AU2013100469A4 - Hinge assembly for self-closing doors or the like, particularly glass doors - Google Patents

Abstract

Hinge assembly for self-closing doors or the like, particularly glass doors Abstract A hinge assembly (1) for coupling a door (P) and a door frame or a floor, the hinge assembly (1) comprising a hydraulically damping hinge (72) and a closing hinge (71) for self-closing the door (P). Both the hydraulically damping hinge (72) and the closing hinge (71) are coupled to the door (P) at longitudinally separated positions. WO 20071125524 PCT/IB2007l051663 2 90 88 15 972 "825 x, -------- 852 ~82' 2 18 5 20/17 -- - - - -~ 38 33 2/ 24

Description

AUSTRALIA Patents Act 1990 Innovation Patent Specification Title: Hinge assembly for self-closing doors or the like, particularly glass doors Applicant(s): DIANORA GOSIO Inventor(s): BACCHETTI, Luciano Agent: OTTERS Patent & Trade Mark Attorneys The following is a full description of the invention which sets forth the best method known to the applicant of performing it.

2 Hinge assembly for self-closing doors or the like, particularly glass doors 5 Related applications This application is related to Australian patent application 2007245248 entitled "Hinge structure for self-closing doors or the like, particularly glass doors or the like, and assembly incorporating such structure", filed 3 May 2007 in the name of Dianora Gosio. 10 This application is also related to Italian patent applications V12006A000307 filed 19 October 2006, V12006A000216 filed 11 July 2006 and V12006A000131 filed 3 May 2006, each in the name of Dianora Gosio. The entire contents of the above noted specifications are hereby incorporated by reference as if fully set forth herein. 15 Field of the invention The present invention relates to hinge structures and suspension hardware for doors. In particular the present invention relates to a hinge assembly for self-closing doors. The hinge assembly can be utilised for self-closing doors, windows or shutters, whether 20 horizontally or vertically oriented, and particularly glass doors. Background of the invention Hinge structures for self-closing doors, and particularly glass doors are known in the art. 25 These prior art hinge structures comprise, as is known, a stationary element to be fixed to the frame of a door, a first movable element to be attached to the door and pivotally mounted to the stationary element for rotating about a longitudinal axis between an open door position and a closed door position. 30 These prior art hinge structures further comprise means for self-closing returning the door to a closed position during opening thereof. Such prior art hinge structures suffer from certain well-recognised drawbacks.

3 A first drawback is their bulky size, heavy weight and high cost, resulting from many different parts, which further complicates their assembly and maintenance. Furthermore, they tend to exhibit poor versatility and require replacement or adjustment as 5 the door or frame on which they are mounted changes. Also, the prior art hinge structures typically do not assure controlled motion of the door during opening and closing. This problem is particularly prevalent with glass doors, for which closing and opening must be smooth, to avoid irreversible damages to the door itself. 10 However, the behaviour of these prior art structures is highly influenced by the mass of the door on which they are mounted. Furthermore, in operation, the prior art hinge structures are often subjected to variations in the closing position, which can be inconvenient for the user and may result in higher 15 maintenance costs. Object of the Invention It is an object of the present invention to substantially overcome or at least ameliorate one or more of the above disadvantages, or to provide a useful alternative. 20 Summary of the invention The present invention provides a hinge assembly for coupling a door and a door frame or a floor, the hinge assembly comprising: a hydraulically damping hinge; and 25 a closing hinge for self-closing the door, wherein both the hydraulically damping hinge and the closing hinge are adapted to be coupled to the door at longitudinally separated positions, further wherein the hydraulically damping hinge comprises: a first stationary element attachable to the frame or the floor and pivotally mounted to 30 a first movable element attachable to the door for rotating about a longitudinal axis between an open door position and a closed door position; the first movable element including a first operating chamber extending parallel to a transverse axis substantially orthogonal to the longitudinal axis; the first stationary element including a first pin extending along the longitudinal axis, 4 the first pin including a first cam element having a first contact surface; a first plunger element movable within the first operating chamber along the transverse axis between a compressed position and an extended position, the first plunger element having a first front face which is adapted to engage the first contact surface of the 5 first pin; wherein the first operating chamber further includes a first spring for urging the first front face of said first plunger element against the first contact surface of the first cam element of the first pin; wherein the first operating chamber further includes first hydraulic damping means 10 acting on the first movable element to damp the hydraulically damping hinge as it approaches the closed position; wherein the first plunger element has a first side wall and a first end wall defining the first front face, the first end wall being designed to separate the first operating chamber into a first variable volume compartment and a second variable volume compartment which are 15 in fluid communication with each other. The closing hinge is preferably adapted to generate a torque to cause the door to pivot toward a closed position about the longitudinal axis. The hydraulically damping hinge is preferably adapted to operate on the first movable element to hydraulically damp the 20 movement produced by the closing hinge. The closing hinge preferably includes a second pin extending along the longitudinal axis, the second pin including a second cam element having a second contact surface, wherein the second contact surface is substantially perpendicular to the first contact surface. 25 The closing hinge preferably includes a second plunger element movable within a second operating chamber between a compressed position and an extended position, the second plunger element preferably having a second front face which is adapted to engage the second contact surface of the second pin. By this arrangement, in the door open position, 30 the first contact surface and the first front face of the hydraulically damping hinge are mutually parallel and the second contact surface and the second front face of the closing hinge are mutually orthogonal; while in the door closed position, the first contact surface and the first front face of the hydraulically damping hinge are mutually orthogonal and the second contact surface and the second front face of the closing hinge are mutually parallel.

5 The second operating chamber preferably further includes a second spring for urging the second plunger element against the second contact surface. By this arrangement, in the door open position, the first spring of the hydraulically damping hinge is in an extended position and the second spring of the closing hinge is in a compressed position; while in the 5 door closed position, the first spring of the hydraulically damping hinge is in a compressed position and the second spring of the closing hinge is in an extended position. The hinge assembly according to one embodiment allows the controlled motion of the door with which it is connected. 10 The hinge assembly can preferably support doors and windows of heavy weight without changing their behaviour and without requiring any adjustment. The hinge assembly preferably has a minimized number of parts and can be adapted to multiple shells of different shapes and sizes. 15 A preferred embodiment provides a hinge assembly that can keep its closed position unaltered with time. The hinge assembly according to a preferred embodiment preferably offers no or little 20 resistance to the closing motion even when pulled abruptly. According to one embodiment the closing means may be held in the first operating chamber, and the hydraulic damping means may be held either in the first operating chamber or in a second operating chamber, other than the first chamber. 25 Brief Description of the Drawings Further features and advantages of the hinge assembly will be more apparent upon reading the detailed description of few preferred, non-exclusive embodiments of an hinge structure and hinge assembly, which is described as non-limiting examples with the help of the 30 annexed drawings, in which: FIG. 1 is a plan view of a door with a first embodiment of a hinge structure mounted thereto; 6 FIG. 2 is an axonometric view of the first embodiment of the hinge structure, in the closed door position; FIG. 3 is a sectional side view of the hinge structure of FIG. 2, taken along a plane A-A; FIG. 4a is an exploded view of the hinge structure of FIG. 2, in a first preferred, non 5 exclusive configuration; FIG. 4b is an exploded view of the hinge structure of FIG. 2, in a second preferred, non exclusive configuration; FIGS. 5a and 5c are axonometric views of the closing means 4 of the hinge structure; FIG. 5b is a sectional view of a few details of FIG. 5a, as taken along a plane M-M; 10 FIG. 6 is an enlarged view of certain details of the hinge structure of FIG. 5; FIGS. 7a and 8a are sectional views of the hinge structure of FIG. 2, as taken along a plane B-B in the closed door and open door positions respectively; FIGS. 7b and 8b are sectional views of the hinge structure of FIG. 2 taken along a plane B-B in partly open door conditions, during door opening and door closing respectively; is FIGS. 9 and 10 are sectional views of alternative embodiments of the hinge structure of FIG. 2 taken along a plane A-A ; FIG. 11 is an axonometric view of a second embodiment of a hinge structure; FIG. 12 is a sectional view of the structure of FIG. 11, taken along a plane C-C; FIG. 13 is a sectional view of the structure of FIG, 11, taken along a plane D-D; 20 FIG. 14 is an exploded view of the structure of FIG. 11; FIG. 15 is an exploded view of the first and second plunger elements of the structure of FIG. 11; FIG. 16 is an exploded view of certain details of FIG. 11 , in which the stationary element is indicated by dashed lines; 25 FIG. 17 is a sectional view of a first preferred non exclusive embodiment of the pin of the structure of FIG. 11; FIG. 18 is a sectional view of the pin of FIG. 17, taken along a plane E-E; FIG. 19 is a sectional view of a second preferred non exclusive embodiment of the pin of the structure of FIG. 11; 30 FIGS 20 to 23 are sectional views of the device of FIG. 11, taken along planes F-F and G-G, in the closed door position, in a partly open position during door opening, in the open door position and in a partly open position during door closing respectively. FIG. 24 is a view of a door with a hinge assembly mounted thereon; FIG. 25 is an axonometric view of the assembly; 7 FIG. 26 is an axonometric view of the assembly in which the first and hydraulically damping hinges are shown in exploded configuration; FIG. 27 is an axonometric view of the assembly in which the first and second stationary elements are shown by dashed lines; 5 FIG. 28 is a view of the assembly in which the first and hydraulically damping hinges are cut away along respective planes H-H, H'-H' FIG. 29 is a view of the assembly in which the first and hydraulically damping hinges are cut away along respective planes L-L, L'-L' and in which they are in the closed door position; FIG. 30 is a view of the assembly in which the first and hydraulically damping hinges are cut 10 away along respective planes L-L, L'-L', and in which they are in an intermediate opening position; FIG. 31 is a view of the assembly in which the first and hydraulically damping hinges are cut away along respective planes L-L, L'-L' and in which they are in the open door position; FIG. 32 is a view of the assembly in which the first and hydraulically damping hinges are cut 15 away along respective planes L-L, L'- L', and in which they are in an intermediate closing position. Detailed description of the preferred embodiments Referring to the above figures, there are shown embodiments of a hinge structure for self 20 closing doors or the like, generally designated by numeral 1, which may be mounted, preferably but without limitation, on glass doors. The hinge structure 1 generally comprises a stationary element 2 to be fixed to a frame T of a door P and a movable element 3 to be fixed to the door P. The movable element 3 is 25 pivotally mounted to the stationary element 2 for rotating about a first longitudinal axis X between an open door position and a closed door position. The hinge structure 1 further comprises closing means, generally designated by numeral 4 and hydraulic damping means, generally designated by numeral 5, which may consist in the 30 embodiments described herein without limitation, of a predetermined amount of oil. The closing means 4 operate on the first movable element 3 for automatically returning the door to the closed position during opening, and the hydraulic damping means 5 operate on 8 such element 3 to oppose and damp the movement produced by the closing means 4. The closing means 4 and the hydraulic damping means 5 may be held in at least one first operating chamber 6 within the stationary element 2. 5 By this arrangement, a hinge structure can be obtained that allows controlled pivotal motion of the door. This means that, when the door is in an open door position, the closing means 4 will operate on the movable element 3 and generate a torque to cause the door P to rotate to its closed position about the axis X. On the other hand, at each time, the hydraulic io damping means 5 will operate on the movable element 3 to generate a resistant torque opposite to the torque generated by the closing means 4. The hinge structure provides no or little resistance to the closing motion even when pulled abruptly. This will prevent any injury to careless users, particularly children. Regardless of 15 the force exerted on the door, the latter will always return smoothly to the closed door position, thereby providing a childproof safety. The hinge structure 1 is also particularly efficient and cost effective, as it can keep its initial characteristics unaltered with time even when used in severe conditions with high moisture 20 content and passage of moisture. Furthermore, because the closing means 4 and the hydraulic damping means 5 are wholly contained in at least one first operating chamber 6 within the stationary element 2, the hinge structure 1 is particularly convenient to handle, and has a small size, and minimized space 25 requirements. Therefore, its installation generally requires no particular masonry or excavation works. As shown in the annexed figures, the structure 1 is fixed to the frame of a door (or to a wall) along the vertical extension of the door, above the level of the floor or the wall to which the stationary element is fixed. 30 The closing means 4 include a first cam element 11 unitary with the first movable element 3 and having a first substantially flat contact surface 16, and a first plunger element 12 movable within said first operating chamber 6 along a transversal axis Y between a compressed end stroke position, corresponding to the open door position, and an extended 9 end stroke position, corresponding to the closed door position. The plunger element 12 has a front face 17 which contacts and engages the surface 16 of the cam element 11. The first contact surface 16 of the first cam element 11 may be offset with respect to the 5 longitudinal axis X by a predetermined distance g such that the front face 17 of the plunger element 12 in its extended end position is positioned beyond said longitudinal axis X. By this arrangement, excellent control of the closing movement of the door can be achieved. In fact, the offset of the contact surface 16 with respect to the longitudinal axis X allows the io automatic closing of the door. This means that, when the door P is closed, starting from the fully open position, as shown in Figure 8b, 22 and 31, on account of the distance g between the axis X and the surface 16, the front face 17 of the piston element 12 will promptly (after a few degrees of rotation) start to interact with the surface 16, thereby rotating the door P to the closed door position, as shown in Figure 7a, 20 and 29. 15 A first preferred, non exclusive embodiment of the hinge structure is shown in Figures 2 to 8, in which there is only one operating chambers 6 containing the closing means 4 and the hydraulic damping means 5. 20 In this embodiment, as shown in Figures 4a and 4b, the stationary element 2 may be defined by a base 7 to be fixed to the frame T by means of screws to be inserted in the holes 8, 8', 8", 8"', whereas the movable element 3 may in turn comprise two half shells 9, 9' to be clamped together by screws 10, 10'. 25 Advantageously, the closing means 4 may include a cam element 11, better shown in Figure 5a, which is able to pivot about the axis X integrally with the movable element 3 and is adapted to cooperate with a plunger element 12, better shown in Figure 5c, which is longitudinally movable within the operating chamber 6. 30 The term "cam" as used herein is meant to indicate a mechanical member of any shape, which is adapted to turn a circular motion into a straight-line motion. Conveniently, in this embodiment, the plunger element 12 operates along a line Y substantially orthogonal to the one defined by the longitudinal axis X, for minimized space 10 requirement. As particularly shown in Figures 7 and 8, the line Y is defined by the axis of the cylindrical operating chamber 6. A pin 13, particularly shown in Figure 5a, which defines the axis X, is provided in the 5 stationary element 2. The pin 13, which has to be mounted in a cylindrical receptacle 24 of the stationary element 2, has a suitably shaped central portion 14 which defines the cam element 11 and side portions 15, 15' to be connected to the movable element 3. By this arrangement, the cam 11 rotates integrally with the movable element 3. 10 The cam element 11, which is defined by the central portion 14 of the pin 13 comprises a substantially flat surface 16, parallel to the axis X and abutting against the front face 17 of the plunger element 12. By rotating about the axis X, the surface 16 interacts with the front face 17 of the plunger element 12 to cause its straight-line motion along the line d. For this purpose, the operating chamber 6 and the cylindrical receptacle 24 are in mutual 15 communication at the contact area between the surface 16 of the pin 13 and the front face 17 of the plunger element 12. In the embodiment shown in Figure 5b, the surface 16 has a distance g from the axis X of 1 to 6 mm, preferably of 1 mm to 3 mm and more preferably of about 2 mm. Thanks to such 20 distance, the closing movement of the door will be automatic. As shown in Figure 5c, the plunger element 12 is composed of a counter spring 18, a locking cap 19, a cover cylinder 20 and a check valve 21, which defines means for controlling the flow of oil 5 in the chamber 6, as better explained herein below. The plunger element 12 is 25 "packed" and introduced, with the help of a gasket 22, in the operating chamber 6, with the locking cap 19 defining the bottom wall thereof. It will be understood that the check valve 21 may be also mounted within the cover cylinder 20, as shown, for example in Figure 4b. In this case, the front face 17 of the plunger 30 element 12 is defined by the front face 23 of the cover cylinder 20. As particularly shown in Figures 7a, 7b, 8a and 8b, the end wall 32 of the plunger element 12, which defines the front face 17 thereof, is adapted to divide the operating chamber 6 11 into a first and second variable volume compartments 33, 34, which are adjacent and in fluid communication with each other. The counter spring 18 is placed in the first compartment 33. This embodiment of the hinge structure 1 allows for simple installation. The installation 5 procedure is simply carried out by fitting the pin 13 in the cylindrical receptacle 24 of the stationary element 2, connecting the side portions 15, 15' thereof to the movable element 3 by introducing the surfaces 25, 25' of the pin 13 in the receptacles 26, 26' of the half shell 9', inserting the oil seals 27, 27', if any, thrust bearings 28, 28' and thrust bearing supports 29, 29' in the receptacle 24, securing the pin 23 to the shell 9' using the screws 30, 30' and 10 clamping together the half shell 9 and the half shell 9' so installed by the screws 10, 10'. The plunger element 12, packed as described above, is introduced in its operating chamber 6, and the locking cap 19 is tightened. Such assembly procedure is completed by introducing oil 5 in the operating chamber 6, for 15 hydraulic damping of the closing movement produced by the closing means 4. For this purpose, a through hole 31 may be formed in the stationary element 2 to define an oil loading channel allowing communication between the operating chamber 6 and the external environment, as shown in Figure 4a. It will be understood that the amount of oil to be loaded in the chamber 6, as well as the volume of the latter, is variable depending on the 20 mass of the door P to be moved. The operation of the hinge structure 1 is shown in Figures 7a, 7b, 8a and 8b. In the closed door position, as shown in Figure 7a, the flat surface 16 of the pin 13 and the 25 front face 17 of the plunger element 12 are in contact with, substantially parallel to and abutting against each other. The counter spring 18 is pre-compressed between the cylinder 20 and the cap 19. In this position, substantially the whole amount of oil 5 is in the first variable volume compartment 33, which has the maximum volume. Also, the counter spring 18 is at its maximum elongation. 30 When a user opens the door P by applying an external load ELthereto, the door P moves in the direction of arrow Fi from the closed door position to an open door position, as shown in Figure 7b. This movement causes the flat surface 16 of the pin 13 to rotate about the axis X, and thence interact with the front face 17 of the plunger element 12 to compress the 12 counter spring 18. The flat surface 16 of the pin 13 and the front face 17 of the plunger element 12 are angularly spaced apart by an angle a which increases as the door is being opened. The end wall 32 of the plunger element 12 is thus displaced along the line Y in the direction V. At the same time, due to the motion of the partition wall 32, the oil 5 is 5 transferred from the first compartment 33, whose volume decreases, to the second compartment 34, whose volume accordingly increases, through the orifice 35 of the check valve 21. In the embodiments illustrated herein, the check valve 21 is defined by an elongate io extension 36 of the end wall 32 coaxial to the cylindrical operating chamber 6 and is of the normally open type, i.e. allowing the passage of oil 5 from the first compartment 33 to the second compartment 34 while the door is being opened and preventing it from flowing back as the door is being closed. 15 Figure 8a shows the fully open door position. In this position, the flat surface 16 of the pin 13 and the front face 17 of the plunger element 12 are perpendicular to each other. As shown in this figure, substantially the whole amount of oil 5 is in the second variable volume compartment 34, which has the maximum volume, while the first compartment 33 has the minimum volume. Also, the counter spring 18 is in its maximum compression position, which 20 corresponds to its minimum elongation. When a user rotates the door P from the fully open door position or, equivalently, when a user releases the door from a partly open door position (i.e. when the external load EL no longer acts thereon), the closing means 4 will start to operate on the movable element 3 to 25 automatically return the door P to the closed position. At the same time, the hydraulic damping means 5 will start to operate on the movable element 3 to oppose and damp the closing movement produced by the closing means 4. Figure 8b shows the above condition, with the door P in a partly open door position during 30 door closing, in the direction of arrow F 2 . In this position, the flat surface 16 of the pin 13 and the front face 17 of the plunger element 12 are angularly spaced apart by an angle a which decreases as the door is being closed. The previously compressed spring 18 performs its opposing action by pushing the front face 17 of the plunger element 12 against the surface 16 of the pin 13, thereby causing the surfaces 16 and 17 to slide one against the 13 other and the end wall 32 to move along the line Y in the direction V'. At the same time, due to the motion of the partition wall 32, the oil 5 is transferred from the second compartment 34, whose volume starts to decrease, to the first compartment 33, whose volume accordingly increases. However, the oil 5 will no longer flow through the orifice 35 of the 5 check valve 21, which is closed, but will flow back into the first compartment 33 through a tubular space 37 between the side wall 38 of the operating chamber 6 and the side wall 39 of the cover cylinder 22 of the plunger element 12. Convenient adjustment of the size of the air space 37 may increase or decrease the damping effect provided by the oil 5, which makes the hinge structure exceptionally safe. 10 In an alternative configuration, as shown in Figure 10, at least one hole 40 may be formed on the side wail 39 of the cover cylinder 20 of the plunger element 12, to facilitate and/or control the backflow of oil 5 into the first compartment 33. Suitable configuration of the sizes and/or number of holes 40, allows to control the return movement of the door P to the 15 closed door position. In a further alternative embodiment, as shown in Figure 9, the structure 1 may comprise a screw 41 for throttling the air gap 37 and thereby adjusting its size as desired, to change the backflow velocity of the oil 5, and thus adjust the damping effect. 20 Figures 11 to 23 show without limitation a second embodiment of the hinge structure, generally designated by numeral 1'. The latter essentially comprises a stationary element 2 and a movable element 3 to be fixed to a door P by the two half shells 42, 42', The stationary element 2 is designed to be fixed to a stationary support S, such as a wall or a 25 floor, through the skirting 43, as shown in Figure 24. This second embodiment differs from the first embodiment in that, while the closing means 4 are held in a single first operating chamber 6, the hydraulic damping means 5 are held both in this first operating chamber 6 and in a second operating chamber 44, which is in 30 fluid connection therewith. As shown in Figure 14, both the first operating chamber 6 and the second operating chamber 44 are wholly contained in the box-like housing defined by the stationary element 2.

14 This configuration allows controlled movement of very heavy doors P and/or gates. This result is achieved thanks to the second operating chamber 44, which provides additional volume for the hydraulic damping means 5, whereby motion of objects of very large mass may be effectively controlled. 5 In this second embodiment, the closing means comprises, in addition to the first cam element 11, a second cam element 45, which is able to pivot about the axis X integrally with the first cam element 11, as particularly shown in Figure 17. Furthermore, the second cam element 45 cooperates with a second plunger element 46, which is longitudinally movable io along the line Y' within the second operating chamber 44. Advantageously, the line Y', which is defined by the axis of the second cylindrical operating chamber 44, is parallel to the line Y of motion of the first cam element 11, thereby minimizing space requirements. 15 In the second embodiment, the central portion 14 of the pin 13, which is always held within the stationary element 2 in a cylindrical receptacle 24, defines both the first cam element 11 and the second cam element 45. 20 The pin 13 is then designed to be fixed to the movable element 3 by means of the attachment surfaces 25, 25' of the end portions 15, 15'. Particularly, the top surface 25 is designed to be introduced in a groove 47 of the half shell 42 of the movable element 3, and the bottom surface 25' is introduced in the skirting 43 to be fixed to the floor S. 25 In this embodiment, both the first cam element 11 and the second cam element 45 are formed by specially shaping the central portion 14 of the pin 13. The first cam element 11, like in the first embodiment, comprises a first substantially flat surface 16, parallel to the axis X and abutting against the front face 17 of the first plunger element 12. The second cam element 45, placed above the first, is substantially defined by a wall 48 having a pair of 30 second substantially flat surfaces 49, 49', parallel to the axis X and substantially perpendicular to the first surface 16. The wall 48, with its surfaces 49, 49' abuts against the front face 50 of the second plunger element 46. For this purpose, as better shown in Figure 16, the cylindrical receptacle 24 is 15 designed to communicate both with the first operating chamber 6 and with the second 44, at the area of contact between the first cam element 11 and the first plunger element 12 and at the area of contact between the second cam element 45 and the second plunger element respectively. 5 The latter, like the first plunger element, is substantially composed of a second counter spring 51, a second locking cap 52, a second cover cylinder 53 and a second check valve 54, which defines means for controlling the flow of oil 5 In the second operating chamber 44, as explained above. The second plunger element 46 is "packed" and introduced, with the help 10 of a second gasket 55, in the second operating chamber 44, with the locking cap 52 defining the bottom wall thereof. As particularly shown in Figures 20 to 23, the end wall 50 of the second plunger element 46 is defined by a wall 56 which is adapted to divide the second operating chamber 44 into a 15 third and fourth variable volume compartments 57, 58, which are adjacent and in fluid communication with each other. The counter spring 51 is placed in the fourth compartment 58. The stationary element 2 has a channel 60, clearly shown in Figure 13, for putting the first 20 and second operating chambers 6, 44 in fluid communication with each other. Furthermore, the channel 60 comprises a throttling screw 61, for adjusting the damping effect of the hydraulic means 5. In the second embodiment described herein, the check valve 21 is of the normally open 25 type, i.e. allowing the passage of oil 5 from the first compartment 33 to the second compartment 34 while the door is being opened and preventing it from flowing back as the door is being closed, whereas the check valve 54 is of the normally closed type, i.e. allowing the passage of oil 5 from the third compartment 57 to the fourth compartment 58 while the door is being opened and preventing it from flowing back as the door is being closed. 30 This embodiment of the hinge structure allows for simple installation, like the first embodiment. The installation procedure is simply carried out by fitting the pin 13 in the cylindrical receptacle 24 of the stationary element 2, connecting the side portions 15, 15' thereof to the movable element 3, as described above, inserting the oil seals 27, 27', if any, 16 thrust bearings 28, 28' and thrust bearing supports 29, 29' in the receptacle 24, and clamping together the half shell 42 and the half shell 42' so installed by the screws 10, 10', 10". The first plunger element 12, packed as described above, is introduced in its operating chamber 6, and the locking cap 19 is tightened, whereas the second plunger element is 5 designed to be packed and introduced in the second operating chamber 44. Such assembly procedure is completed by introducing oil 5 in the operating chambers 6 and 44, for hydraulic damping of the closing movement produced by the closing means 4. This may be accomplished using the loading channel 31 in the stationary element 2, which puts 10 the external environment in communication with the second operating chamber 44, the latter being in turn in fluid communication with the first operating chamber 6. It will be understood that the predetermined amount of oil loaded through the channel 31 will be distributed among the first 33, the second 34, the third 57 and the fourth 58 variable volume compartments. The channel 31, which is particularly useful for adding oil 5 when needed, is 15 closed by the cap 59. The operation of the hinge structure 1 is better shown in Figures 20 to 23. Figure 20 shows the relative position of the closing means 4 and the hydraulic damping 20 means 5 in the closed door position. In this position, the front face 17 of the first plunger element 12 abuts against and is parallel to the flat surface 16 of the first cam element 11 to keep the door closed, like in the first embodiment. The front face 50 of the second plunger element 46 abuts in turn against and is perpendicular to the wall 48 with its surfaces 49, 49'. 25 The first counter spring 18 is precompressed between the cylinder 20 and the cap 19, and the second counter spring 51 is compressed between the cap 52 and the cylinder 53. In this position, the first 33 and third 57 variable volume compartments have the maximum volume, and the second 34 and fourth 58 have the minimum volume. Also, the counter spring 18 is at its maximum elongation, and the second counter spring 51 has its minimum elongation 30 (maximum compression position). As the door P is opened, i.e. as an external load EL IS applied thereon, the movable element 3 will start to pivot about the axis X relative to the stationary element 2, the pin 13 will move in the direction of arrow Fi, and the first surface 26 of the first cam element 11 and the 17 second surfaces 49, 49' of the second cam element 45 will start to pivot integrally therewith. This partly open door position during door opening is shown in figure 21. Due to the rotation of the pin 13, and the resulting thrust exerted by the surface 16 on the 5 front face 17 of the first plunger element 12, the latter starts to move along the line Y in the direction V. At the same time, the second plunger element 46 starts to move along the line Y' in the direction V opposite to the direction V. As the door is being opened, the angle a between the first flat surface 16 of the pin 13 and the front face 17 of the first plunger element 12 starts to increase, whereas the angle P between the flat surfaces 49, 49' of the io second plunger element 46 starts to decrease. Thus, the volume of the first compartment 33 starts to decrease, as loading of the first spring 18 occurs. Furthermore, as the volume of the first compartment 33 decreases, the oil 5 therein starts to flow out through the orifice 35 of the valve 21 into the second variable 15 volume compartment 34, which starts to receive oil 5 and increases its volume. At the same time, due to the rotation of the surfaces 49', 49 and the resulting thrust exerted by the front face 50 of the second plunger element 46 thereon, the volume of the fourth compartment 58 starts to increase, as release of the second spring 51 occurs. Also, the 20 volume of the third compartment 57 starts to decrease, therefore the oil 5 therein starts to flow into the fourth compartment 58, whose volume accordingly increases. Figure 22 shows the fully open door position. It will be appreciated that the device of this embodiment allows 900 opening of the door also in the other direction. In this position, the 25 fourth compartment 58 will have the maximum volume, whereas the second compartment 34 will have the minimum volume. The first spring 18 is in its maximum load condition (minimum elongation), and the second spring 51 is in its minimum load condition (maximum elongation). 30 As a user releases the door or moves it from the position of Figure 22 to the closed position, the first spring 18 starts to be released, and the first plunger element 12 starts to push on the surface 16 of the pin 13 thereby rotating it in the direction of arrow F 2 back to the closed door position. At the same time, the surfaces 49, 49' compress the second spring 51, so that the volume of the fourth compartment 58 starts to decrease and oil flows out of it.

18 Figure 23 shows the above condition, with the door P in a partly open door position during door closing, in the direction of arrow F2. In this position, the first flat surface 16 of the pin 13 and the front face 17 of the first plunger element 12 are angularly spaced apart by an 5 angle a which decreases as the door is being closed, whereas the second flat surfaces 49, 49' of the pin 13 and the front face 50 of the second plunger element 46 are angularly spaced apart by an increasing angle P. The previously compressed first spring 18 performs its opposing action by pushing the front 10 face 17 of the first plunger element 12 against the first surface 16 of the pin 13, thereby causing the surfaces 16 and 17 to slide one against the other and the first end wall 32 to move along the line Y in the direction V. Now, the second spring 51 is also compressed due to the pressure of the second wall 48 of the second cam element 45 against the second plunger element 46, which moves along the line Y' in the direction V', opposite to the 15 direction V. The second valve 54 is of the normally closed type and does not allow the passage of the working fluid through its orifice 62, whereby oil 5 is forced to flow out at the hole 63 into the air gap 63 defined by the side walls 65, 66 of the second operating chamber 44 and the 20 second cover cylinder 53 respectively. The out-flowing oil 5 flows through the channel 60 into the first compartment 33 whose volume progressively increases. The first valve 21, which is of the normally open type, does not allow the passage of oil 5 through its orifice 35, wherefore oil will flow from the second compartment 34 to the third 25 compartment 57, which are in fluid communication with each other. In fact, in the second embodiment as shown in the figures, the working fluid follows a counter-clockwise path within the box-like housing defined by the stationary element 2, to hydraulically delay the rotary motion of the movable element 3 with respect to the return 30 movement thereof to the closed door position. Likewise, the working fluid is also delayed during door opening, so that the hinge structure is safe even for outdoor installations, in which wind or a careless user might exert an excessive load on the door.

19 In an alternative embodiment, as shown in FIG. 19, the first cam element 11 of the pin 13 may have a rounded peripheral surface, e.g. formed by turning, to allow the door P to be moved back to the closed door position from any open door position. This embodiment is particularly advantageous for fire doors. 5 Figures 24 to 32 show a preferred, non exclusive embodiment of a hinge assembly, generally designated by numeral 70, to be mounted on doors P or the like for self-closing thereof. The assembly 70 comprises a closing hinge 71 in the form of a closing hinge 71, and a hydraulically damping hinge 72 in the form of a hydraulically damping hinge 72. 10 Each of the a closing hinge 71 and the hydraulically damping hinge 72 comprises a stationary element 2, 2' to be fixed to the frame T of the door P and a movable element 3, 3' to be fixed to the door P. The movable elements 3, 3' are pivotally mounted to their respective stationary elements 2, 2' for rotating about the axis X. In this embodiment, the 15 door P acts as a "drive shaft" between the two hinge structures 71, 72. Accordingly, both the hydraulically damping hinge 72 and the closing hinge 71 are coupled to the door at longitudinally separated positions. The hydraulically damping hinge 72 includes a first pin 13' extending along the longitudinal 20 axis X. The first pin 13' includes a first cam element having first contact surfaces 82, 82' parallel to each other. The hydraulically damping hinge 72 further includes a first plunger element 83 movable within the first operating chamber 81 along the transverse axis d' between a compressed 25 position and an extended position. The first plunger element 83 having a first front face which is adapted to engage the first contact surfaces 82, 82' of the first pin 13'. The first operating chamber 81 further includes a first spring 90 for urging the first front face of said first plunger element 83 against the first contact surface of the first cam element of 30 the first pin 13'. The first operating chamber 81 further includes first hydraulic damping means 80 acting on the first movable element 3' to damp the hydraulically damping hinge 72 as it approaches the closed position.

20 The first plunger element 83 has a first side wall and a first end wall defining the first front face, the first end wall being designed to separate the first operating chamber into a first variable volume compartment and a second variable volume compartment which are in fluid 5 communication with each other. As shown in the embodiment of Figure 28, the closing means 4 and the hydraulic damping means 5 may be held in two operating chambers 6, 44 within the box-like housing defined by the first stationary element 2 of the closing hinge 71 , whereas the hydraulically damping 10 hinge 72 comprises damping means 80, which may also consist of a predetermined amount of the same oil as used in the closing hinge 71, contained in another operating chamber 81 within the box-like housing defined by the second stationary element 2'. In other words, the closing hinge 71 operates on the movable element 3 (and thence on the 15 movable element 3') to generate the torque C required to cause the door P to pivot to its closed position about the axis X whereas the hydraulically damping hinge 72 operates on its movable element 3' (and thence on the movable element 3) to hydraulically damp the movement produced by the closing hinge 71, thereby generating a resistant torque C' opposite the torque C. 20 This configuration allows for optimized motion control of very heavy doors and gates, during both the opening and closing movements. Concerning both construction and operation, the closing hinge 71 is very similar to the first 25 embodiment as shown herein in Figures 1 to 10, or to the lower half of the second embodiment as shown herein in Figures 11 to 23, However, the hydraulically damping hinge 72 is very similar, still in terms of construction and operation, to the upper half of the second embodiment as shown herein in Figures 11 to 23. The only functional and structural difference between the latter and the hinge assembly 70 is that the operating chambers 6, 30 44 and the operating chamber 81 are not in fluid communication with each other, although their operation is identical. In an alternative embodiment, the assembly 70 may be formed of the first embodiment of the hinge structure, as shown in Figures 1 to 10 (with the closing means held in a single operating chamber 6) and the hinge structure 72.

21 The contact surfaces 82, 82' of the first pin 13' are substantially perpendicular to the surfaces 16 and 49 of the pin 13 of the closing hinge 71. Furthermore, the pin 13' has a central portion 14' that defines a corresponding cam element s 86, as well as side portions 87, 87' that are appropriately shaped for connection with the movable element 3'. The cam element 86 interacts with the corresponding plunger element 83 as described above. 10 The hydraulically damping hinge 72 further comprises a corresponding check valve 84 located at an end wall 85 of the plunger element 83 to allow the passage of oil 80 during door closing and prevent backflow thereof during door opening. The wall 85 divides the operating chamber 81 into respective variable volume compartments 88 and 89, a counter 15 spring 90 being located in the compartment designated by numeral 88. As particularly shown in Figures 29 to 32, the check valves 21, 54 and 84 associated to their respective plunger elements 12, 46 and 83 are of the normally open type. 20 A further difference between the hydraulically damping hinge 72 and the upper half of the second embodiment as shown in Figures 11 to 24 is that the second check valve 84 is of the normally open type (like the first valves 21, 54), i.e. allows the passage of oil 5 from the fourth compartment 58 to the third compartment 57 during door opening and prevents backflow thereof during door closing. 25 Thus, unlike the second embodiment as shown in Figures 11 to 24, the first valves 21, 54 and the second check valve 84 operate in the same directions, i.e. open during door opening and close during door closing. 30 The closing and hydraulically damping hinges 71 and 72 are assembled in the same manner as those described above. Two channels 78, 79 are provided for filling oil 5 once the assembly has been completed.

22 In operation, the first and hydraulically damping hinges 71, 72 are mounted to the door P and cooperate to control its pivotal movement about the axis X. As shown in Figure 26, their pins 13 and 13' are configured in such a manner that the overlapping flat surfaces of the former and the opposite flat surfaces 82, 82' of the latter are perpendicular to each other. 5 To adjust the alignment of the door P 1 the closing hinge 71 may have suitable adjustment dowels 75, 76. The operation of the assembly 70 is identical to that of the second embodiment of the hinge io structure as shown in Figures 11 to 24, except that the flow of oil 5 is controlled by normally open check valves 21, 54, whereas the oil 80 is controlled by the valve 84, which is of the same type. Figure 29 shows the closing and hydraulically damping hinges 71, 72 in the closed door P is position, and Figure 31 shows the first and hydraulically damping hinges 71 , 72 in the fully open door P position. It will be understood that, while Figures 29 to 32 only show the upper portion of the hinge structure 71, the parts of the lower portion, not shown, operate exactly like those of the upper portion. 20 As the door P is opened by a user, i.e. as an external load EL is applied thereon, e.g. in the direction of arrow Fi as shown in Figure 30, the pin 13 and the pin 13' pivot about the axis X and cause the overlying surface 16 and the opposite flat surfaces 82, 82' respectively to rotate about the same axis X. The spring 18 of the plunger element 12 of the closing hinge 71 starts to be compressed, whereas the spring 90 of the hydraulically damping hinge 72 25 starts to be released. Thus, the volume of the compartment 33 starts to decrease, as loading of the spring 18 occurs. Furthermore, as the volume of the first compartment 33 decreases, the oil 5 therein starts to flow out through the orifice 35 of the valve 21 into the second variable volume 30 compartment 34, which starts to receive oil 5 and increases its volume. At the same time, due to the rotation of the surfaces 82', 82, the volume of the compartment 89 starts to increase, as the spring 90 starts to be released. Also, the volume of the compartment 88 starts to decrease, therefore the oil 80 therein starts to flow into the 23 adjacent compartment 89, whose volume accordingly increases. However, since the valve 84 is of the normally open type, the oil 80 cannot pass through the orifice of the valve, and will flow into the compartment 89 through an air gap 91 between the side wall 92 of the operating chamber 81 and the side wall 93 of the plunger element 83. 5 As a user releases the door or moves it from the position of Figure 31 to the closed position, the first spring 18 starts to be released, and the plunger element 12 starts to push on the surface 16 of the pin 13 thereby rotating it in the direction of arrow F2 back to the closed door position. At the same time, the surface 82 (or 82', depending on the door opening 10 direction) compresses the spring 90, so that the volume of the compartment 89 starts to decrease and oil 80 flows out of it. Figure 32 shows the above condition, with the door P in a partly open door position during door closing, in the direction of arrow F2. The previously compressed spring 18 performs its 15 opposing action by pushing the front face 17 of the plunger element 12 against the surface 16 of the pin 13, thereby causing the surfaces 16 and 17 to slide one against the other and the first end wall 32 to move along the line Y in the direction V. Now, the spring 90 is also compressed due to the pressure of the cam element 86 against the plunger element 83, which moves along the line Y' in the direction V', opposite to the direction V. 20 The valve 21, which is of the normally open type, does not allow the passage of oil 5 through its orifice 35, wherefore oil will flow from the second compartment 34 to the first compartment 33 through the air gap 37 between the side wall 38 of the operating chamber 6 and the side wall 39 of the cylinder 20. The valve 84, which is also of the normally open 25 type, allows the passage of oil 80 through its orifice, to cause it to flow from the variable volume compartment 89 to the compartment 88. It will be understood that both the closing and the hydraulically damping hinges 71, 72 may include fluid flow control means, like in the first and second embodiments described 30 hereinbefore. This will afford control during both opening and closing of the door P. Thus, the door may be designed to oppose no (or very low) resistance at low closing speeds, and to increase its resistance as the door P closing speed increases.

24 Thanks to this arrangement, if the door is mounted outdoors, it can be designed to be easily opened by users, while not being slammed because of external agents, such as wind or the like. 5 During door closing, such controlled movement prevents the door from banging against its frame, thereby ensuring integrity and long life thereof. On the other hand, during opening, such controlled movement will prevent any abrupt opening of the door P due to gusts of wind, to protect both the door and any user within its 10 operating range. While the hinge structure and assembly have been described with particular reference to the accompanying figures, the numerals referred to in the disclosure and claims are only used for the sake of a better intelligibility and shall not be intended to limit the claimed scope in is any manner. Although the hinge assembly have been described with reference to specific examples, it will be appreciated by those skilled in the art that the hinge assembly may be embodied in many other forms. 20 25

Claims (5)

1. A hinge assembly for coupling a door and a door frame or a floor, the hinge assembly comprising: a hydraulically damping hinge; and a closing hinge for self-closing the door, wherein both the hydraulically damping hinge and the closing hinge are adapted to be coupled to the door at longitudinally separated positions, further wherein the hydraulically damping hinge comprises: a first stationary element attachable to the frame or the floor and pivotally mounted to a first movable element attachable to the door for rotating about a longitudinal axis between an open door position and a closed door position; the first movable element including a first operating chamber extending parallel to a transverse axis substantially orthogonal to the longitudinal axis; the first stationary element including a first pin extending along the longitudinal axis, the first pin including a first cam element having a first contact surface; a first plunger element movable within the first operating chamber along the transverse axis between a compressed position and an extended position, the first plunger element having a first front face which is adapted to engage the first contact surface of the first pin; wherein the first operating chamber further includes a first spring for urging the first front face of said first plunger element against the first contact surface of the first cam element of the first pin; wherein the first operating chamber further includes first hydraulic damping means acting on the first movable element to damp the hydraulically damping hinge as it approaches the closed position; wherein the first plunger element has a first side wall and a first end wall defining the first front face, the first end wall being designed to separate the first operating chamber into a first variable volume compartment and a second variable volume compartment which are in fluid communication with each other.

2. The hinge assembly of claim 1, wherein the closing hinge is adapted to generate a torque to cause the door to pivot toward a closed position about the longitudinal axis, 26 further wherein the hydraulically damping hinge is adapted to operate on the first movable element to hydraulically damp the movement produced by the closing hinge.

3. The hinge assembly of claim 1 or 2, wherein the closing hinge includes a second pin extending along the longitudinal axis, the second pin including a second cam element having a second contact surface, wherein the second contact surface is substantially perpendicular to the first contact surface.

4. The hinge assembly of claim 3, wherein the closing hinge includes a second plunger element movable within a second operating chamber between a compressed position and an extended position, the second plunger element having a second front face which is adapted to engage the second contact surface of the second pin; further wherein in the door open position, the first contact surface and the first front face of the hydraulically damping hinge are mutually parallel and the second contact surface and the second front face of the closing hinge are mutually orthogonal; further wherein in the door closed position, the first contact surface and the first front face of the hydraulically damping hinge are mutually orthogonal and the second contact surface and the second front face of the closing hinge are mutually parallel.

5. The hinge assembly of claim 4, wherein the second operating chamber further includes a second spring for urging the second plunger element against the second contact surface; further wherein in the door open position, the first spring of the hydraulically damping hinge is in an extended position and the second spring of the closing hinge is in a compressed position; further wherein in the door closed position, the first spring of the hydraulically damping hinge is in a compressed position and the second spring of the closing hinge is in an extended position. DIANORA GOSIO By Patent Attorneys for the Applicant W COTTERS Patent & Trade Mark Attorneys