Patent Publication Number: US-10760316-B2

Title: Hinge device for doors, shutters and the like

Description:
FIELD OF INVENTION 
     The present invention is generally applicable to the technical field of the closing and/or control hinges for doors, shutters or like closing elements, and particularly relates to a hinge device for rotatably moving and/or controlling during closing and/or opening a closing element, such as a door, a shutter or the like, anchored to a stationary support structure, such as a wall or a frame. 
     BACKGROUND OF THE INVENTION 
     As known, hinges generally include a movable member, usually fixed to a door, a shutter or the like, pivoted onto a fixed member, usually fixed to the support frame thereof, or to a wall and/or to the floor. 
     From documents U.S. Pat. No. 7,305,797, EP1997994 and U.S. 2004/206007 hinges are known wherein the action of the closing means that ensure the return of the door in the closed position is not damped. From document EP0407150 is known a door closer which includes hydraulic damping means for damping the action of the closing means. 
     All these known devices are more or less bulky, and consequently they have an unpleasant aesthetic appeal. Moreover, they do not allow for adjustment of the closing speed and/or of the latch action of the door, or in any case they do not allow a simple and quick adjustment. 
     Further, these known devices have a large number of construction parts, being both difficult to manufacture and relatively expensive, and requiring frequent maintenance. 
     Other hinges are known from documents GB19477, U.S. Pat. No. 1,423,784, GB401858, WO03/067011, U.S. 2009/241289, EP0255781, WO2008/50989, EP2241708, CN101705775, GB1516622, U.S. 20110041285, WO200713776, WO200636044, U.S. 20040250377 and WO2006025663. 
     These known hinges can be improved in terms of size and/or reliability and/or performance. 
     SUMMARY OF THE INVENTION 
     An object of the present invention is to overcome at least partly the above mentioned drawbacks, by providing a hinge device having high functionality, simple construction and low cost. 
     Another object of the invention is to provide a hinge device that allows a simple and quick adjustment of the opening and/or closing angle of the closing element to which it is coupled. 
     Another object of the invention is to provide a hinge device of small bulkiness that allows to automatically close even very heavy doors. 
     Another object of the invention is to provide a hinge device which ensures the controlled movement of the door to which it is coupled, during opening and/or during closing. 
     Another object of the invention is to provide a hinge device which has a minimum number of constituent parts. 
     Another object of the invention is to provide a hinge device capable of maintaining time the exact closing position over time. 
     Another object of the invention is to provide a hinge device extremely safe. 
     Another object of the invention is to provide a hinge device extremely easy to install. 
     These objects, as well as others that will appear more clearly hereinafter, are achieved by a hinge device having one or more of the features herein disclosed and/or claimed and/or shown. 
     Advantageous embodiments of the invention are defined in accordance with the dependent claims. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       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, wherein: 
         FIG. 1  is an exploded view of a first embodiment of the hinge device  1 ; 
         FIGS. 2 a  and 2 b    are respectively axonometric and axially sectioned views of the first embodiment of the hinge device  1  of  FIG. 1 , wherein the second tubular half-shell  13  is in the closed position; 
         FIGS. 3 a  and 3 b    are respectively axonometric and axially sectioned views of the first embodiment of the hinge device  1  of  FIG. 1 , wherein the second tubular half-shell  13  is in a partially open position with the connecting plate  15  is substantially perpendicular to the connecting plate  14  of the first fixed tubular half-shell  12  and wherein the stop screw  90  is in the rest position; 
         FIG. 3 c    is an axially sectioned exploded view of some details of the first embodiment of the hinge device  1  of  FIG. 1 ; 
         FIGS. 4 a  and 4 b    are respectively axonometric and axially sectioned views of the first embodiment of the hinge device  1  of  FIG. 1 , wherein the second tubular half-shell  13  is in a partially open position with the connecting plate  15  substantially perpendicular to the connecting plate  14  of the first fixed tubular half-shell  12  and wherein the stop screw  90  is in working position to block the sliding of the elongated element  60 ; 
         FIG. 4 c    is an axially sectioned enlarged view of some details of the first embodiment of the hinge device  1  of  FIG. 1 ; 
         FIGS. 5 a , 5 b  and 5 c    are respectively axonometric, axially sectioned and side views of the first embodiment of the hinge device  1  of  FIG. 1 , wherein the second tubular half-shell  13  is in the fully open position with the connecting plate  15  substantially coplanar with the connecting plate  14  of the first fixed tubular half-shell  12 ; 
         FIGS. 6 a , 6 b  and 6 c    are axonometric views of the hinge device  1  of  FIG. 1  which show the position of the pin  73  relative to both the bushing  80  and the pivot  50  respectively in the closed positions of  FIGS. 3 a  and 3 b   , in the partially open position of  FIGS. 4 a  and 4 b    and in the of fully open position of  FIGS. 5 a , 5 b    and  5   c;    
         FIG. 7  is a partially exploded, broken axonometric view of the hinge device  1  of  FIG. 1 , which shows the coupling between the second movable tubular half-shell  13  and the bushing  80 ; 
         FIGS. 8 a  and 8 c    are enlarged sectioned views of some details of the first embodiment of the hinge device  1  of  FIG. 1 , with respectively in  FIGS. 8 b  and 8 d    an enlargement of a first embodiment of the regulating member  130  respectively in the of work and rest positions; 
         FIG. 8 e    is a sectioned, enlarged and broken view of some details of the first embodiment of the hinge device  1  of  FIG. 1 , which shows the seat  108  of the channel  100 ; 
         FIG. 8 f    is an axonometric view of the regulating member  130  of  FIGS. 8 a    and  8   b;    
         FIGS. 9 a  to 15 c    are side views of some embodiments of the bushing  80 , wherein for each embodiment of the latter two axonometric views show the position of the pin  73 , the plunger member  30  and the elastic counteracting means  40  in the closed and fully open positions of the second tubular half-shell  13 ; 
         FIGS. 16 and 17  are axonometric views of some embodiments of the pivot  50 , wherein the actuating passing-trough element  72  consist of a single helical portion  71 ′,  71 ″ having a constant inclination or helical pitch, the helical portion  71 ′,  71 ″ being wound respectively for 180° and 90° around the axis X; 
         FIGS. 18 a  to 18 c    are further side views of another embodiment of the bushing  80 , which show two axonometric views of the position of the pin  73 , the plunger member  30  and the elastic counteracting means  40  in the closed and fully open positions of the second tubular half-shell  13 ; 
         FIGS. 19 a  to 19 d    are further side views of another embodiment of the bushing  80 , which show three axonometric views of the position of the pin  73 , the plunger member  30  and the elastic counteracting means  40  in the closed, partially open and fully open positions of the second tubular half-shell  13 ; 
         FIG. 20  is an exploded axonometric view of a third embodiment of the hinge device  1 , wherein the hydraulic circuit  100  is partially located within the end cap  27 ; 
         FIGS. 21 a , 21 b  and 21 c    are axially sectioned views of the hinge device  1  of  FIG. 20  respectively in the closed, partially open with the stop screw  90  in the working position and completely open positions; 
         FIG. 22  is an exploded view of a fourth embodiment of the hinge device  1 ; 
         FIGS. 23 a  and 23 b    are respectively axonometric and axially sectioned views of the embodiment of the hinge device  1  of  FIG. 22 , wherein the second tubular half-shell  13  is in the closed position; 
         FIGS. 24 a  and 24 b    are respectively axonometric and axially sectioned views of the embodiment of the hinge device  1  of  FIG. 22 , wherein the second tubular half-shell  13  is in a partially open position with the connecting plate  15  substantially perpendicular to the connecting plate  14  of the first fixed tubular half-shell  12 ; 
         FIGS. 25 a  and 25 b    are respectively axonometric and axially sectioned views of the embodiment of the hinge device  1  of  FIG. 22 , wherein the second tubular half-shell  13  is in the fully open position with the connecting plate  15  substantially coplanar with the connecting plate  14  of the first fixed tubular half-shell  12 ; 
         FIG. 26  is an exploded view of a fifth embodiment of the hinge device  1 ; 
         FIGS. 27 a  and 27 b    are respectively axonometric and axially sectioned views of the embodiment of the hinge device  1  of  FIG. 26 , wherein the second tubular half-shell element  13  is in the closed position; 
         FIGS. 28 a  and 28 b    are respectively axonometric and axially sectioned views of the embodiment of the hinge device  1  of  FIG. 26 , wherein the second tubular half-shell  13  is in a partially open position with the connecting plate  15  substantially perpendicular to the connecting plate  14  of the first fixed tubular half-shell  12 ; 
         FIGS. 29 a  and 29 b    are respectively axonometric and axially sectioned views of the embodiment of the hinge device  1  of  FIG. 26 , wherein the second tubular half-shell  13  is in the fully open position with the connecting plate  15  substantially coplanar with the connecting plate  14  of the first fixed tubular half-shell  12 ; 
         FIG. 30  is an exploded view of a sixth embodiment of the hinge device  1 ; 
         FIGS. 31 a  and 31 b    are respectively axonometric and axially sectioned views of the embodiment of the hinge device  1  of  FIG. 30 , wherein the second tubular half-shell  13  is in the closed position; 
         FIGS. 32 a  and 32 b    are respectively axonometric and axially sectioned views of the embodiment of the hinge device  1  of  FIG. 30 , wherein the second tubular half-shell  13  is in a partially open position with the connecting plate  15  substantially perpendicular to the connecting plate  14  of the first fixed tubular half-shell  12  and wherein the stop screw  90  is in the rest position; 
         FIGS. 33 a  and 33 b    are respectively axonometric and axially sectioned views of the embodiment of the hinge device  1  of  FIG. 30 , wherein the second tubular half-shell  13  is in a partially open position with the connecting plate  15  substantially perpendicular to the connecting plate  14  of the first fixed tubular half-shell  12  and wherein the stop screw  90  is in the working position to block the sliding of the elongated element  60 ; 
         FIGS. 34 a , 34 b  and 34 c    are respectively axonometric, axially sectioned and side views of the embodiment of the hinge device  1  of  FIG. 30 , wherein the second tubular half-shell  13  is in the fully open position with the connecting plate  15  substantially coplanar with the connecting plate  14  of the first fixed tubular half-shell  12 ; 
         FIG. 35  is an axonometric view of a seventh embodiment of the hinge device  1 ; 
         FIG. 36  is a partially exploded axonometric view of the seventh embodiment of the hinge device  1 ; 
         FIG. 37  is a top view of the embodiment of  FIG. 35  wherein the hinge device  1  has the second tubular half-shell  13  is in the closed position; 
         FIGS. 38 a  and 38 b    are axonometric views of the hinge device  1  of  FIG. 36 , which respectively show the relative position of the connecting plates  14 ,  15  and the positions of the pin  73 , the plunger member  30  and the elastic counteracting means  40  in the position shown in  FIG. 37 ; 
         FIG. 39  is a top view of the embodiment of  FIG. 35  wherein the hinge device  1  has the second tubular half-shell  13  in a partially open position; 
         FIGS. 40 a  and 40 b    are axonometric views of the hinge device  1  of  FIG. 36 , which respectively show the relative position of the connecting plates  14 ,  15  and the positions of the pin  73 , the plunger member  30  and the elastic counteracting means  40  in the position shown in  FIG. 39 ; 
         FIG. 41  is a top view of the embodiment of  FIG. 35  wherein the hinge device  1  has the second tubular half-shell  13  is in the fully open position; 
         FIGS. 42 a  and 42 b    are axonometric views of the hinge device  1  of  FIG. 36 , which respectively show the relative position of the connecting plates  14 ,  15  and the positions of the pin  73 , the plunger member  30  and the elastic counteracting means  40  in the position shown in  FIG. 41 ; 
         FIGS. 43 a  and 43 b    are enlarged sectional views of some details of the embodiment of the hinge device  1  of  FIG. 20 ; 
         FIGS. 44 a , 44 b  and 44 c    are side, sectioned along a plane XLIV-XLIV and axonometric sectioned as above views of the end cap  27 ; 
         FIGS. 45 a  and 45 b    are axonometric views of another embodiment of the bushing  80 ; 
         FIGS. 46 a  and 46 b    are axonometric views of a further embodiment of the bushing  80 ; 
         FIGS. 47 a  to 47 e    are axonometric views of a hinge device  1  which includes the embodiment of the bushing  80  of  FIGS. 46 a  and 46 b    wherein the pin  73  is in several positions along the cam slots  81 ; 
         FIGS. 48 a  and 48 b    are enlarged sectioned views of some details of a hinge device  1  that includes a second embodiment of the regulating member  130  respectively in the work and rest positions; 
         FIG. 49  is an axonometric view of the second embodiment of the regulating member  130  of  FIGS. 48 a    and  48   b;    
         FIG. 50  is an axonometrically sectioned view taken along a plane L-L in  FIG. 49 . 
     
    
    
     DETAILED DESCRIPTION OF EMBODIMENTS OF THE INVENTION 
     With reference to the above figures, the hinge device according to the invention, generally indicated with  1 , is particularly useful for rotatably moving and/or controlling a closing element D, such as a door, a shutter, a gate or the like, which can be anchored to a stationary support structure S, such as a wall and/or a door or window frame and/or a support pillar and/or the floor. 
     Depending on the configuration, the hinge device  1  according to the invention allows only the automatic closing of the closing element D to which it is coupled, as shown in  FIGS. 30 to 34   c , or only the control during opening and/or closing thereof, as shown for example in  FIGS. 22 to 25   b , or both actions, as shown in  FIGS. 1 to 5   c.    
     In general, the hinge device  1  may include a fixed element  10  anchored to the stationary support structure S and a movable element  11  which may be anchored to the closing element D. 
     In a preferred, not exclusive embodiment, the fixed element  10  may be positioned below the movable element  11 . 
     In a preferred, not exclusive embodiment, the fixed and movable elements  10 ,  11  may include a respective first and second tubular half-shell  12 ,  13  mutually coupled each other to rotate about a longitudinal axis X between an open position, shown for example in  FIGS. 3 a  to 5 c   , and a closed position, shown for example in  FIGS. 2 a    and  2   b.    
     Suitably, the fixed and movable elements  10 ,  11  may include a respective first and second connecting plates  14 ,  15  connected respectively to the first and second tubular half-shell  12 ,  13  for anchoring to the stationary support structure S and the closing element D. 
     Preferably, the hinge device  1  can be configured as an “anuba”-type hinge. 
     Advantageously, with the exception of connecting plates  14 ,  15 , all other components of the hinge device  1  may be included within the first and second tubular half-shells  12 ,  13 . 
     In particular, the first tubular half-shell  12  may be fixed and include a working chamber  20  defining the axis X and a plunger member  30  sliding therein. Appropriately, the working chamber  20  can be closed by a closing cap  27  inserted into the tubular half-shell  12 . 
     As better explained later, the first fixed tubular half-shell  12  may further include a working fluid, usually oil, acting on the piston  30  to hydraulically counteract the action thereof and/or elastic counteracting means  40 , for example a helical compression spring  41 , acting on the same plunger member  30 . 
     Suitably, externally to the working chamber  20  and coaxially therewith a pivot  50  may be provided, which may advantageously act as an actuator, which may include an end portion  51  and a tubular body  52 . Advantageously, the pivot  50  may be supported by the end portion  16  of the first fixed tubular half-shell  12 . 
     The end portion  51  of the pivot  50  will allow the coaxial coupling between the same and the second movable tubular half-shell  13 , so that the latter and the pivot  50  unitary rotate between the open and the closed positions of the second movable tubular half-shell  13 . 
     To this end, in a preferred, not exclusive embodiment, the end portion  51  of the pivot  50  may include an outer surface  53  having a predetermined shape which is coupled, preferably in a removable manner, with a countershaped surface  17  of the second movable tubular half-shell  13 . 
     In a preferred, not exclusive embodiment, shown for example in  FIG. 7 , the shaped surface  53  may include a plurality of axial projections, susceptible to engage corresponding recesses of the countershaped surface  17 . 
     Preferably, the shaped surface  53  of the pivot  50  and the countershaped surface  17  of the second tubular half-shell  13  may be configured so as to allow the selective variation of the mutual angular position thereof. 
     In this way, it will be possible to change the mutual angular position of the connecting plates  14 ,  15  according to needs in such a manner that, for example, they may be perpendicular to each other in the closed position of the closing element D, as shown e.g. in  FIG. 38   th.    
     Suitably, the plunger member  30  and the pivot  50  may be operatively connected to each other through the elongated cylindrical element  60 , so that the rotation of the latter about the axis X corresponds to the sliding of the former along the same axis X and vice-versa. 
     To this end, the elongate element  60  may include a first cylindrical end portion  61  inserted within the working chamber  20  and mutually connected with the plunger member  30  and a second end portion  62  external to the working chamber  20  and sliding within the tubular body  52  of the pivot  50 . 
     The connection between the elongate cylindrical element  60  and the plunger member  30  may be susceptible to make unitary these elements, so that they may define a slider movable along the axis X. 
     Advantageously, the tubular portion  52  of the pivot  50  may have an internal diameter Di′ substantially coincident with the diameter D″′ of the elongated cylindrical element  60 . 
     The elongated cylindrical element  60  may therefore be slidable along the axis X unitary with the plunger member  30 . In other words, the elongated cylindrical element  60  and the pivot  50  may be coupled together in a telescopic manner. 
     Moreover, as better explained later, depending on the configuration of the guide cam slots  81  of the bushing  80  the cylindrical elongated element  60  with its plunger member  30  may or may not be rotatably locked in the working chamber  20  to prevent rotation around axis X during its sliding along the latter. 
     Therefore, the plunger member  30  may slide along the axis X between an end-stroke position proximal to the pivot  50 , corresponding to one of the open and closed position of the second movable tubular half-shell  13 , and an end-stroke position distal from the pivot  50 , corresponding to the other of the open and closed position of the second movable tubular half-shell  13 . 
     To allow the mutual movement between the plunger member  30  and the pivot  50 , the tubular body  52  of the latter may include at least one pair of grooves  70 ′,  70 ″ equal to each other angularly spaced by 180°, each comprising at least one helical portion  71 ′,  71 ″ wound around the axis X. The grooves  70 ′,  70 ″ may be communicating with each other to define a single passing-through actuating member  72 . 
     In  FIGS. 16 and 17  an embodiment of passing-through actuating member  72  is shown. 
     Suitably, the at least one helical portion  71 ′,  71 ″ may have any inclination, and may be right-handed, respectively left-handed. Preferably, the at least one helical portion  71 ′,  71 ″ may be wound for at least 90° around the axis X, and even more preferably for at least 180°. 
     Advantageously, the at least one helical portion  71 ′,  71 ″ may have a helical pitch P of 20 mm to 100 mm, and preferably of 30 mm to 80 mm. 
     In a preferred, not exclusive embodiment, each of the grooves  70 ′,  70 ″ may be formed by a single helical portion  71 ′,  71 ″ which may have constant inclination or helical pitch. 
     Conveniently, the actuating member  72  may be closed at both ends so as to define a closed path having two end blocking points  74 ′,  74 ″ for the pin  73  sliding therethrough, the closed path being defined by the grooves  71 ′,  71 ″. 
     Irrespective of its position or configuration, the rotation of the actuating member  72  around the axis X allows the mutual movement of the pivot  50  and the plunger member  30 . 
     To guide this rotation, a tubular guide bushing  80  external to the tubular body  52  of the pivot  50  and coaxial thereto may be provided. The guide bushing  80  may include a pair of cam slots  81  angularly spaced by 180°. 
     To allow the mutual connection between the pivot  50 , the elongated element  60  and the guide bushing  80 , the second end portion  62  of the elongated element  60  may include a pin  73  inserted through the passing-through actuating member  72  and the cam slots  81  to move within them. 
     Therefore, the length of the pin  73  may be such as to allow this function. The pin  73  may also define a axis Y substantially perpendicular to the axis X. 
     As a consequence, upon rotation of the passing-through actuating member  72  the pin  73  is moved by the latter and guided by the cam slots  81 . 
     As already described above, the end portion  16  of the first tubular half-shell  12  may be capable of supporting the pivot  50 . The bushing  80 , coaxially coupled with the latter, may in turn be unitary coupled with the first tubular half-shell  12 , preferably at the same end portion  16 , so as to allow the coupling of the first and second tubular half-shell  12 ,  13 . 
     Advantageously, the tubular portion  52  of the pivot  50  may have an external diameter De′ less than or possibly substantially coincident with the internal diameter Di″ of the bushing  80 . 
     Moreover, the end portion  16  of the first tubular half-shell  12  may further include a substantially annular appendix  18  having outer diameter De greater than or substantially coincident with the external diameter De′ of the tubular portion  52  of the pivot  50 , and therefore less than or substantially coincident with the internal diameter Di″ of the bushing  80 . 
     The substantially annular appendix  18  may further have an internal diameter Di substantially coincident with the inner diameter Di′ of the tubular portion  52  of the pivot  50 , and therefore substantially coincident with the diameter D′″ of the elongated cylindrical element  60 . 
     More particularly, the substantially annular appendix  18  may further include a lower surface  21  defining the upper wall of the working chamber  20 , an upper surface  19 ′ facing the lower portion  54  of the tubular portion  52  of the pivot  50 , an inner side surface  19 ″ facing the side wall  63  of the elongated element  60  and a cylindrical outer side surface  19 ′″ facing the inner side wall  83  of the bushing  80  for the unitary coupling thereof with the first tubular half-shell  12 . To this end, for example, the wall  19 ′ may be threaded, while the corresponding coupling portion  85  of the inner wall  83  may be counterthreaded. 
     Preferably, the second half-shell  13  may have a tubular inner side wall  13 ′ facing the outer side wall  82  of the bushing  80  when the same second tubular half-shell  13  is coupled to the first tubular half-shell  12 . 
     Thanks to one or more of the above features, the hinge device  1  has high performance while being extremely simple to manufacture and cost-effective. 
     In fact, the bushing  80  has the double function of guiding the pin  73  and of supporting as a column the second movable tubular half-shell  13  which is coupled to the closing element D. 
     In this way, the vertical component of the weight of the latter is loaded on the stationary support structure S while the horizontal component thereof is distributed over the entire length of the bushing  80 , without minimally loading the moving parts of the hinge device  1  and in particular the pivot  50 . 
     This provides for higher performances with respect to the devices of the prior art. 
     Moreover, the first and/or the second tubular half-shell  12 ,  13  may be made of polymeric material, e.g. polyethylene, ABS or polypropylene, or of metallic material with relatively low mechanical strength, such as aluminum, since their function is predominantly a supporting one and have relatively low wear. 
     This allows minimizing costs and manufacturing times. 
     Further, this allows to minimize or to eliminate the thermal transmission which occur in the hinges or the hydraulic door closer with metal structure, since the latter transmit to the working fluid the changes of the external temperature, which in turn change the viscosity of the same working fluid and, therefore, change the operational parameters set upon installation. 
     On the other hand, the pivot  50  and/or the bushing  80 , which are more stressed during use, may be made of metallic material with a relatively high mechanical strength, for example hardened steel. 
     Moreover, the assembly of the hinge device is exceptionally simple, thus simplifying the manufacturing thereof. 
     As mentioned above, the bushing  80  and the second tubular half-shell  13  may be further coupled each other in a removable manner, for example by sliding the latter onto the former along the axis X and subsequent mutual engagement between the outer shaped surface  53  and the countershaped surface  17 . 
     This greatly simplify the maintenance operations of the closing element D, as the same may be removed from the operative position by simple lifting it, without disassembling the hinge device  1 . 
     In this case, the second tubular half-shell will remain in operative position on the bushing  80  simply thanks to the gravity force. 
       FIGS. 9 a  to 15 c  and 18 a  to 19 c    show, to merely illustrate the invention in a non-limitative manner, some embodiments of the bushing  80 , which differ each other for the configuration of the guide cam slots  81 . 
     In particular,  FIG. 9 a    shows a bushing  80  having guide cam slots  81  that have a first portion  84 ′ extending parallel to the axis X and a subsequent second portion  84 ″ extending perpendicularly thereto. 
     Both portions  84 ′,  84 ″ may have a length sufficient to guide the rotation of the pivot  50 , which is unitary with the second tubular half-shell  13 , for 90° around the axis X. Possibly, a stop portion  145  may also be provided for blocking the pin  73  in the desired position, which in the exemplary embodiment shown is at the end of the second portion  84 ″. 
     This configuration is particularly advantageous in the embodiments of the hinge device  1  that include the elastic means  40 , and in particular the compression spring  41 . 
     Thanks to the particular configuration of the guide cam slots  81 , the spring  41  can be preload with its highest preloading force, so that with the same size the hinge device of the invention has a greater force than the devices of the prior art, or with the same force the hinge device of the invention has a smaller size. 
     In fact, when the pin  73  slides along the first portion  84 ′ extending parallel to the axis X, the pivot  50  in rotation about the same axis X compresses the spring  41  for 90°. When the pin  73  slides along the second portion  84 ″ extending perpendicularly to the axis X, the pivot  50  continues to rotate around the same axis X but does not compress the spring  41 . 
     This allows preloading the spring  41  with its highest preloading force, with the above mentioned advantages. It is self-evident that in this case the spring  41  moves only when the pin  73  slides along the first portion  84 ′. 
     In this case, the bushing  80  may be for example operatively coupled with the pivot shown in  FIG. 16 , wherein the passing-through actuating member  72  consists of a single helical portion  71 ′,  71 ″ having constant inclination or helical pitch wound for 180° around the axis X. 
       FIG. 10 a    shows a bushing  80  having guide cam slots  81  which have a first portion  84 ′ extending parallel to the axis X and a subsequent second portion  84 ″ extending perpendicularly thereto, and differs from the bushing  80  shown in  FIG. 9 a    for the presence of three stop portions  145  along the second portion  84 ″ of the guide cam slots  81 . 
       FIG. 11 a    shows a bushing  80  having guide cam slots  81  which have a first portion  84 ′ extending parallel to the axis X and a subsequent second portion  84 ″ extending perpendicularly thereto, and differs from the bushings  80  shown in  FIGS. 9 a  and 10 a    for the orientation of the same second portion  84 ″ and for the sliding direction of the pin  73  through the guide cam slots  81 . 
     In fact, in this case the spring  41  is susceptible to push up the pin  73 , unlike what occurs in the embodiments shown in  FIGS. 9 a  to 10 c   , in which the spring  41  pulls the pin  73  down. The guide cam slots  81  are therefore configured to guide the pin  73  in its path downwards, so as to load the spring  41 . 
       FIGS. 12 a , 13 a  and 14 a    show bushings  80  having guide cam slots  81  that have a single portion  84  inclined or helical shaped, with predetermined angle or pitch. In this way, there are not intermediate stop points the pin  73  between the closed and the fully open position of the second half-shell  13 . 
     This configuration is extremely advantageous in the case in which the portion  84  has an angle or pitch opposite to the one of the helical portions  71 ′,  71 ″ of the passing-through actuating member  72 . In fact, in this case the vertical component of the reaction force that the pin  73  exerts on the guide cam slots  81  upon the sliding therethrough is added to the one given by the passing-through actuating member  72 . 
     This allow obtaining a hinge device that with the same size has a force greater than the devices of the prior art, or with the same force to obtain a hinge device of smaller size. 
       FIG. 15 a    shows a bushing  80  having guide cam slots  81  having a single portion  84 ′ substantially parallel to the axis X. 
       FIG. 18 a    shows a bushing  80  having guide cam slots  81  that have a first portion  84  and a subsequent second portion  84 ′ extending perpendicularly to the axis X. The first portion  84  may be inclined or helical with predetermined angle or pitch. The angle may be less than 30°, preferably less than 25° and even more preferably close to 20°, and may have angle or pitch opposite to that of the helical portion  71 ′,  71 ″ of the passing-through actuating member  72 . 
     This allows combining the advantages described above, for example for the bushings  80  of  FIGS. 9 a  to 12 a   . In fact, the first portion  84 , with its slight angle allows preloading with the highest preloading force the spring  41 , while the second portion  84 ′ allows maximizing this force upon closing or opening. In practice, a closing element D potentially without blocking points is obtained, except those in correspondence of a possible stop portions  145 , which has high closing or opening force and double speed, at first slow and then fast or vice-versa. Moreover, by acting on the stop screw  90  it is possible to obtain practically any opening or closing angle between 0° and 180°. 
     It is understood that each of the embodiments of the hinge device  1  shown in the  FIGS. 1 to 8   d  and  18  to  42   b  may include any one of the bushings  80  shown in  FIGS. 9 a  to 15 c  and 18 a  to 19 c   , as well as pivots  50  having the at least one helical portion  71 ′,  71 ″ either right-handed or left-handed, without departing from the scope of the invention defined by the appended claims. 
     Regardless of the shape of the cam slots  81 , the latter may be closed at both ends so as to define a closed path having two end blocking points  87 ′,  87 ″ for the pin  73  sliding therethrough. 
       FIGS. 45 a  to 46 b    show further embodiments of the bushing  80 , in which the cam slots  81  may include a first portion  84 ′ and a second portion  84 ″. 
     The first portion  84 ′ may extend substantially parallel to the axis X, as shown in  FIGS. 45 a  and 45 b   , or may be slightly inclined with respect to the same axis X with opposite inclination with respect to that of the grooves  70 ′,  70 ″ of the pivot  50 , as shown in  FIGS. 46 a    and  46   b.    
     On the other hand, the second portion  84 ″ may extend substantially perpendicularly to the axis X. 
     Suitably, the first and the second portion  84 ′,  84 ″ may each have a length sufficient to guide the rotation of the movable tubular half-shell  13  for 90° around the axis X. 
       FIGS. 47 a  to 47 e    show a hinge device  1  that includes the bushing  80  in accordance with  FIGS. 45 a    and  45   b.    
       FIG. 47 a    shows the position completely closed of the closing element D. The pin  73  is in correspondence of the first end blocking point  87 ′. 
       FIG. 47 b    shows the position of the closing element D at 90° with respect to the closed door position. The pin  73  is in correspondence of an intermediate blocking point  87 ″. 
     In correspondence of the latter a first shock-absorbing portion  287 ′ may be provided that extends substantially parallel to the axis X in a direction concordant to the sliding direction of the pin  73  within the first portion  84 ′ to allow a further minimum compression of the spring  41 , for example of 1-2 mm, which may correspond to a further slight rotation of the movable tubular half-shell  13 . In the embodiment shown, the first shock-absorbing portion  287 ′ guides the pin  73  so as to rotate the closing element D from 90°, which position is shown in  FIG. 47 b   , to 120° with respect to the closed door position, as shown in  FIG. 47   c.    
       FIG. 47 d    shows the position of closing element D at 180° with respect to the closed door position. The pin  73  is in correspondence of the second blocking point  87 ″. 
     In correspondence of the latter a second shock-absorbing portion  287 ″ may be provided to guide the pin  73  so as to rotate the closing element D from 180°, which position is shown in  FIG. 47 d   , to 190° with respect to the door closed position, as shown in  FIG. 47   e.    
     Advantageously, the blocking points  87 ′,  87 ″,  87 ″ may include zones of the cam slots  81  against which the pin  73  abuts during its sliding through the same cam slots  81  to block the closing element D during opening and/or closing. 
     It is pointed out that the blocking points  87 ′,  87 ″,  87 ″ are different from the stop portions  145 , and have also different functions. 
     The shock-absorbing portions  287 ′,  287 ″ allow to absorb the shock imparted to the closing element D by the abutment of the pin  73  against the blocking points  87 ′,  87 ″. 
     In fact, this abutment is rigidly transferred to the closing element D, with the consequent unhinging danger thereof. Therefore, the shock-absorbing portions  287 ′,  287 ″ allow a further compression of the spring  41  which absorb the shock of the abutment of the pin  73  against the blocking points  87 ″,  87 ″, thus avoiding the above danger. 
     This configuration is particularly advantageous in case of aluminum frames, so as to avoid the reciprocal torsion of the closing element D and the stationary support structure S. 
     Suitably, the shock-absorbing portions  287 ′,  287 ″ may have a length sufficient to allow a further minimum rotation of the movable element  11  of 5° to 15° around the axis X. 
     A further advantage of the above configuration is that even if the closing element D rotates beyond the open position determined by the blocking points  87 ″,  87 ′, the spring  41  returns the same closing element D in the predetermined open position. Therefore, the action of the shock-absorbing portions  287 ′,  287 ″ does not affect the predetermined open position of the closing element D, which therefore is maintained over time even in the case of several shock-absorbing actions. 
     It is understood that both the blocking points that the shock-absorbing portions of the cam slots  81  may be in any number without departing from the scope of the appended claims. 
     In order to allow a user to adjust the opening and/or closing angle of the second tubular half-shell  13 , at least one stop screw  90  may be provided having a first end  91  susceptible to selectively interact with the second end portion  62  of the elongated element  60  and a second end  92  to be operated from the outside by a user to adjust the stroke of the same elongated element  60  along the axis X. 
     Preferably, the at least one stop screw  90  can be inserted within the pivot  50  in correspondence of the end portion  51  thereof, so as to slide along the axis X between a rest position spaced from the second end portion  62  of the elongated element  60  and a working position in contact therewith. 
     In this way, it is possible to adjust the hinge device  1  in any manner. 
     For example,  FIGS. 4 b  and 33 b    show embodiments of the hinge device  1  in which the stop screw  90  is in working position to prevent the pin  73  to slide through the second portion  84 ″ of the guide cam slot  81  of the bushing  80 . Thanks to this configuration, in such embodiments the pin  73  slides between the closed and fully open position of the second half-shell  13  without any intermediate blocking point, which fully open position in this embodiments shows an angle of approximately 90° between the connecting plates  14 ,  15 . 
     In some embodiments, such as the ones shown in  FIGS. 30 to 34   c , a pair of stop screws  90 ,  90 ′ may be provided, which are placed in correspondence of the respective upper and lower ends  2 ,  3  of the hinge device  1 . 
     The top stop screw  90  may have the above described features. 
     The lower stop screw  90 ′ may have a first end  91 ′ susceptible to interact selectively with the plunger member  30  and a second end  92 ′ to be operated from the outside by a user. 
     As mentioned above, some embodiments of the hinge device  1  may include a working fluid, such as those shown in  FIGS. 1 to 8   d  and  20  to  29   b.    
     Such embodiments may include the elastic means  40 , such as those shown in  FIGS. 1 to 8   d ,  20  to  21   c  and  26  to  29   c , or not include them, such as the one shown in  FIGS. 22 to 25   c.    
     In the embodiments that include the elastic means  40 , the latter will ensure automatic closing or the opening of the closing element D, such as in those shown in  FIGS. 1 to 8   d ,  20  to  21   c  and  26  to  29   c , or simply allow the plunger member  30  to return from one of the distal or proximal positions towards the other of the distal or proximal positions without ensuring the automatic closing or opening of the closing element D. 
     In the first case the elastic means  40  may include a thrust spring  41  of relatively high force, in the second case they may include a reset spring having a relatively low force. 
     In the first case, the hinge device  1  acts as a hydraulic hinge or door closer with automatic closure, while in the second case the same hinge device  1  acts as a hydraulic damping hinge. 
     It is understood that the use of the spring  41  in the damping hinge device  1  is purely optional. For example, in the embodiment of the hinge device  1  shown in  FIGS. 22 to 25   b  the spring is not employed. 
     This allows to use the entire length of the working chamber  20 , thus minimizing the bulkiness. Advantageously, in embodiments that include the working fluid, the working chamber  20  may include one or more sealing elements  22  to prevent the leakage thereof, for example one or more O-rings. 
     The plunger member  30  may separate the working chamber  20  in at least one first and at least one second variable volume compartment  23 ,  24  fluidly communicating each other and preferably adjacent. Suitably, when present, the elastic counteracting means can be inserted in the first compartment  23 . 
     To allow the passage of the working fluid between the first and the second compartments  23 ,  24 , the plunger member  30  may comprise a passing-through opening  31  and valve means, which may include a non-return valve  32 . 
     Advantageously, the non-return valve  32  may include a disc  33  inserted with minimum clearance in a suitable housing  34  to move axially along the axis X. 
     Depending on the direction in which the non-return valve  32  is mounted, it opens upon the opening or closing of the closing element D, so as to allow the passage of the working fluid between the first compartment  23  and second compartment  24  during one of the opening or closing of the closing element D and to prevent backflow thereof during the other of the opening or the closing of the same closing element D. 
     For the controlled backflow of the working fluid between the first compartment  23  and the second compartment  24  during the other of the opening or closing of the closing element D, a suitable hydraulic circuit  100  may be provided. 
     Suitably, the plunger member  30  may include, or respectively may consists of, a cylindrical body tightly inserted in the working chamber  20  and facing the inner side wall  25  thereof. The hydraulic circuit  100  may at least partially lie within the first tubular half-shell  12 , and may preferably include a channel  107  external to the working chamber  20  which defines an axis X′ substantially parallel to the axis X. 
     Advantageously, the hydraulic circuit  100  may include at least one first opening  101  in the first compartment  23  and at least one further opening  102  in the second compartment  24 . Depending on the direction in which is mounted the valve  32 , the openings  101 ,  102  may act respectively as inlet and outlet of the circuit  100  or as outlet and inlet thereof. 
     The first tubular half-shell  12  may have at least one first adjusting screw  103  having a first end  104  which interacts with the opening  102  of the hydraulic circuit  100  and a second end  105  which can be operated from outside by a user to adjust the flow section of the working fluid through the same opening  102 . 
     In the embodiments shown in  FIGS. 1 to 8   d  and  20  to  29   c , the valve  32  opens upon opening of the closing element and closes upon closing thereof, thus forcing the working fluid to flow back through the hydraulic circuit  100 . In these conditions, the opening  101  acts as inlet of the hydraulic circuit  100  while the opening  102  acts as outlet thereof. 
     Suitably, the outlet  102  may be fluidly decoupled from the plunger member  30  during the whole stroke thereof. The screw  103  may have the first end  104  which interacts with the opening  102  to adjust the closing speed of the closing element. 
     In some preferred but not exclusive embodiments, for example those shown in  FIGS. 1 to 8   d  and  22  to  25   c , the hydraulic circuit  100  may include a further opening  106  in the second compartment  24 , which in the above mentioned example may act as a second outlet in the second compartment  24  for the circuit  100 . 
     Therefore, the plunger member  30  may be in a spatial relationship with the openings  102 ,  106  such as to remain fluidly decoupled from the opening  102  for the entire stroke of the plunger member  30 , as mentioned above, and such as to remain fluidically coupled with the opening  106  for a first part of the stroke thereof and to remain fluidly decoupled from the same opening  106  for a second part of the stroke of the plunger member  30 . 
     In this way, in the above embodiment the closing element D latches towards the closed position when the second tubular half-shell  13  is in close to the first tubular half-shell  12 , or in any event when the closing element D is in the proximity of the closed position. 
     In the case of valve  32  mounted on the contrary, i.e. that opens upon the closing of the closing element and closes upon the opening thereof, the circuit  100  configured as described above allows to have two resistances during opening, a first resistance for a first angular portion of the opening of the closing element D and a second resistance for a second angular portion of the opening thereof. 
     In this case, upon opening of the closing element D the working fluid flows from the second compartment  24  to the first compartment  23  through the channel  107 , by entering through the openings  102 ,  106  and exiting through the opening  101 . Upon the time of closing of the closing element D the working fluid flows from the first compartment  23  to second compartment  24  through the valve  32 . The first resistance during opening is obtained when the plunger member  30  is fluidly coupled with the opening  106  during the first part of the stroke thereof, while the second resistance during opening is obtained when the plunger member  30  is fluidly decoupled from the same opening  106  for the second part of the stroke thereof. 
     In some preferred but not exclusive embodiments, for example those shown in  FIGS. 1 to 5   d , the channel  107  may include a substantially cylindrical seat  108  in which a regulating member  130  can be inserted, the regulating member  130  comprising an operative end  131  and a rod  132  coupled thereto. The rod  132  may define a longitudinal axis X″ mutually parallel or coincident with the axis X′ of the channel  107 . 
     As particularly shown in  FIG. 8 e   , the seat  108  may have a first cylindrical portion  109 ′ in correspondence of the opening  102  and a second cylindrical portion  109 ″ in correspondence of the opening  106 . 
     To enable the mutual coupling between the regulating member  130  and the seat  108 , the rod  132  of the regulating member  130  may include a first and a second threaded portion  133 ′,  133 ″, while the seat  108  may be counterthreaded in correspondence of the first cylindrical portion  109 ′. Alternatively, instead of the first threaded portion  133 ′ the regulating member  130  may include a ring of the Seeger type inserted trough a first countershaped cylindrical portion  109 ′. 
     However, the second cylindrical portion  109 ″ may advantageously be smooth, that is free of counterthread. Therefore, the first cylindrical portion  109 ′ of the seat  108  may have a maximum diameter Dp 1  greater than the one Dp 2  of the second cylindrical portion  109 ″. 
     The rod  132  may have an outer surface  134  faced to both the openings  101  and  106 , which in a first embodiment shown for example in  FIGS. 8 a  to 8 f    may essentially have a substantially cylindrical area  135 ′ and a flat area  135 ″ opposite thereto. 
     More particularly, the outer surface  134  may include a third and a fourth cylindrical portion  136 ′,  136 ″ and a first and a second flat portion  137 ′,  137 ″ opposed thereto which are respectively faced to the first and the second cylindrical portion  109 ′,  109 ″ of the seat  108 . 
     Suitably, the maximum diameter Dp 4  of the fourth cylindrical portion  136 ″ is greater than the maximum diameter Dp 3  of the third cylindrical portion  136 ′ and may substantially coincide with the maximum diameter Dp 2  of the second cylindrical portion  109 ″ of the seat  108 . Therefore, the maximum diameter Dp 3  of the third cylindrical portion  136 ′ is less than the maximum diameter Dp 1  of the first cylindrical portion  109 ′. 
     The shape of the rod  132  may be such that the substantially cylindrical area  135 ′ extends beyond the plane of symmetry of the regulating member  130 . Therefore, the first and the second flat portions  137 ′,  137 ″ may have respective maximum widths h′, h″ lower than the respective maximum diameters Dp 3 , Dp 4  of the third and fourth cylindrical portions  136 ′,  136 ″. 
     Advantageously, the first threaded portion  133 ′, which may be interposed between the third and fourth cylindrical portions  136 ′,  136 ″, may in turn include a first cylindrical zone  138 ′ in correspondence of the third and fourth cylindrical portions  136 ′,  136 ″ and a first planar zone  138 ″ in correspondence of the first and second flat portions  137 ′,  137 ″. 
     On the other hand, the second threaded portion  133 ″, which may be interposed between the operative end  131  and the third cylindrical portion  136 ′ of the rod  132 , may in turn include a second cylindrical zone  139 ′ in correspondence of the third cylindrical portion  136 ′ and a second planar zone  139 ″ in correspondence of the first flat portion  137 ′. 
     Thanks to one or more of the above features, the regulating member  130  easily allows to adjust the flow section of the opening  106  when, as in this case, the limited bulkiness of the hinge device  1  does not allow the use a “classical” radial screw. The regulating member  130  allows for example to adjust the force by which the closing element D latches towards the closed position, as well as to avoid the latch action, as well as to adjust or to avoid one of the resistances during opening. 
     By acting on the operative end  131 , for example by using a screwdriver, a user can promote the rotation of the rod  132  around the axis X″ between a working position, shown for example in  FIGS. 8 b  and 8 d   , and a rest position, shown for example in  FIGS. 8 a    and  8   c.    
     As shown in these figures, in the working position the third and fourth cylindrical portions  136 ′,  136 ″ are respectively faced to the first and second openings  101 ,  106 , so that the outer surface  134  of the rod  132  selectively obstruct the opening  106  while the other opening  101  will remain in fluid communication with the channel  107  and the opening  102  regardless of the rest or working position of the rod  132 . 
     On the other hand, in the rest position the first and the second flat portions  137 ′,  137 ″ remain respectively faced to the openings  101 ,  106 , so that the working fluid is free to pass between the first and the second volume variable compartments  23 ,  24  through the channel  107 . 
     It is therefore apparent that regardless the rest or working position of the regulating member  130  the opening  101  is always in fluid communication with the opening  102 , while depending from the rest or the working position of the regulating member  130  the opening  106  remains respectively in fluid communication or not with the same opening  102 . 
     Consequently, when the adjustment member  130  is in the rest position the opening  101  remains in fluid communication with both openings  102  and  106 , so as to allow for example the above mentioned latch action or double resistance during opening, while in the working position, the opening  101  remains in fluid communication exclusively with the opening  102 , so as to exclude for example the above mentioned latch action or double resistance during opening. 
     In an alternative embodiment, shown in  FIGS. 48 a    to  50 , the regulating member  130  may include an axial blind hole  240 , while the third and fourth cylindrical portion  136 ′,  136 ″ may include a respective first and second passing-through hole  250 ′,  250 ″ in mutual fluidic communication with the axial blind hole  240 , as particularly shown in  FIG. 50 . 
     The operation of this embodiment is similar to that of the above described embodiment shown in  FIGS. 8 a    to  8   f.    
     As shown in  FIGS. 48 a  and 48 b   , when the rod  132  is in the rest position, as shown in  FIG. 48 b   , the second passing-through hole  250 ″ remains fluidly coupled with the opening  106  and when the rod  132  is in working position, as shown in  FIG. 48 a   , the second passing-through hole  250 ″ remains fluidly decoupled from the opening  106 , so as to selectively obstruct it. 
     Suitably, the first passing-through hole  250 ′ may be susceptible to put in mutual fluid communication the opening  101  and the opening  102  through the channel  107  regardless of the rest or working position of the rod  132 . In fact, when the latter is in the working position, the working fluid flows in correspondence of the cylindrical portion  136 ′ and passes through the passing-through hole  250 ′. 
     In some preferred but not exclusive embodiments, for example those shown in  FIGS. 1 to 8 and 22 to 29   b , the channel  107  may pass through the connecting plate  14 . 
     Advantageously, in such embodiments the regulating member  130  can be inserted at one end of the channel  107 , for example the bottom one, to selectively obstruct the opening  106 , while the adjustment screw  103  can be inserted at the other end of the same channel  107 , for example the upper one, to selectively obstruct the opening  102 . 
     More particularly, the regulating member  130  and the adjustment screw  103  can be inserted into the channel  107  so that the axis X′ of the latter coincides with the fourth axis X″ of the regulating member  130  and with the fifth axis X′ of the adjusting screw  103 . It is understood that the axes X′, X″ and X′″ are substantially parallel to the axis X. 
     In this way, the operative end  131  of the regulating member  130  and the operative end  105  of the adjusting screw  103  can be accessible by the user at opposite sides with respect to a median plane .pi.M, shown for example in  FIG. 3 a   , passing through the connecting plate  14  and substantially perpendicular to the axes X′, X″ and X″′, and consequently perpendicular to the axis X. 
     Thanks to this configuration, it is possible to obtain both the adjustment of the closing and/or opening speed of the closing element D (by acting on the adjustment screw  103 ) and the force of the latch action and/or of the resistances during opening (by acting on the regulating member  130 ) with minimum bulkiness and round shapes, typical of the “Anuba”-type hinges. 
     In some preferred but not exclusive embodiments, for example those shown in  FIGS. 20 to 21   c  and  43   a  to  44   c , the closing cap  27  of the working chamber  20  may include a passing-through duct  100 ′ and a substantially annular peripheral groove  29  around the substantially cylindrical side wall  28  of the same cap  27 . Once the cap  27  is inserted in the working chamber  20 , its substantially cylindrical side wall  28 , and therefore the peripheral groove  29 , remains faced the inner side wall  25  of the same working chamber  20 . 
     Conveniently, the peripheral groove  29 , which may have facing side walls  29 ′,  29 ″ and a bottom wall  29 ″′, may be open at the top so that the bottom wall  29 ′ and the inner side wall  25  of the working chamber  20  remain directly faced each other. 
     The passing-through duct  100 ′ may include a pair of first branches  140 ′,  140 ″ having respective openings  100  fluidly communicating with the channel  107  through the peripheral groove  29  and the opening  101  passing through the second half-shell  12  and a second branch  141  with an opening  100 ′ fluidly communicating with the first compartment  23 . 
     A central manifold  100 ′ may lye in a substantially central position along the X axis between the first branches  140 ′,  140 ″ and the second branch  141 , which central manifold  100 ′ is therefore in fluid communication with both the channel  107  that the first compartment  23 . 
     Advantageously, the cap  27  may include the adjustment screw  103  preferably in axial position along the axis X. The screw  103  may have the end  104  interacting with the central manifold  100 ′ and the operative end  105  to be operated from the outside by a user to adjust the flow section of the working fluid therethrough. 
     In the embodiment shown in  FIGS. 20 to 21   c  and  43   a  to  44   c , in which the valve means  32  are configured to allow the passage of the working fluid between the first compartment  23  and second compartment  24  during the opening of the closing element D and to prevent the backflow thereof during the closing of the same closing element D, the single screw  103  is susceptible to adjust the closing speed of the closing element D. 
     Thanks to one or more of the above features, it is possible to obtain a simple and quick adjustment even in hinge devices  1  having minimum dimensions or completely round shaped, where it is not possible to insert screws neither axially nor radially. 
     Moreover, the peripheral annular channel  29  allows simplifying the mounting of the hinge device  1 , while improving the reliability thereof. 
     As mentioned above, some embodiments of the hinge device  1  may include the elastic counteracting means  40 , such as those shown in  FIGS. 1 to 8   d ,  20  to  21   c  and  26  to  34   c.    
     Such embodiments may include the working fluid, such as those shown in  FIGS. 1 to 8   d ,  20  to  21   c  and  26  to  29   c , or not, such as that shown in  FIGS. 30 to 34   c.    
     In the latter case, the hinge device  1  acts as a purely mechanical opening/closing hinge. 
     In some preferred but not exclusive embodiments, for example those shown in  FIGS. 1 to 8   d ,  20  to  21   c  and  30  to  34   c , the spring  41  and the plunger member  30  may be coupled to each other so that the former  41  is in the position of maximum elongation in correspondence of the end-stroke distal position of the latter. In this case, the spring  41  may be interposed between the cylindrical portion  52  of the pivot  50  and the plunger member  30 . 
     In order to minimize friction between the moving parts, at least one antifriction member may be provided, such as an annular bearing  110 , interposed between the pivot  50  and the end portion  16  of the first tubular half-shell  12  for the supporting thereof. 
     In fact, in the above mentioned embodiment the pin  73  will be pulled downwards, thus urging downwards also the pivot  50  which therefore rotate about the axis X on the bearing  110 . Suitably, the pin loads the stresses due to the action of the spring  41  on the latter bearing  110 . 
     In other preferred but not exclusive embodiments, such as the one shown in  FIGS. 26 to 29   c , the spring  41  and the plunger member  30  may be coupled to each other so that the first is in the position of maximum elongation in correspondence of the proximal end-stroke position of the plunger member  30 . In this case, the spring  41  may be interposed between the bottom wall  26  of the working chamber  20  and the plunger member  30 . 
     In this case, to minimize friction between the moving parts at least one antifriction member may be provided, for example a further annular bearing  112 , interposed between the pivot  50  and the upper wall  121  of a sleeve  120  susceptible to retain the pivot  50 , which sleeve  120  being unitary coupled externally to the bushing  80  coaxially therewith. 
     In fact, with the above configuration the pin  73  is urged upwards, by urging in turn upwords the pivot  50  which therefore rotate about the axis X on the bearing  111 . The retaining sleeve  120  may for example be screwed into the lower portion of the bushing  80 , so as to retain the pivot  50  in the operative position. 
     In any case, the hinge device  1  can be configured to minimize friction between the moving parts. 
     For this purpose, at least one antifriction member may be provided, for example a further annular bearing  112 , interposed between the bushing  80  and the second tubular half-shell  13 , in such a manner that the latter rotates around the axis X on the bearing  112 . 
     Therefore, the bushing  80  may suitably have a central opening  86  in the proximity of the upper portion  87  for insertion of the end portion  51  of the pivot  50 . More particularly, the bushing  80  and the pivot  50  may be mutually configured so that once the pivot  50  is inserted within the bushing  80  the end portion  51  of the former passes through the central opening  86  of the latter. 
     To this end, the bushing  80  may have a height h substantially equal to the sum of the height of the bearing  110 , the tubular body  52  of the pivot  50  and its coupling portion  85  with the outer side wall  19 ″′ of the annular appendix  18 . 
     Therefore, the bearing  112  rests on the upper portion  87 , so that the closing element does not load at all the pivot  50  during its rotation about the axis X. In fact, the weight of the closing element D is loaded on the bearing  112 . 
     Moreover, the position of the pivot  50  within the bushing  80  prevents misalignment and/or slipping out of the same pivot  50  due to forces pushing the same upwards, for example in the case of a user that force in closing the closing element D. In fact, in this case the pivot  50  impacts against the upper portion  87  of the bushing  80 , such as clearly visible in  FIGS. 32 b  and 33 b   , thus remaining in its original position. 
     Moreover, the bushing  80  and the second tubular half-shell  13  may be preferably in a spatial relationship to each other such that the second tubular half-shell  13  once coupled with the bushing  80  remains spaced from the first tubular half-shell  12 , for example by a distance d of few tenths of a millimeter. 
     From the above description, it is apparent that the invention fulfils the intended objects. 
     The invention is susceptible to many changes and variants. 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 defined by the appended claims.