
Another object of the invention is to provide a hinge device which ensures the controlled movement of the door to which it is connected, upon its opening as well as upon its closing.
Another object of the invention is to provide a hinge device which can support even very heavy doors and door or window frame structures, without changing its behavior and without need for adjustments.
Another object of the invention is to provide a hinge device which has a minimum number of constitutive parts.
Another object of the invention is to provide a hinge device which can keep the exact closing position over time.
Another object of the invention is to provide an extremely safe hinge device.
Another object of the invention is to provide a hinge device that is extremely easy to install.
Another object of the invention is to provide a hinge device which can be mounted on closing means, which have a right as well as a left opening direction.
These and other objects, as better explained hereafter, are fulfilled by a hinge device having one or more of the features that are herein described, claimed, and/or shown.
A hinge device according to the invention may be employed for the rotating movement of a closing element, such as a door, a shutter or the like, which may be anchored to a stationary support structure such as a wall or frame of a door or of a window, or a wall.
Appropriately, the device may include a fixed element anchorable to the stationary support structure and a movable element anchorable to the closing element.
The fixed and the movable elements may be reciprocally coupled to rotate around a first longitudinal axis, which may be substantially vertical, between an open position and a closed position, corresponding to the positions of the open and closed closing element.
As used herein, the terms “fixed element” and “movable element” are intended to indicate the one or more parts or components of the hinge device which, respectively, are designed to be fixed and movable during the normal use of the hinge device.
Advantageously, the device may comprise at least one slider slidably movable along a respective second axis between a compressed end position, corresponding to one between the closed or the open position of the movable element, and an extended end position, corresponding to the other one between the closed or the open position of the movable element.
In a preferred, non-exclusive embodiment, the at least one slider and the movable element may be mutually coupled so that to the rotation of the movable element around the first axis corresponds to the sliding of the slider along the second axis and vice versa.
The first and the second axis may be reciprocally parallel or coincident. In the last case, the first and the second axis may define a single axis which acts as both rotation axis for the movable element and sliding axis for the slider.
Appropriately, one between the movable and the fix elements may include at least one working chamber defining the second longitudinal axis to slidably house the at least one slider, whereas the other between the movable element and the fix element may comprise a pivot defining the first rotation axis of the movable element.
Advantageously, the hinge device may include a generally box-shaped hinge body which may include the at least one working chamber. The hinge body may have an elongated shape to define the first rotation axis of the movable element and/or the second sliding axis of the slider.
In a preferred, non-exclusive embodiment, the pivot may include an actuating member which cooperates with the at least one slider to allow the rotating movement of the movable element around the first axis.
As used herein, the expression “actuating member” and derivatives thereof is intended to indicate at least one mechanic member which, interacting with another mechanic member, is suitable for moving thereof of any motion and/or in any direction. Therefore, as used herein, the actuating member may be fix or may move of any motion and/or in any direction, provided that it is suitable to allow the rotating movement of the movable element around the first axis.
In another preferred, non-exclusive embodiment, the slider may include the actuating member, which may cooperate with the pivot to allow the rotating movement of the movable element around the first axis.
Appropriately, the at least one slider may be rotatably blocked in the at least one working chamber, so as to avoid any rotation around the second axis during the sliding thereof between the compressed and extended end positions.
In a preferred, non-exclusive embodiment of the invention, the actuating member may include a cylindrical portion of the pivot or of the at least one slider.
Thanks to such configuration, the hinge device according to the invention allows the rotating movement of the closing element around the first longitudinal axis in a simple and effective way.
The bulkiness and the production costs result extremely moderate. Moreover, thanks to the minimum number of constitutive parts, the average life of the device is maximized, minimizing at the same time the maintenance costs.
Further, thanks to such configuration, the hinge device according to the invention may be indifferently mounted on closing elements having right as well as left opening senses.
In order to ensure the automatic closing of the door once it has been opened, the hinge device according to the invention may further include counteracting elastic means, for example one or more springs or a pneumatic cylinder, acting on the at least one slider to automatically return it from one between said compressed and extended end positions towards the other between said compressed and extended end positions.
On the other side, independently from the presence or not of the counteracting elastic means, the slider of the hinge device according to the invention may include a plunger element movable in the at least one working chamber along the second axis, the working chamber including a working fluid, for example oil, acting on the plunger element to hydraulically counteract the action thereof, so as to adjust the rotation of the movable element from the open position to the closed position.
In this last embodiment, if the hinge device also includes the counteracting elastic means it acts as a hydraulic door closer or as a hydraulic hinge with automatic closing wherein the closing action of the counteracting elastic means is hydraulically damped by the working fluid.
If, on the contrary, the hinge device does not include the counteracting elastic means, it acts as an hydraulic brake to hydraulically damp the closing action which may be imparted to the closing element manually or by a further hinge, for example the hinge manufactured according to the teachings of European patent EP2019895 B1.
If, on the other hand, the device includes the counteracting elastic means but does not include the working fluid, the device acts as a mechanic door closer or hinge with automatic closing.
In any case, to adjust the closing angle of the closing element, the at least one working chamber may possibly comprise at least one set screw having a first end interacting with the at least one slider and a second end operable from the outside by a user to adjust the stroke of the slider along the second axis.
Preferably, the at least one working chamber may include one couple of set screws placed in correspondence of the ends of the hinge body, so as to allow the double adjustment thereof.
Advantageously, one between the pivot and the at least one slider may have at least one groove inclined with respect to the first longitudinal axis, which defines at least partially the actuating member, whereas the other between the at least one slider and the pivot may be mutually coupled with the at least one groove. Wth this aim, at least one outwardly extending appendix may be provided, to slide in the at least one groove.
Preferably, at least one pair of equal grooves angularly spaced of 180° may be provided, with a respective pair of appendices each outwardly extending to slide in a respective groove.
Appropriately, the appendices may define a third axis substantially parallel to the first and/or to the second axis.
In a particularly preferred but non-exclusive embodiment of the invention, these grooves may be communicating between one another to define a single guide element passing through the pivot or the slider, a first passing through pin being provided which is housed in the single guide element to define the appendices.
In order to ensure the maximum control of the closing element upon the closing as well as upon the opening of the closing element, each appendix may have at least one sliding portion in the respective groove which has an outer diameter substantially equal to the width of the respective groove.
Further, in order to minimize the vertical bulk, each groove may have at least one helical portion wound around the first axis defined by the pivot, which may be right-handed or left-handed.
Advantageously, the at least one helical portion may develop for at least 90° along the cylindrical portion of the pin, preferably for at least 180°, up to 360° and over.
In this manner, the actuating member is defined by a single spiral with two or more starts, with the first pin sliding within it. The first pin and the actuating member, therefore, are connected to one another by means of a helical primary pair wherein the pin translates and rotates during the interaction with the single guide element constituted by the spiral having two starts.
Advantageously, the single guide element may include only one single helical portion having constant slope.
In a first preferred embodiment, the single guide element is closed to both ends so as to define a closed path having two blocking end point for the first pin sliding therethrough. This configuration allows the maximum control of the closing element, both during opening and closing.
In another preferred embodiment the single guide element is closed to only one end so as to define a partly open path having one blocking end point for the first pin sliding therethrough and one open end point.
In order to have optimal vertical bulk, the at least one helical portion may have a pitch comprised between 20 and 100 mm, and preferably comprised between 30 and 80 mm.
As used herein, the expression “pitch” of the helical portion and derivatives thereof is intended to indicate the linear distance in millimeters between the initial point of the helical portion and the point where the helical portion makes a complete rotation of 360°, taken in correspondence of the central point of the helical portion along an axis parallel to the axis around which the helical portion winds.
In order to ensure a blocking point of the closing element along the opening/closing path thereof, each groove may have a flat portion before or after the helical portion, which may develop for at least 10° along the cylindrical portion, up to 180°.
This way, it is possible to block the closing element, for example in its open position.
The blocking points, and therefore the flat portions, may be more than one along the opening/closing path of the closing element.
Advantageously, in order to further minimize the vertical bulks, the pivot and the slider may be telescopically coupled to each other.
Appropriately, one between the pivot and the at least one slider may include a tubular body to internally house at least one portion of the other between the pivot and the at least one slider.
The tubular body may have a cylindrical wall encompassing the portion of the other between the pivot and the at least one slider. The cylindrical wall and the portion of the other between the pivot and the at least one slider may be reciprocally connected to allow the sliding movement of the slider upon the rotation of the tubular body and vice versa.
In a preferred, non-exclusive embodiment of the invention, the pivot may include the tubular body, whereas the elongated body of the at least one slider may include a stem having its first end slidingly inserted in the tubular body, the latter including a cylindrical wall defining the cylindrical portion having the at least one inclined groove.
On the other side, in another preferred, non-exclusive embodiment of the invention, the elongated body of the at least one slider may include the tubular body, whereas the pivot may be housed within the at least one slider, the latter including a first end sliding in the at least one inclined groove of the pivot.
The counteracting elastic means, if present, may be configured to slidingly move along the second axis between a position of maximum and minimum elongation.
In a preferred, non-exclusive embodiment, the counteracting elastic means and the at least one slider may be reciprocally coupled so that the counteracting elastic means are in their position of maximum elongation in correspondence of the extended end position of the slider.
In this embodiment, the counteracting elastic means may be interposed between the cylindrical portion of the pivot and the second end of the at least one slider, which may be opposed to the first end.
This way, upon the opening of the closing element, the counteracting elastic means act on the second end of the at least one slider to return it back to its extended end position, returning at the same time the closing element back to its closed position. Wth this purpose, the at least one slider may include a radial expansion of the second end, whereas the counteracting elastic means may be contact engaged against the pivot. Alternatively or in combination with this feature, the counteracting elastic means may be housed internally to the pivot so as to act on the at least one slider in correspondence of its first end.
Also in this case, upon the opening of the closing element, the counteracting elastic means act on the at least one slider to return it back to its extended end position, returning at the same time the closing element back to its closed position. With this aim, the counteracting elastic means may be contact engaged against an upper wall of the pivot and they may comprise a pushing member acting against the first end of the at least one slider.
In another preferred, non-exclusive embodiment of the invention, the counteracting elastic means and the at least one slider may be reciprocally coupled so that the counteracting elastic means are in the position of maximum elongation in correspondence of the compressed end position of the slider.
In such embodiment, the counteracting elastic means may be placed within the at least one working chamber so as to act on the at least one slider in correspondence with the second end.
With this aim, the counteracting elastic means may be contact engaged against a lower wall of the at least one working chamber, whereas the second end of the at least one slider may include the above mentioned radial expansion.
Advantageously, the hinge device according to the invention may further include one or more anti-friction elements, which may preferably be interposed between the movable element and the fixed element to facilitate the mutual rotation thereof.
Suitably, the anti-friction element may include at least one annular bearing, while the box-shaped hinge body may include at least one support portion to support said the annular bearing.
Suitably, the box-shaped hinge body may include at least one support portion susceptible to be loaded by the closing element through the movable element, the at least one support portion being designed to support the at least one anti-friction element.
Preferably, the at least one anti-friction element and the at least one support portion may be configured and/or may be in a mutual spaced relationship so that the movable element and the fixed element are spaced apart each other.
In a preferred embodiment of the invention, the above support portion may be a first support portion which is positioned in correspondence of at least one end of the box-shaped hinge body to be loaded by the closing element during use through the movable element. In this case, the annular bearing may be a first annular bearing, which may be of the radial-axial type, interposed between the first support end portion and the loading movable element.
It is understood that the first support portion may support one or more first annular bearings.
Preferably, the movable element has a loading surface susceptible to came into contact with said the first annular bearing in such a manner to rotate thereon.
In order to further minimize the mutual frictions, the first annular bearing and the first support end portion of the box-shaped hinge body may be configured and/or may be in a mutual spaced relationship so that during use the loading movable element is spaced apart from said box-shaped hinge body.
Preferably, the hinge device of the invention may include a couple of first annular bearings positioned in correspondence of a respective couple of first support end portions positioned to both ends of the box-shaped hinge body. In this manner, the hinge device of the invention may be reversible, i.e. may be turned upside down by maintaining the same anti-friction property on both ends.
In a further preferred but non exclusive embodiment of the invention, the above at least one support portion may be a second support portion positioned within the working chamber to be loaded by said pivot during use. In this case, the above at least one annular bearing may be a second annular bearing, which may be of the axial type, interposed between the second support portion and the pivot.
It is understood that the second support portion may support one or more second annular bearings.
Preferably, the pivot may have a loading surface susceptible to came into contact with the second annular bearing in such a manner to rotate thereon.
In case of hinge device including the counteracting elastic means located within the working chamber but outside the pivot, the second support portion may be susceptible to separate said the working chamber into a first and second areas, the pivot and the second annular bearing being housed into the first area, the counteracting elastic means being housed in the second area.
Thanks to this configuration, no torsion action between the pivot and the counteracting elastic means may arise, since the two elements are mutually separated by the second support portion. Moreover, the counteracting elastic means have not loss of force due to frictions, since the pivot rotate on the annular bearing which is positioned onto the second support portion.
In this manner, an extremely performing hinge device can be provided.
Suitably, the counteracting elastic means may include a spring having one end interacting, preferably directly, with the second support portion.
In case of hinge device including the counteracting elastic means located within the pivot, the anti-friction element may be is an anti-friction interface member interposed between the counteracting elastic means and the slider.
Advantageously, the first end of the slider may have a round surface, the anti-friction interface member having a contact surface interacting with the rounded first end. Preferably, the anti-friction interface member may have a spherical of discoid shape.
It is understood that the box-shaped hinge body may include both the first and the second support portions for supporting respectively the first and the second one or more annular bearings. On the other hand, the box-shaped hinge body may include the first support portion or portions or the second support portion for supporting respectively the first or the second one or more annular bearings.
In order to rotatably block the at least one slider in the at least one working chamber, the at least one slider may include an axial passing slot extending along the second longitudinal axis, whereas the device may further include a second pin radially inserted through the slot and anchored to the at least one working chamber.
The second pin rotatable blocking the at least one slider into the at least one working chamber may be different from the first pin for connecting the first end of the at least one slider to the inclined grooves of the pivot.
However, in a preferred, non-exclusive embodiment of the invention, the first pin defining the appendices of the at least one slider may coincide with the second pin rotatable blocking the at least one slider into the at least one working chamber. In other words, in this embodiment the hinge device may include a single pin which fulfils both functions.
The plunger element of the at least one slider, if present, may comprise a pushing head designed to separate said at least one working chamber into at least a first and a second variable volume compartments.
Appropriately, the first and the second variable volume compartments may be fluidly connected to each other and/or adjacent.
Moreover, the first and second variable volume compartments may be advantageously designed to have in correspondence of the closed position of the closing element respectively the maximum and the minimum volume.
In order to allow the flow of the working fluid from the first to the second compartment during the opening of the closing element, the pushing head of the plunger element may comprise a passing through hole so as to put into fluidic communication the first and the second compartment.
Furthermore, in order to prevent the backflow of the working fluid from the second compartment to the first one during the closing of the closing element, a check valve may be provided which interacts with the passing through hole of the pushing head, which valve may be preferably of the one-way normally closed type to open upon the opening of the closing element.
For the controlled backflow of the working fluid from the second compartment to the first one during the closing of the closing element, an appropriate hydraulic circuit may be provided.
In a preferred, non-exclusive embodiment, in which the plunger element may be housed with a predetermined clearance in the a least one working chamber, this backflow hydraulic circuit may be defined by the interspace between the pushing head of the plunger element and the inner surface of the at least one working chamber.
In another preferred, non-exclusive embodiment of the invention, in which the plunger element may be tightly housed in the at least one working chamber, the hinge body of the hinge device may comprise the hydraulic circuit for the controlled backflow of the working fluid.
Appropriately, this hydraulic circuit may have an inlet for the working fluid which is present into the second compartment and one or more outlets thereof in the first compartment, for example a first and a second outlets which may be fluidly connected to one another.
These first and second outlets may control and adjust, respectively, the speed of the closing element and its latch action towards the closed position.
For this purpose, the plunger element may comprise a substantially cylindrical rear portion facing the inner surface of the first compartment, which may remain decoupled from the first outlet of the at least one hydraulic circuit for the whole stroke of the plunger element.
On the other hand, the rear portion of the plunger element may be in a spatial relationship with the second outlet so that the second outlet remains coupled with the first outlet for a first initial part of the stroke of the plunger element and remains decoupled from the second outlet for a second final part of this stroke, so that the closing element latches towards the closed position when the movable element is in proximity of the fix element.
Appropriately designing the parts, it is possible to adjust the position of the latch action, which may be normally accomplished when the movable element is in a position comprised between 5° and 15° with respect to the closed position.
In order to adjust the flow of the working fluid from the second compartment to the first one during the closing of the closing element, the hinge body may have a first screw having a first end interacting with the first outlet of the hydraulic circuit and a second end operable from the outside by a user.
In this way the user, appropriately operating on the second end of the first screw, acts on the first end thereof so that it progressively obstructs the first outlet, adjusting the speed with which the working fluid returns from the second to the first compartment.
On the other hand, for adjusting the force with which the closing element latches towards the closed position, the hinge body may have a second screw having a first end interacting with the second outlet of the hydraulic circuit and a second end operable from the outside by a user.
This way the latter, appropriately operating on the second end of the second screw, acts on the first end thereof so that it progressively obstructs the second outlet, adjusting the latch speed of the closing element towards the closed position.
Advantageous embodiments of the invention are defined according to the dependent claims.
Further features and advantages of the invention will appear more evident upon reading the detailed description of some preferred, non-exclusive embodiments of a hinge device according to the invention, which are described as non-limiting examples with the help of the annexed drawings, in which:
Referring to the above mentioned FIGS., the hinge device according to the invention, generally indicated with 1, is particularly suitable for rotatably moving a closing element D, such as a door, a shutter or the like, which may be anchored to a stationary support structure S, such as for instance a wall and/or a frame of a door or of a window and/or a supporting pillar and/or the floor.
c show several embodiments of the hinge device 1. Where not otherwise specified, similar or equal parts and/or elements are indicated with a single reference number, which means that the described technical features are common to all the similar or equal parts and/or elements.
It is understood that only the embodiment of
All the embodiments shown herein include a movable element, which may include a movable connecting plate 10, anchorable to the closing element D, and a fixed element, which may include a fixed connecting plate 11, anchorable to the stationary support structure S.
The fix plate 11 and the movable plate 10 may be mutually coupled for rotating around a first longitudinal axis X, which may be substantially vertical, between an open position, shown for instance in
In all the embodiments of the invention shown herein, the hinge device 1 may include at least one slider 20 movable along a respective second axis Y between a compressed end position, shown for instance in
The first and the second axis X, Y may be reciprocally parallel, such as for example in the embodiments of the invention shown in figures from 32 to 34c, or coincident, such as for example in the embodiments of the invention shown in figures from 1 to 31b.
In this last case, the first and the second axis X, Y may define a single axis, indicated with X≡Y, which acts as both rotation axis for the movable plate 10 and sliding axis for the slider 20.
In all the embodiments of the invention shown herein, the hinge device 1 may comprise at least one working chamber 30 defining the second longitudinal axis Y to slidably house the respective slider 20. On the other hand, the hinge device 1 may comprise two or more working chambers 30, 30′ each one defining a respective second longitudinal axis Y, Y′ and comprising a respective slider 20, 20′, such as for instance in the embodiment of the invention shown in FIGS. from 32 to 34c.
Each working chamber 30 may be made within a hinge body 31, which may have a generally box-shaped shape.
The slider 20 may include a body 21 elongated along the axis Y, with a first end 22 and a second opposed end 23.
Of course, in the embodiments of the invention in which the first and the second axis X, Y coincide, the working chamber 30 may be single and define the single axis X≡Y.
Advantageously, in all the embodiments of the invention shown herein, the hinge device 1 may comprise a pivot 40, which may define the rotations axis X of the movable plate 10.
Of course, in the embodiments of the invention wherein the first and the second axis X, Y coincide, the pivot 40 may define the single axis X≡Y, and may be at least partially housed in the working chamber 30 so as to be coaxial with the working chamber.
In some embodiments of the invention, as for example those shown in
On the other hand, in other embodiments of the invention, such as the one shown in
Appropriately, the pivot 40 may comprise a portion 41 outgoing from the hinge body 31 for the coupling with the movable element 10 or with the stationary support structure S or with the closing element D.
Moreover, the pivot 40 may include a substantially cylindrical portion 42 internal to the hinge body 31 and suitable to cooperate with the slider 20 so that to the rotation of the movable element 10 around the first axis X corresponds the sliding of the slider 20 along the second axis Y and vice versa.
For this purpose, the cylindrical portion 42 of the pivot 40 may include at least one pair of grooves 43′, 43″ equal to each other and angularly spaced of 180°. Appropriately, the grooves 43′, 43″ may be communicating with one another so as to define a single guide element 46 passing through the cylindrical portion 42 of the pivot 40.
In this way, it is possible to obtain a total control of the closing element D upon its opening as well as upon its closing, and to act on the spring 50 with extremely great force.
Moreover, the first end 22 of the slider 20 may include one pair of appendices 24′, 24″ extending outwards from corresponding opposed parts thereof to slide each in a respective groove 43′, 43″. Appropriately, the appendices 24′, 24″ may define a third axis Z substantially perpendicular to the first and second axis X, Y.
On the other side, as shown in the embodiment shown in the
It is to understand that the assembly pivot 40-slider 20 shown in FIGS. from 6a to 6c may equivalently replace the assembly present in all embodiments of the invention shown in FIGS. from 1 to 5b and from 7 to 35b.
Advantageously, the appendices 24′, 24″ may be defined by a first pin 25 passing through the slider 20 or the pivot 40 in proximity of the first end 22 and housed in the single guide element formed by the communicating grooves 43′, 43″. The first pin 25 may define an axis Z substantially perpendicular to the first and/or to the second axis X, Y.
In order to ensure the maximum control of the closing element D upon its opening and closing, each appendix 24′, 24″ may have at least one sliding portion in the respective groove which has an outer diameter Øe substantially equal to the width Ls of the respective groove 43′, 43″. Even if for sake of simplicity this feature has been shown only in
Furthermore, in order to minimize the vertical bulk, each groove 43′, 43″ may have at least one helical portion 44′, 44″ wound around the first axis X defined by the pivot 40, which may be right-handed or left-handed.
Advantageously, the single guide element 46 may include a single helical portion 44′, 44″ having constant slope.
Moreover, in order to have optimal bulk, each helical portion 44′, 44″ may have a pitch comprised between 20 mm and 60 mm, and preferably comprised between 35 mm and 45 mm.
Appropriately, the slider 20 may be rotatably blocked in the respective working chamber 30, so as to avoid rotations around the axis Y during the sliding thereof between the compressed and extended end positions.
Wth this aim, the slider 20 may include a passing-through axial slot 26 extending along the axis Y, a second pin 27 radially housed into the slot 26 and anchored to the working chamber 30 being further provided. The second pin 27 may define an axis Z′ substantially perpendicular to the first and/or to the second axis X, Y.
As shown in the embodiments shown in the FIGS. from 1 to 17c, the first pin 25 and the second pin 27 may be different from each other.
However, as for instance particularly shown in the FIGS. from 20 to 34c, the hinge device 1 may include a single pin 25≡27, which acts as both guide of the slider 20 during the sliding thereof along the grooves 43′, 43″ and rotating blocking element thereof. In this case, the axis Z may coincide with the axis Z′, so as to define a single axis Z≡Z′.
In order to minimize the vertical bulk of the hinge device 1, the pivot 40 and the slider 20 may be telescopically coupled to one another.
For this purpose, one between the pivot 40 and the slider 20 may comprise a tubular body to internally house at least one portion of the other between the pivot 40 and the slider 20.
In the embodiments wherein the pivot 40 internally houses the slider 20, such as for example those shown in the FIGS. from 1 to 5b and from 7 to 17c, the tubular body is defined by the cylindrical portion 42, whereas the internally housed portion may be defined by the first end 22 which includes the first pin 25. On the other side, in the embodiment shown in
In the embodiments wherein the slider 20 internally houses the pivot 40, such as for example those shown in the FIGS. from 20 to 25b, the tubular body is defined by the plunger element 60, whereas the internally housed portion may be defined by the cylindrical portion 42 of the pivot 40.
The assembly pivot 40-working chamber 30-slider 20, therefore, defines a mechanism wherein the three components are mutually coupled by means of lower pairs.
In fact, the pivot 40 and the working chamber 30 are connected to each other by a revolute pair, so that the only reciprocal movement can be the rotation of the first one with respect to the other one around the axis X. It is understood that the pivot 40 may rotate with respect to the working chamber 30 or vice versa.
The slider 20 is then connected to the pivot 40 and with the working chamber 30 by means of respective prismatic pairs, so that the only reciprocal movement can be the sliding of the slider 20 along the axis Y.
Moreover, the pivot 40 and the slider 20 are connected to each other by means of a screw pair, so that to the rotation of the pivot 40 or of the working chamber 30 around the axis X corresponds exclusively to the sliding of the slider 20 along the axis Y.
The extreme simplicity of the mechanism allows obtaining an exceptionally efficient, reliable and long-lasting hinge device, even under the hardest work conditions.
In order to ensure a blocking point of the closing element D along the opening/closing path thereof, as for example shown in the FIGS. from 15 to 19c, each groove 43′, 43″ may have a flat portion 45′, 45″ after or before the portion with helical course 44′, 44″, which may wind for at least 10° along the cylindrical portion 42, up to 180°.
In this way it is possible to block the closing element, for example in its open position.
Advantageously, as shown in
Thanks to this feature, it is possible to obtain the maximum control of the closing element D.
On the other hand, as shown in
In order to ensure the automatic closing of the door once opened, the hinge device 1 may further include counteracting elastic means, for example a spring 50, acting on the slider 20 to automatically return it from one between the compressed and extended end position and the other between the compressed and extended end position.
For example, in the embodiment shown in FIGS. from 1 to 4b, the spring 50 acts on the slider 20 to return it from the extended end position to the compressed end position, which represents the rest position or maximum elongation of the spring 50.
On the other hand, in the embodiment shown in
Even if in the embodiments shown in FIGS. from 1 to 22c and from 28 to 34c all hinge devices 1 include a single spring 50, it is understood that the counteracting elastic means may include also more springs or alternative means, for example a pneumatic cylinder, without departing from the scope of the invention defined by the appended claims.
The spring 50 may have any position along the axis Y. For example, in the embodiment shown in FIGS. from 1 to 4b it is interposed between the end 23 of the slider 20 and an abutment wall 35 of the chamber 30.
On the other hand, it may be interposed between the pivot 40 and the end 23 of the slider 20, such as for example in the embodiment shown in FIGS. from 7 to 12c.
The spring 50 may be then internal to the pivot 40, such as for example in the embodiment shown in FIGS. from 15 to 22c.
In order to minimize the mutual frictions, the hinge device according to the invention may include at least one anti-friction element, which may be interposed between the movable and the fixed part of the hinge device.
Suitably, the at least one anti-friction element may include at least one annular bearing, while the box-shaped hinge body 31 may include at least one support portion to support the at least one annular bearing.
All embodiments of the invention may include a first support portion 200 positioned in correspondence of an end 210 of the box-shaped hinge body 31 to be loaded by the closing element D during use through the movable plate 10. The first support portion 200 is suitable to support a first annular bearing 220 interposed between the same first support end portion and the movable connecting plate 10.
Suitably, the movable connecting plate 10 may have a loading surface 230 susceptible to came into contact with the first annular bearing 220, in such a manner to rotate thereon.
The first annular bearing 220 which is positioned on the first support portion 200 of the hinge body 31 is suitable to support the load of the closing element D, so as to leave the pivot 40 free to rotate around the axis X with minimum friction. In other words, the pivot 40 is not loaded by the closing element D, which load is fully supported by the hinge body 31.
To this end, the first annular bearing 220 is of the radial-axial type, so as to support both the axial and the radial load of the closing element D. In
In order to maximize the anti-friction effect, the first annular bearing 220 and the first support end portion 200 may be configured and/or in a mutual spaced relationship so that during use the movable element 10 is spaced apart from the box-shaped hinge body 31, thus defining an interspace 360 as shown in
The first annular bearing 220 may have a first outer diameter D′ and a first height H, while the first support end portion 200 may be defined by a annular recess having a diameter substantially matching the first outer diameter D′ of the first annular bearing 220 and a second height h.
Suitably, the first height H may be higher than the second height h. The thickness T of the interspace 360 may be defined by the difference between the first height H of the first annular bearing 220 and the second height h of the first support end portion 200.
In some preferred, non-exclusive embodiment of the invention, the hinge body 31 may include a couple of first annular axial-radial bearings 220, 220′ positioned in correspondence of a respective couple of first support end portions 200, 200′ located at both ends 210, 210′ thereof.
In this manner, the hinge device of the invention may be reversible, i.e. may be turned upside down by maintaining the same anti-friction properties on both ends.
Suitably, the connecting plate 10 may include a couple of loading surfaces 230, 230′ each susceptible to came into contact with a respective first annular bearing 220, 200′ of said couple. In order to maximize the anti-friction effect, the first annular bearings 220, 220′ and the couple of first support end portions 200, 200′ may be configured and/or may be in a mutual spaced relationship so that the loading surfaces 230, 230′ of the movable connecting plate 10 are both spaced apart from the box-shaped hinge body 31, so as to define respective interspaces 360, 360′ having thickness T.
Advantageously, the hinge device 1 of the invention may comprise a second support portion 240 within the working chamber 30 to be loaded by the pivot 40 during use. The second support portion 240 may support a second annular bearing 250 interposed between the same second support portion 240 and the pivot 40.
The second annular bearing 250 may have a second outer diameter D″ and a third height H′, while the second support end portion 240 may be defined by a annular projecting bracket having a maximum diameter D′″ substantially matching the second outer diameter D″ of the second annular bearing 250. The second annular end portion may define a central bore 240′ suitable for the passage of the slider 20 and/or the first and/or second pin 25, 27.
Suitably, the pivot 40 may have a loading surface 260 susceptible to came into contact with the second annular bearing 250 in such a manner to rotate thereon.
Advantageously, the second annular bearing 250 may be of the axial type. In
Without being bound by any theory, it is possible to establish that in the embodiments of the invention which include the tubular bushing 300 the second annular bearing 250 may be of the axial type, while in the embodiments of the invention which do not include the tubular bushing 300 the second annular bearing 250 may be of the radial-axial type.
In order to maximize the anti-friction effect, the second annular bearing 250 and the pivot 40 may be configured and/or may be in a mutual spaced relationship so that the pivot 40 remains spaced apart from the second support portion 240, thus defining an interspace 360′ as shown in
In this manner, no part of the pivot 40 is in contact with the hinge body 31. In another words, the pivot 40 has both ends interposed between the first and the second annular bearings 220, 250.
Moreover, in order to maximize the anti-friction effect, the pivot 40 and the first annular bearing 220 may be configured and/or may be in a mutual spaced relationship so that during use the upper end of the pivot 40 remains spaced apart from the second loading surface 230′ of the connecting plate 10, thus defining an interspace 360″ as shown in
Thanks to this feature, the pivot 40 is completely free to rotate without any friction effect imparted by the load of the closing element D.
Moreover, the pivot 40 is also free from the friction effect imparted by the elastic means 50, which “push” or “pull” the pivot against the second support portion 240.
In the embodiments of the hinge device 1 that include the counteracting elastic means 50 located within the working chamber 30 outside the pivot 40, such as the one shown in
As particularly shown in
In this manner, the pivot 40 and the counteracting elastic means 50 are mutually separated by the second support portion 240. Therefore, the rotation of the pivot 40 does not affect the action of the elastic means 50, which work independently each other.
Moreover, the counteracting elastic means 50 have not loss of force due to frictions, since the pivot 40 rotate on the annular bearing 250 which is positioned onto the second support portion 240.
In this manner, it is possible to use the full force of the elastic means 50 for all the path of the single guide element 46.
For example, thanks to this feature it is possible to use a single guide element 46 including a single helical portion 44′, 44″ having constant slope and extending for 180° along the cylindrical portion 42, so as to obtain a closing element D which opens for 180°.
Advantageously, the counteracting elastic means 50 may include a spring 51 having one end 51′.
Suitably, the end 51′ of the spring 51 may directly interact with the second support portion 240. As an alternative, as e.g. shown in
In case of hinge device 1 including the counteracting elastic means 50 located within the pivot 40, such as the one shown in
Suitably, the first end 22 of the slider 20 has a round surface, while the anti-friction interface member 280 has a contact surface 290 interacting with the rounded first end 22.
Advantageously, the anti-friction interface member 280 may have a spherical of discoid shape, such as respectively in the embodiments of
Advantageously, the slider 20 may comprise a plunger element 60 movable in the working chamber 30 along the axis Y. Appropriately, in some embodiments, such as for instance those shown in
Moreover, the chamber 30 may include a working fluid, for example oil, acting on the plunger element 60 to hydraulically counteract the action thereof, so as to control the action of the movable element 10 from the open to the closed position.
The presence of the plunger element 60 and of the oil may be independent from the presence of the counteracting elastic means 50.
For example, the embodiments shown in FIGS. from 1 to 5b do not include the plunger element 60 and the oil, whereas the embodiment shown in
Appropriately, the working chamber 30 may preferably comprise a pair of set screws 32′, 32″ housed in opposite parts 84′, 84″ of the hinge body 31.
Each set screw 32′, 32″ may have a first end 33′, 33″ interacting with the slider 20 to adjust its sliding along the axis Y. Each set screw 32′, 32″ may further have a second end 34′, 34″ operable from outside by a user.
In this way, the user can easily adjust the closing angle of the closing element D.
On the other hand, the hinge device 1 may include the plunger element 60 as well as the relative oil and the counteracting elastic means 50, such as for instance in the embodiments shown in FIGS. from 7 to 19c. In this case, these hinge devices act as a hydraulic hinge or door closer with automatic closing.
Advantageously, the plunger element 60 may comprise a pushing head 61 configured to separate the working chamber 30 a first and a second variable volume compartment 36′, 36″, preferably fluidly connected to one another and adjacent.
In order to allow the flow of the working fluid from the first compartment 36′ to the second compartment 36″ during the opening of the closing element D, the pushing head 61 of the plunger element 60 may comprise a passing through hole 62 to put into fluidic communication the first and the second compartment 36′, 36″.
Moreover, in order to prevent the backflow of the working fluid from the second compartment 36″ to the first compartment 36′ during the closing of the closing element D, valve means may be provided, which may comprise a check valve 63, which may preferably be of the one-way normally closed type to open exclusively upon the opening of the closing element D.
Advantageously, the check valve 63 may include a disc 90 housed with a minimum clearance in a suitable housing 91 to axially move along the axis X and/or Y, with a counteracting spring 92 acting thereon to keep it normally closed. Depending from the sense in which the check valve 63 is mounted, it may open upon the opening or closing of the closing element D.
For the controlled backflow of the working fluid from the second compartment 36″ to the first compartment 36′ upon the closing of the closing element D, an appropriate hydraulic circuit 80 may be provided.
In the embodiments shown in FIGS. from 7 to 9c and from 15 to 17c, the plunger element 60 may be housed with a predetermined clearance in the working chamber 30. In these embodiments, the backflow hydraulic circuit 80 may be defined by the tubular interspace 81 between the pushing head 61 of the plunger element 60 and the inner surface 82 of the working chamber 30.
In this case, the return speed of the working fluid from the second compartment 36″ to the first compartment 36′ may be predetermined and not adjustable, defined in practice by the dimensions of the backflow interspace 81. Moreover, it is not possible to have the latch action of the closing element D towards the closed position.
On the other hand, in the embodiments shown in FIGS. from 10 to 12c, the plunger element 60 may be tightly housed in the working chamber 30. In this embodiment, the backflow circuit 80 may be made within the hinge body 31.
In the embodiments shown in FIGS. from 20 to 25b, for minimizing the bulk, the backflow circuit 80 may be made within the hinge body 31 and within the closing cap 83.
In the embodiment shown in FIGS. from 28 to 31b, the backflow circuit 80 is made within the interspace 81 between the pivot 40 and the inner surface 82 of the working chamber 30. Wth this aim, in correspondence of the closing cap 83, an interface element 85 appropriately shaped to keep in its position the pivot 40 and to define the inlet 38 of the circuit 80 may be inserted.
In these embodiments, the backflow speed of the working fluid from the second compartment 36″ to the first compartment 36′ may be adjustable by means of the screw 71, and further may be possibly possible to have the latch action of the closing element D towards the closed position. The force of the latch action is adjustable by means of the screw 70.
For this purpose, the hydraulic circuit may have an inlet 38 for the working fluid present in the second compartment 36″ and one or more outlets thereof in the first compartment 36′, respectively indicated with 39′, 39″, which may be fluidly connected in parallel.
The first and second outlets 39′, 39″ may control and adjust, respectively, the speed of the closing element D and its latch action towards the closed position.
For this purpose, the plunger element 60 may comprise a substantially cylindrical rear portion 64 unitary sliding therewith and facing the inner surface of the first compartment 36′, which may remain decoupled to the first outlet 39′ for the whole stroke of the plunger element 60. In other words, the cylindrical rear portion 64 of the plunger element 60 does not obstruct the first outlet 39′ for its whole stroke.
On the other hand, the rear portion 64 of the plunger element 60 may be in a spatial relationship with the second outlet 39″ so that the second outlet is fluidly coupled with the rear portion 64 for a first initial part of the stroke of the plunger element 60 and is fluidly uncoupled therefrom for a second final part of this stroke, so that the closing element latches towards the closed position when the movable connecting plate 10 is in proximity of the connecting plate 11.
In other words, the cylindrical rear portion 64 of the plunger element 60 obstructs the second outlet 39″ for a first initial part of its stroke and does not obstruct the second outlet 39″ for a second final part of its stroke.
Appropriately designing the parts, it is possible to adjust the latch position, which may normally take place when the movable element 10 is in a position comprised between 5° and 15° with respect to the closed position.
The screw 71 has a first end 72′ interacting with the first outlet 39′ to progressively obstruct it and a second end 72″ operable from the outside by a user to adjust the flow speed of the working fluid from the second compartment 36″ to the first compartment 36′.
On the other side, the screw 70 has a first end 73′ interacting with the second outlet 39″ to progressively obstruct it and a second end 73″ operable from the outside by a user to adjust the force with which the closing element D latches towards the closed position.
It is understood that in order to have the control of the speed in this last embodiment, it is necessary to tightly insert the plunger element 60 into the working chamber 30 and to replace the backflow circuit 80 by making it within the hinge body 31, as for example in the embodiment of
Moreover, if also the latch action of the closing element is desired, it is sufficient to mount on the plunger element 60 the cylindrical portion 64, as for example in the embodiment of
As particularly shown in
As particularly shown in
In FIGS. from 13a to 14b are schematically shown some embodiments of assemblies 100 for the controlled automatic closing of a closing element D, which include a pair of hinges 110 and 120.
In the embodiment shown in
In other words, in this assembly the spring 50 of the two hinges 110 and 120 cooperates with each other to close the closing element D once opened, whereas the oil present in the hinge 120 hydraulically damps this closing action.
In this embodiment, by acting on the set screws 32′, 32″ it is possible to adjust the opening and closing angle of the closing element D. In particular, by acting on the screw 32′ it is possible to adjust the closing angle of the closing element D, whereas acting on the screw 32″ it is possible to adjust the opening angle thereof.
Moreover, by appropriately acting on the screws 70 and 71 it is possible to adjust the closing speed and the force of the latch action of the closing element D.
In the embodiment shown in
In practice, in this assembly the springs 50 of the two hinges 110 and 120 cooperate with each other so as to close the closing element D once opened, whereas the oil present in both hinges 110 and 120 hydraulically damps this closing action.
As particularly shown in the
In this way, the check valve 63 of the upper hinge 110 opens upon the opening of the closing element D, allowing the flow of the working fluid from the first compartment 36′ to the second compartment 36″, and closes upon the closing of the closing element D, forcing the working fluid to flow through the backflow circuit 80.
On the other side, the check valve 63 of the lower hinge 120 opens upon the closing of the closing element D, allowing the flow of the working fluid from the second compartment 36″ to the first compartment 36′, and closes upon the opening of the closing element D, forcing the working fluid to flow through the backflow circuit 80, which allows the flow of the working fluid from the first compartment 36′ to the second compartment 36″.
In this way the maximum control on the closing element D is obtained, the movement of which is controlled upon its opening as well as upon its closing.
In this embodiment, acting on the screws 70 and 71 it is possible to adjust the closing speed and the force of the latch action of the closing element D.
The pivot 40 has a portion 41 which is elongated to internally house the spring 50.
It is understood that, in order to have the control of the speed in this embodiment, it is necessary to tightly insert the plunger element 60 in the working chamber 30 and to replace the backflow circuit 80 by making it within the hinge body 31 and/or within the closing cap 83, as for example in the embodiment of
Furthermore, if also the latch action of the closing element is desired, it is sufficient to mount on the plunger element 60 the cylindrical portion 64 and to manufacture a suitable outlet of the circuit 80 in the compartment 36″.
As particularly shown in the FIGS. from 18a to 19c, this embodiment has two flat portions 45′, 45″ extending for 180° around the axis X, in correspondence of which the closing element D is blocked.
The pivot 40 has an elongated portion 41 to internally include the spring 50.
For bulkiness reasons, in this hinge the backflow circuit 80 of the working fluid in the first compartment 36′ is made within the hinge body 31 and the closing cap 83, within which the screw 71 for adjusting the closing speed of the closing element D is housed.
Moreover, if also the latch action of the closing element is desired, it is sufficient to mount on the plunger element 60 the cylindrical portion 64 and to manufacture a suitable outlet of the circuit 80 in the compartment 36″.
As particularly shown in
In this embodiment, the plunger element 60 acts also as a slider 20, and is connected to the pivot 40 by means of a single pin 25≡27 which defines a single axis Z≡Z′ substantially perpendicular to the single axis X≡Y.
Apart from this, this hinge is substantially similar to the hinge of
It is also understood that it is possible to use a hinge having the counteracting elastic means 50 for hydraulically braking the closing element, during opening and/or during closing thereof according to the orientation of the valve means 63.
For example,
Thanks to the counteracting elastic means 50, both hinges automatically close the closing element D once opened.
During opening of the closing element, in the upper hinge 110 the oil passes from the compartment 36′ to the compartment 36″ through the valve means 63, while in the lower hinge 120 the oil passes from the compartment 36′ to the compartment 36″ through the circuit 80.
During closing of the closing element, in the upper hinge 110 the oil flows back from the compartment 36″ to the compartment 36′ through the circuit 80, while in the lower hinge 120 the oil flows back from the compartment 36″ to the compartment 36′ through the valve means 63.
As a result, the upper hinge 110 acts as an hydraulic brake during closing of the closing element, while the lower hinge 120 acts as an hydraulic brake during opening thereof.
It is understood that the upper and lower hinges 110, 120 may be used also separate each other, as well as that each hinge can be used in cooperation with any other hinge and/or hydraulic brake.
FIGS. from 26a to 27d schematically show an embodiment of an assembly 100 for the controlled automatic closing and opening of the closing element D. FIGS. from 26a to 26d show the closed position of the closing element D, whereas FIGS. from 27a to 27d show the open position thereof.
In this embodiment, the hinge 110 consists of the hinge-hydraulic brake shown in
As particularly shown in
In practice, in this assembly the spring 50 of the hinge 120 closes the closing element D once opened, whereas the oil in both hinges 110 and 120 hydraulically damps the closing element D upon its opening as well as upon its closing. In particular, the hinge-hydraulic brake 110 damps the closing element D upon its opening, whereas the hinge 120 damps the closing element D upon its closing.
Therefore, in this embodiment, by acting on the screws 71 of the hinges 110 and 120 it is possible to adjust the speed of the closing element D upon its opening as well as upon its closing.
For example, by closing to the utmost the screw 71 of the upper 110, it is possible to completely prevent the opening of the closing element.
Moreover, by adjusting the oil quantity present in the hinge 110 and acting on the screw 71, it is possible to adjust the point beyond which the damping action of the closing element D upon its opening begins. In this case, it is necessary to fill the chamber 30 with less oil than the actual capacity thereof.
In this way, it is possible for example to prevent the closing element D from impacting against a wall or a support, so preserving the integrity of the hinges.
Furthermore, by adjusting the oil quantity present in the hinge 110 and completely closing the screw 71, it is possible to hydraulically create a stopping point to the closing element D upon its opening.
In this hinge the backflow circuit 80 of the working fluid in the first compartment 36′ is made within the interspace 81 between the pivot 40 and the inner surface 82 of the working chamber 30 in the interface element 85, within which the screw 71 for the adjusting of the closing speed of the closing element D is placed.
In this embodiment, the plunger element 60 acts as slider 20, and it is connected to the pivot 40 by means of a single pin 25≡27 which defines a single axis Z≡Z′ substantially parallel to the single axis X≡Y.
The pivot 40 has an elongated cylindrical portion to internally house the spring 50 and the slider 20-plunger 60. The latter is tightly housed within the pivot 40.
The sliders 20, 20′-plunger elements 60, 60′ may be operatively connected to the grooves of the single pivot 40, which may be interposed therebetween for defining the axis X, by means of the single pin 25≡27 inserted into the slots 26, 26′.
By acting on the screw 71 it is possible to adjust the closing speed of the closing element D.
As shown in
Advantageously, these embodiments of the hinge device 1 may comprise an antirotation tubular bushing 300 having a couple of cam slots 310 extending along the first and/or second axis X, Y. The tubular bushing 300 may be coaxially coupled externally to the pivot 40 in such a manner that the first pin 25 operatively engages the cam slots 310.
In this manner, it is possible to have an optimal control of the closing element during opening and/or closing.
Apparently, all stresses of the rotation movement imparted by the pin 25 act on the pivot 40 and/or the tubular bushing 300.
Therefore, advantageously, the material in which the tubular bushing 300 and/or the pivot 40 are made may be different from the material in which the hinge body 31 is made.
For example, the tubular bushing 300 and/or the pivot 40 may be made of a metallic material, e.g. steel, while the hinge body 31 may be made of a polymeric material. In this manner, a very low-cost hinge device is provided.
These embodiments of the hinge device 1, as well as the embodiments shown in the
By contrast,
In particular,
In fact, the embodiment of
To this end, the central housing 30″ and the working chambers 30, 30′ may be fluidly non-communicating. In order to do this, the central housing 30″ may be placed below the working chambers 30, 30′, and the quantity of working fluid within the central housing 30″ may be such that the working chambers 30, 30′ remains free of it.
The plunger element 60 may be configured such as e.g. the one of the embodiment of
The valve member 63 may be configured to allow the passage of the working fluid between the first compartment 36′ and the second compartment 36″ during one of the opening and closing of the closing element D and to prevent the backflow thereof during the other of the opening and the closing of the same closing element D.
A hydraulic circuit 80 may be provided for the controlled backflow of the working fluid between the first compartment 36′ and the second compartment 36″ during the other of the opening and the closing of the same closing element D.
Advantageously, the box-shaped hinge body 31 may include an end cap 400 tightly inserted through the central housing 30″. The end cap 400 may be configured according to the teachings of international application PCT/IB2015/057625 and/or of Italian patent application 102016000034061, which are incorporated herein by reference.
In particular, the hydraulic circuit 80 may include a first duct 401 passing through the end cap 400 in fluid communication with both the first compartment 36′ and the second compartment 36″ and a first adjusting member 402 having a first end 403 interacting with the first duct 401 and a second end 404 accessible by a user to adjust the passage section of the working fluid passing through the first duct 401. In this manner, it is possible to adjust the closing or opening speed of the closing element D.
The hydraulic circuit 80 may further include a second duct 410 passing through the end cap 400 in fluid communication with the first compartment 36′, the second compartment 36″ and the first duct 401. Advantageously, the end cap 400 may further include a second adjusting member 412 having a third end 413 interacting with the second duct 410 and a fourth end 413 accessible by a user to adjust the passage section of the working fluid passing therethrough. In this manner, it is possible to adjust the force by which the closing element D latches towards the closed or open position.
Moreover, the end cap 400 may further include a valve unit 420 acting upon the first duct 401 to selectively open when the pressure in the central housing 30″ exceeds a predetermined threshold value. In practice, the valve unit 420 is an overpressure valve.
In this manner, it is possible to avoid any damage due to an excessive closing or opening force imparted e.g. by a children, which in turn causes an very high working fluid pressure in the hydraulic chamber.
Suitably, an anti-friction element 430 interposed between the end cap 400 and the pivot 40 may be provided to be loaded by the latter, having the same function as described above.
The above disclosure clearly shows that the invention fulfils the intended objects.
The invention is susceptible to many changes and variants, all falling within the inventive concept expressed in the annexed claims. All particulars may be replaced by other technically equivalent elements, and the materials may be different according to the needs, without departing the scope of the invention as defined by the annexed claims.
| Number | Date | Country | Kind |
|---|---|---|---|
| VI2011A0081 | Apr 2011 | IT | national |
| PCT/IB2011/051688 | Apr 2011 | WO | international |
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| Number | Date | Country | |
|---|---|---|---|
| 20160215549 A1 | Jul 2016 | US |
| Number | Date | Country | |
|---|---|---|---|
| Parent | 14007571 | US | |
| Child | 14542999 | US |
| Number | Date | Country | |
|---|---|---|---|
| Parent | 14542999 | Nov 2014 | US |
| Child | 15091460 | US |
