GB2504917A

GB2504917A - Damped self centering hinge

Info

Publication number: GB2504917A
Application number: GB201201395A
Authority: GB
Inventors: Chung Chow
Original assignee: Individual
Current assignee: Individual
Priority date: 2012-01-27
Filing date: 2012-01-27
Publication date: 2014-02-19
Anticipated expiration: 2032-01-27
Also published as: HK1190178A1; CN103225456A; GB2504917B; GB201201395D0

Abstract

A hinge having a damped self centering stop arrangement comprising a housing 1 having a spindle 9 parallel and offset from a hinge axis, the spindle rotationally coupled to the hinged connection via an attachment such as a gear train (7, 8, 6, fig.2) or crank lever (210, fig.12). The spindle has first cam surfaces 24 engaged by a pusher head 22 of a spring biased closing piston 17 and a second cam surface (49) engaged by a pusher head 27 of a spring biased damping piston 38 arrangement within a cylinder. The closing and damping pistons extending radially of the spindle axis. The damping arrangement may comprise one way valve 34 in the piston head with a first chamber 37 formed by the interior surface of the piston head and the cylinder and a second chamber 38 formed by the exterior of the piston head and the spindle 9. The spindle may include stop surfaces holding a door open, such surfaces may be flattened portions of the spindle located perpendicular of the first cam surface.

Description

DAMPED SELF-CENTERING HINGE LINKAGE

This invention relates to a hinge for a door, particulady for a wooden door or a glass door. The invention relates particularly but not exclusively to internal hinges for s framed wooden or glass doors.

Wooden or glass doors are often heavy. Glass doors may be double or triple glazed, particularly when intended for exterior use or for chilled rooms. Wooden doors may be very large and may require a robust hinge which provides reliable self-closing of the door to a centred closed position, avoiding the need for a latch or stop arrangement.

Doors having internal door stops have been disclosed, for example in US 6560821.

W020l 1/020630 discloses a glass door hinge having an internal door stop arrangement cornpnsing: a housing; a mount for coupling the housing to a support member; a pair of is clamps; an axial spindle; and a plurality of biasing members arranged to engage the spindle to return the clamps to one of a plurality of positions selected from a closed position and one or more open positions; wherein the spindle has a plurality of centering surfaces, each biasing member being arranged to apply a force to a respective centering surface to centre the hinge in one or more of the positions. UK patent application no. 1117784.7 discloses a further hinge having a self-centering internal door stop alTangement cornpnsing: a closing alTangement within a housing and adapted to engage a spindle to urge the hinge to a closed or centred position; a damping arrangement within the housing and adapted to engage the spinifie to damp movement of the hinge toward the closed position; wherein the spindle has a vertical axis and first and second centenng camsurfaces, wherein the closing alTangement comprises a pusher head having at least one closing contact surface and a spnng alTanged to urge the contact surface into engagement with a first centering surface; wherein the damping arrangement comprises working fluid and a piston slidably mounted within a cylinder urged by the spring into engagement with a second centering surface of the spindle; the damping piston including a non-return valve; wherein the closing and damping arrangements extend radially from the spindle axis in opposite directions; wherein an interior surface of the damping piston, sleeve and cylinder form a first chamber and the exterior surface of the damping piston head, bore and spindle form a second chamber for working fluid; working fluid disposed in the second chamber passing through the non-return valve in the damping piston as the damping piston moves towards the spindle axis in use, return flow through the non-return valve being prevented as the damping piston moves away from the spindle axis.

The disclosure of these specifications are incorporated by reference for all purposes

into the disclosure of the present specification.

According to the present invention there is provided a door hinge having a self-centenng internal door stop arrangement comprising: a housing; a mount for coupling the housing to a support member; attachment means for attaching a door to the housing so that the door can rotate about a main hinge axis; a spindle mounted vertically within the housing, the spindle having a spindle axis located in parallel spaced relation to the hinge axis is a closing arrangement within the housing and adapted to engage the spindle to urge the hinge to a closed or centred position; a damping arrangement within the housing and adapted to engage the spindle to damp movement of the hinge toward the dosed position; wherein the spindle has a vertical axis and first and second cam surfaces, the cam surfaces being arranged to urge the closing or damping arrangements respectively away from the axis as the housing rotates in relation to the spindle wherein the closing arrangement comprises a pusher head having at least one closing contact surface and a spring, the spring being arranged to urge the contact surface into engagement with a first cam surface; wherein the damping arrangement comprises working fluid and a piston, the piston comprising a piston head slidably mounted within a cylinder, a spring located within the cylinder, the piston having a damping contact surface, the damping contact surface being urged by the spring into engagement with a second cam surface of the spindle; the piston induding a non-return valve; wherein the closing and damping arrangements extend radially from the spindle axis; and wherein the spindle is connected to the mount by a linkage arranged so that the spindle is caused to rotate simultaneously as the hinge rotates on the hinge axis.

The linkage may be further arranged so that rotation of the spindle causes rotation of the hinge. Rotation of the spindle caused by the closing arrangement may rotate the hinge so that rotation of the spindle may cause the hinge to rotate to a closed position.

In a first embodiment the linkage comprises a gear train; the gear train comprising an outer toothed gear connected to the spindle and an inner toothed gear connected to the mount, wherein the inner toothed gear is located on the hinge axis or the outer toothed gear is in spaced relation to the hinge axis.

In a second embodiment the linkage may comprise cranks mounted on the spindle and on the housing, the cranks being connected by a connecting member. For example a connecting rod may be connected by pivots to the spindle and housing.

is The pivots may be located at radial distances from the spindle and hinge axes respectively to provide sufficient turning force so that the spring of the closing alTangements can cause closing of a door on which the hinge is mounted.

The linkage is preferably arranged so that the hinge and spindle are positively driven during both opening and closing; so that the closing and damping arrangements are engaged at all stages of the opening and closing of a door to which the hinge is attached.

In a preferred embodiment of the present invention, an interior surface of the damping piston, and cylinder form a first chamber and the exterior surface of the damping piston head, bore and spindle form a second chamber for working fluid disposed in the second chamber passing through the non-return valve in the damper piston as the damping piston moves towards the spindle axis in use, return flow through the non-return valve being prevented as the damping piston moves away from the spindle axis; and wherein the second cam surface has a radius from the spindle axis which increases from a minimum value at a location in which the damping contact sm-face engages the cam surface in a fully open position of the hinge to a maximum value at a location in which the damping contact surface engages the cam surface in the fully closed position of the hinge.

In the prefened embodiment, the radius of the second cain surface may have minimum values at locations on opposite sides of the spindle perpendicular to the closed position.

In a hinge which can open in both direcfions, for example for frameless glass doors,the profile of the second cam surface in cross sectional plan view is preferably symmetrical on either side of the closed position. In such an arrangement the damping force is controlled so that it changes with the angular disposition of the housing symmetncally as the hinge opens on either side of the closed position. The second cam surfaces may be both convex, for example cylindncal or otherwise outwardly curved.

Alternatively, the second cam surface may be planar.

The closing contact surface may be provided on a pusher head. The pusher head may be a portion of the piston forwardly extending towards the spindle. The contact surface may comprise a planar or curved surface on the pusher head.

Alternatively the pusher head of the closing piston may comprise one or a plurality of rollers mounted for free rotation about a vertical axis. A single roller may be used, for example mounted in a slot in the pusher head. Alternatively, two rollers may be mounted in spaced relation, for example on upper and lower sides of the pusher head. In such arrangements the circumference of the or each roller fonns the contact surface of the closing arrangement.

The closing cam surface may have circumferential indentations or projections arranged to define stop locations for the roller or rollers. The stop locations may be in the fully closed or perpendicular opened positions of the hinge.

The first and second cam surfaces may form a heart shape or pear shape cam profile. In one embodiment the profile is a mitre shape wherein two convex surfaces extend from a generafly planar base to form an apex; wherein the closing cam surface coinpnses the base and the damping cam surfaces extend from the base to an apex at the fully closed contact position.

Alternatively, when the first and second cam surfaces are generally planar the s spindle may be triangular in cross-section.

in a first embodiment the closing and damping cam surfaces are at the same locaion along the axis of the spindle. Such an arrangement reduces twisting forces on the spindle and bearings and also allows the height of the housing to be minimised.

Alternatively in a second embodiment the closing and damping surfaces may be alTanged at different axial locations so that one is above the other along the spindle axis within the housing. The closing and damping arrangements may extend parallel on the same side of the spindle axis. Alternatively, the closing and damping arrangements may is extend in different directions. In a preferred embodiment the closing and damping arrangements extend radially from the spindle axis in opposite directions.

In a further ahemative embodiment the spindle may have a damping cam surface located between two closing cam surfaces, the closing pusher head comprising two members extending towards the spindle. The members may comprise rollers mounted on the pusher head.

Conversely, a closing cam surface may be located between two damping cam surfaces, the damping pusher head comprising two members extending towards the spindle. These members may comprise rollers.

In a first embodiment of this invention, the spindle may be located on the hinge axis.

In a second embodiment of this invention, the spindle may be thcated in parallel spaced relation to the hinge axis. Location of the spindle on the hinge axis allows the spindle to be directly connected to the housing so that the spindle does not rotate in use.

Such an arrangement finds particular apphcation in hinges for use with &ass doors.

In particular embodiments but not essentially, an interior surface of the damping piston, and cylinder form a first chamber and the exterior surface of the damping piston head, bore and spindle form a second chamber for working fluid; working fluid disposed in the second chamber passing through the non-return valve in the damper piston as the damping piston moves towards the spindle axis in use, return flow through the non-return valve being prevented as the damping piston moves away from the spindle axis; A particularly advantageous embodiment incorporates both of the first and second aspects of the invention.

is The hinge is preferably for use with a wooden or glass door, more preferably an internal hinge for a wooden door or for a framed glass door. Movement of the hinge to an opened or closed position correspondingly moves the door to an opened or closed position.

The centering surfaces, particularly the main centering surface act as cam surfaces as the biasing member is rotated during opening or closing of the door.

In preferred embodiments an adjustable valve is located in the housing; a first duct communicating between the first chamber and the adjustable valve; a second duct communicating between the second chamber and the adjustable valve; whereby adjustment of the valve controls flow of working fluid from the first chamber to the second chamber to damp movement of the hinge towards the closed or centred position.

Use of a single adjustable valve is preferred. However, two or more adjustable valves may be used, if desired.

Use of two separate closing and damping arrangements allows each of them to be manufactured with a simple and robust construction so that the closing and damping forces and the damping profile may be selected to suit any particular application. For example, a stronger damping arrangement may be used for a heavy door or a large door which may be easily slammed during use.

The location of the damping alTangement on the opposite side of the spindle to the closing arrangement provides a more balanced construction in comparison to hinges in which both closing and damping pistons are on the same side of the spindle axis. Wear of the bearings is reduced so that misalignment of the cam surfaces is less likely to occur after prolonged use. This is particularly important where there are relatively small secondary or intermediate cam surfaces since the edges of these cam surfaces may become worn if the spindle is not accurately aligned.

The damping piston may comprise the piston head and a sleeve slideably moveable within the cylinder.

The working fluid is preferably oil or hydraulic fluid.

The damping arrangement comprises a circuit for working fluid extending from the chamber in which the spring is located to the adjustable valve, and from the adjustable valve to the chamber in which the exterior front sm-face of the damping piston engages the cam or centering surface of the spindle. The moving parts are therefore maintained in a well lubricated condition.

A single adjustable valve may be located on the exterior of the housing permitting simple and convenient adjustment.

The dosing arrangement, located in a separate chamber within the housing, may be tilled with oil or other fluid, although this is not essential. When a piston arrangement is used, one or more apertures may be provided to permit circdation of the working fluid as the piston extends and retracts in use. The aperture may be dimensioned to restrict the flow of fluid in order to provide additional damping for the hinge. Alternatively, the aperture may be sufficiently large to permit a free flow.

In contrast, in an arrangement in which there is free flow between the two chambers, control of damping by use of an adjustment valve may not be possible.

The first and second cam surfaces may have similar or different configurations. In s preferred embodiments, the surfaces are generally planar or comprise planar portions.

Preferably the cam surfaces extend forwardly of the spindle axis so that the axis passes through the spindle and does not pass through the space in front of the planar surface.

Secondary stop sm-faces perpendicular to the planar closing cam sm-face may be provided.

This arrangement permits the hinge to be stopped at an open position, for example 9Q0 from the closed centred position. Such an arrangement is not feasible if the closing member extends beyond the spindle axis in the centred position.

The or each stop surface may be arranged to engage the main biasing member to hold the clamps of the hinge in an opened position. Preferably the hinge is held in an is opened position perpendicuInr to the closed position.

Preferably the or each stop surface is perpendicular to the main centering surface.

Preferably two parallel stop surfaces are provided. There are preferably two open positions perpendicular on either side of the closed position. In this ammgement the door may be held in an open position perpendicular on either side of the closed position. A door attached to the hinge may be held open in either direction unless a small closing force is applied to the door sufficient to overcome the force of the main spring.

In the following description a direction towards the biasing member or piston is referred to as forward and a direction away from the biasing member or piston towards the spindle is referred to as rearward.

In a preferred embodiment the spindile is arranged so that when the main centering surface is facing towards the biasing member, the or each stop surface extends perpendicularly relative to the centering surface, the stop surface having a forward edge facing towards the biasing member and a rearward edge facing away from the biasing member.

In this position the stop surface preferably extends from a location rearwardly of the spindle axis either to a location forwardly of the spindle axis, or to a location on the axis that is on the diameter of the spindle parallel to the main centering surface. In the latter arrangement, wherein the or both forward edges are located on the spindle diameter in the closed position, the forward edge is orthogonal to the spindle diameter, the or each stop surface preferably extends rearwardly of the spindle axis. In this arrangement the hinge is prevented from angular rotation beyond the angle of the opened position, due to abutment between the biasing member and the stop surface. Rotation of the hinge towards the closed position is facilitated by the biasing member contacting the forward edge of the stop surface before engagement with the main centering surface.

In an alternative embodiment the proximal edge is located forwardly of the spindle diameter. In this arrangement the stop surface preferably extends forward by a sufficient is distance to provide a restoring force to resist rotation of the hinge towards the closed position. The distance between the forward edge and the diameter (or spindle axis) may be selected so that the biasing member provides a restoring force sufficient to allow a door secured to the hinge to be held in the opened position but with the force not being so large that a user would have difficulty in closing the door. The magnitude of the distance and consequently of the restoring force may depend on the width of the door, the weight of the door and the strength of an intended user.

In preferred embodiments the main centering cam surface is located forward of the spindle diameter. This confers several advantages. Closing of the hinge is facilitated. The length of the extension of the spring or other biasing member in use is reduced. This permits use of a more powerful but less expensive spring. The volume of lubricating oil dispbced during rotation of the spindle is reduced. This provides a longer worlcing life for the oil.

A further cam surface may be provided between the forward edge of the stop surface and an adjacent edge of the main centering cam surface. The further cam surface may be rounded to facilitate smooth opening and closing of the hinge, reducing wear of the contact surface. This permits use of a lower grade of steel for manufacture of the spindle.

One or more intermediate surfaces may be provided between the first and second surfaces, these being thcated at an angle intermediate the first and second surfaces. The intermediate surfaces may be planar or convex and may serve to impede or prevent closure of the hinge at an intermediate angle. In such an alTangement, accidental slamming of a door may be prevented. The intermediate surfaces may be at an angle of 300, 45° or 60° to the main closing centering cam surface. The engagement of the biasing member with the intermediate surfaces may reduce the rate of rotation of the door or may allow the door to be halted at the intermediate angle.

Where the hinge is for use with a glass door, the clamps may be adapted to securely engage a glass door panel. The glass panel may have holes to receive bolts passing through the clamps. Alternatively or in addition the clamps may engage the glass panel by friction or by use of an adhesive.

The invention is further described by means of example, but not in any limitative sense, with reference to the accompanying drawings, of which: Figure 1 shows a hinge in accordance with the invention; Figure 2 shows the hinge in the open position; Figure 3 the hinge in the closed position; Figure 4 shows the various views of the housing; Figure 5 is a cross-sectional view on B-B of Figure 4; Figure 6 is a cross-sectional view on A-A of Figure 4; Figure 7 is an exploded view of the hinge; Figure 8 is a side elevation of the moving parts; Figure 9 shows various views of the spindle; Figure 10 shows a further embodiment of the invention, including a crank linkage; Figures II and 12 show the hinge in closed and opened positions; Figure 13 is an expthded view of the hinge; Figure 14 shows the moving parts of the hinge; Figure iS shows the spindle; Figure 16 shows the closing piston; and Figure 17 shows the damping piston.

In the foflowing description, the same reference numerals are used to denote the same components in the various figures of each embodiment.

Figures I to 4 show a hinge in accordance with this invention. The hinge comprises a housing (1) having a horizontal integral flange (2) provided with screw holes and a vertical flange (3) also provided with screw holes to permit the hinge to be secured to a corner of a door (not shown). A mount comprises a horizontal flange (4) and a vertical flange (5) each provided with holes to allow the hinge to be bolted to the floor or cefling and vertical portions of a doorjamb (not shown). The mounting (4) has an integral gear (6) located on the hinge axis. This is referred to as an inner gear. An outer gear 7) is located on the extenor of the the housing (1) and is connected to the inner gear by an intermediate gear (8).

Figures 5 and 6 are cross-sectional views of the hinge on B-B and A-A of Figure 4.

A spindle (9) extends vertically within the housing, mounted on upper and lower bearings (10,11). The lower end of the spinifie (9) and lower bearing (10) are mounted in a blind bore in the housing. The upper end of the spindle (9) extends through an aperture within the housing formed by a sealing ring (12) and gasket (13). The spindle end (14) has a rectangu'ar or otherwise irregularly configured head to engage the outer gear (7). The gear (7) is secured to the head (14) by a grub screw (15) and is constrainted to rotate as the spindle rotates.

A closing arrangement comprises a cylindrical bore within which a piston (17) is mounted for sliding movement. The bore is closed by an end cap (18). A pair of springs (19,20) extending between the end cap and the rear face (21) of the piston (17) urge the piston outwardly towards the spindle (9) to provide a closing force for the hinge. A pusher head (22) extends towards the axis of the spincHe (9). A planar contact surface (23) of the pusher head engages a planar cam surface (24) of the piston to urge the hinge into the closed position as shown in Figures 5 and 6.

Figure 7 is an exploded view showing the components of the hinge. Figure 8 is a side elevation of the principal moving parts. An oil passage way (25,26) permits flow of oil through the piston (17) during opening and closing of the hinge.

The damping arrangement comprises a damping piston compnsing a piston head and cylindrical sleeve (28) mounted within cylindrical bore (29). The damping piston comprises a pusher head (27) with a planar contact suiface (41) engaging the damping cam suitace (49) of the spindle (9). The damping arrangement bore (29) may be co-axial with the closing arrangement bore (16). The bore (29) is closed by an end cap (30). A damping spring (31) and valve seat (33) are located adjacent the pusher head (27). A valve member (34) captive between the rear surface of the pusher head (27) and the valve seat 33) acts to seal valve aperture (35) as the piston is urged radially outwardly by the spindle during closing of the hinge. A needle valve (36) located within a threaded bore in the housing provides an adjustable passageway for flow of oil displaced by the piston from is the piston chamber (37) to the spinifie chamber (38) during rotation of the spindle relative to the housing and consequent compression of the piston against the restonng force of the spring (31). The bores (16,29) are filled with oil or hydraulic fluid. Adjustment of the first adjustable valve (36), shown in Figure 5, allows the maximum flow of oil displaced by the damping piston to be controlled in order to limit the maximum rate of closing of the hinge in use. This arrangement is disclosed in UK patent application no. 1117784.7 (Attorney docket no. CHO-P3291GB2) the disclosure of which is incorporated into the specificadon by reference for all purposes.

Figure 6 shows a second adjustable valve (51), shown in Figure 6, which regulates flow of oil between passageways 52 and 53. Use of two valves provides differential damping at selected angels of the hinge. A first valve may control oil flow to provide damping at 80° to 25° and the second vlave provides damping between 25° to 5°, for

example.

The gear train connecting the housing (I) to the mount (4,5) comprises an inner gear (6) integral with the mount, an outer gear (7) fastened to the spindle head (14) and an intermediate gear (8). Intermediate gear (8) is secured by a screw and bearing (39) to a post (40) extending downwardly from the housing (1). The three gears (6,7,8) are arranged to be aligned with co-planar axes when the hinge is in the fully closed position.

Figure 9 shows vanous views of the spindle (9). The spindle (9) comprises a cylindrical shaft with a rectangular or square key section (114) dimensioned to engage the gear (7). A collar extends radially from the spindle to retain the bearing (11) within the closing ring (12). The upper part of the spindle comprises a cylindrical head (45) dimensioned to be received in the bearing (10) and blind bore of the housing (1).

The spindle comprises two cam surfaces located at the same position on the spindle axis. A closing cam surface has a planar contact surface, two perpendicubr secondary or stop cam surfaces (47) and intermediate cam surfaces (48) extending between the closing cain surface (46) and the secondary or stop cam surfaces (47). The axis extends through the body of the spindle behind the contact surface (46) so that the secondary surface (47) is extends from a position rearwardly of the spindle axis to a position forwardly of the spindle axis to form a retaining stop surface permitting the hinge to be held in the perpendicular open position.

The damping cam surface comprises two convex cylindrical or otherwise curved surfaces (49) extending rearwardly to form an apex (50). The radial distance of the convex surfaces (49) from the spindle axis increases from a minimum value at the secondary stop surfaces (47) to a maximum value at the apex (50).

In the fully opened position of the hinge the contact surface of the closing piston (23) engages the secondary or stop contact surfaces (47) of the spindle so that the apex (50) is directed perpendicularly away from the contact surface of the damping piston (41).

When the hinge is displaced from the fully open position the springs (19,20) of the opposing arrangement urge the piston (17) towards the spindle until the first cam surface (46) is paralld with the contact surface (23) of the pusher head (22). During the movement from the opened position the damping piston is urged radially outwardly from the spindle by the increasing radius of one of the damping cam surfaces (49) until the dampings spring is fully compressed and the damping piston is fully retracted by engagement with the apex (50). During this process the valve (32) is closed so that oil is forced through needle valve (36) to provide controlled damping during closing of the hinge. The pressure exerted by the cam surface (49) increases to a maximum as the apex (50) reaches the fully extended position with the contact surface of the damping piston at the maximum distance from the spindle axis.

When the hinge is opened the closing springs (19,20) are compressed. The damping spring (31) is released as the damping piston moves towards the spindle. Oil within the spindle cavity (38) allowed to pass through the valve passageway (35) past valve member (34) and into the interior (37) of the damping piston, recharging the damping arrangement for further use.

Figures 10 to 16 descnbe a further embodiment of the invention wherein the linkage comprises a crank arrangement. The hinge comprises a housing (201) having a horizontal integral flange (202) provided with screw holes and a vertical flange (203) also is provided with screw holes to permit the hinge to be secured to the corner of a door (not shown). The mount compnses a honzontal flange (204) and a vertical flange (205), each provided with holes to allow the hinge to be bolted to the floor or ceiling and vertical portions of a doorjamb (not shown).

The mounting (204, 205) is connected to the housing (201) by a linkage. The linkage comprises an inner crank (206) connected to an outer crank (207) by means of a connecting member (210). Inner crank (206) is mounted on a pivot (208) on the main axis of the hinge. Pivot (207) is connected to a spindle (209) by means of a grub screw.

Rotation of the housing (1201) relative to the mount (204, 205) causes rotation of the spindle (209). Conversely. rotafion of spindle (209) causes rotation of the housing (201) relative to the mount (204,205). The radii of the cranks (206,207) are selected to provide a suitable turning moment of the hinge as the spindle is caused to rotate by the closing member.

The construction of the dosing and damping arrangement is similar to that described with reference to the preceding Figures. The spindle (209) extends vertically within the housing. The lower end of the spindle is mounted in a blind bore in the housing. The upper end of the spindle extends through an aperture within the housing foimed by a closing cap (212) and gasket (213). A crank (207) comprises a collar secured to the head of the spindle (214) and carries a crank aim. A pin (215) pivotally secures the connecting member (210) to the crank arm.

The arrangement of the moving pails is shown in Figure 14.

Figures 15 to 17 illustrate the spindle and closing and damping piston arrangements.

The spindle (170) has annular collars (171, 172) with a cam surface extending between the collars. The profile of the cam surface is shown on section A-A. The configuration is similar to that shown in Figure 23 with the exception that the main closing cain surface is located between upper and lower damping cam surfaces. The main closing cain comprises a central concave cam surface (173) located between convex shoulders (174). Convex surfaces (175) extend rearwardly to an apex (176). A pair of projections is (177) extend outwardly to form a recess (178) which co-operates with the roller to form stop surfaces. The damping cam surfaces (175) each have a radius increasing from the stop surfaces 078) rearwardly to the apex (176). The closing piston (186) has laminar pusher head members (179) defining a channel in which a roller (180) is mounted on pivot (181) for free rotation during engagement with the cam surface.

Figure 17 shows the damping piston (182) having a pusher head (183), the pusher head (183) having a forwardly extending slot (184) between two parallel members (185) arranged to receive the projections (177) of the spindle as the spinifie rotates.

Claims

CLAIMSI. A door hinge having a seff-centering internal door stop arrangement cornpnsing: a housing; a mount for coupling the housing to a support member; attachment means for attaching a door to the housing so that the door can rotate about a main hinge axis; a spindle mounted vertically within the housing, the spindle having a spindle axis located in parallel spaced relation to the hinge axis a closing arrangement within the housing and adapted to engage the spindle to urge the hinge to a closed or centred position; a damping arrangement within the housing and adapted to engage the spindle to is damp movement of the hinge toward the dosed position; wherein the spindle has a vertical axis and first and second cam surfaces, the cam surfaces being arranged to urge the closing or damping alTangements respectively away from the axis as the housing rotates in relation to the spindle wherein the closing arrangement comprises a pusher head having at least one closing contact surface and a spring, the spithig being arranged to urge the contact sm-face into engagement with a first cam surface; wherein the damping arrangement comprises working fluid and a piston, the piston comprising a piston head slidably mounted within a cylinder, a spring located within the cylinder, the piston having a damping contact surface, the damping contact surface being urged by the spring into engagement with a second cam surface of the spindle; the piston including a non-return valve; wherein the closing and damping arrangements extend radially from the spindle axis; and wherein the spindle is connected to the mount by a linkage arranged so that the spindle is caused to rotate simultaneously as the hinge rotates on the hinge axis.
2. A hinge as claimed in claim 1 wherein the linkage is arranged so that rotation of the spindle causes rotation of the hinge.
3. A hinge as claimed in any preceding claim wherein the spindle axis is in parallel spaced relation to the hinge axis; and wherein the spindle is connected to the mount by a linkage arranged so that the sphidle is caused to rotate simultaneously as the hinge rotates on the hinge axis.
4. A hinge as claimed in claim 3 wherein the linkage is alTanged so that rotation of the spindle causes rotation of the hinge.
5. A hinge as claimed in claims 3 or 4 wherein the linkage comprises a gear train.
6. A hinge as claimed in claim 5 wherein the gear train comprises a toothed gear connected to the spindle and a toothed gear connected to the mount on the hinge axis.
7. A hinge as claimed in any of claims 5 to 6 further comprising an intermediate gear.
8. A hinge as claimed in claim 1 wherein the linkage comprises cranks mounted on the spindle and housing, the cranks being connected by a connecting member.
9. A hinge as claimed in claim S wherein an interior surface of the damping piston, and cylinder form a first chamber and the exterior surface of the damping piston head, bore and spinifie form a second chamber for working fluid; working fluid disposed in the second chamber passing through the non-return valve in the damper piston as the damping piston moves towards the spindle axis in use, return flow through the non-return valve being prevented as the damping piston moves away from the spindle axis.
10. A hinge as claimed in any preceding claim wherein the hinge and spindle are positively driven during both opening and closing of the hinge.
11. A hinge as claimed in any preceding dairn. wherein an interior surface of the damping piston, and cylinder form a first chamber and the exterior surface of the damping piston head, bore and spindle form a second chamber for working fluid; working fluid disposed in the second chamber passing through the non-return valve in the damper piston as the damping piston moves towards the spindle axis in use, return flow through the non-return valve being prevented as the damping piston moves away from the spindle axis; and wherein the second cam surface has a radius from the spindle axis which increases from a minimum value at a location in which the damping contact surface engages the cam surface in a fully open position of the hinge to a maximum value at a location in which the damping contact surface engages the cam sm-face in the fully closed position of the hinge.
12. A hinge as claimed in claim 11 wherein the radius of the second cam surface has minimum values at locations on opposite sides of the spindle.
13. A hinge as claimed in claim 10 or 11 wherein the profile of the second cam surface is symmetrical.
14. A hinge as claimed in any of claims 11 to 13 wherein the damping force changes with the angular disposition of the housing.
15. A hinge as claimed in any of claims 11 to 14 wherein the second cam surfaces are convex.
16, A hinge as claimed in any of claims 11 to 15 wherein the second cam surfaces comprise two convex surfaces extend from a generally planar first cam surface to form an apex.
17. A hinge as claimed in any of claims 11 to 15 wherein the second cam surfaces are planar.
18. A hinge as claimed in any of claims II to 17 wherein the closing and damping cam surfaces are at the same ocation along the axis of the spindle.
19. A hinge as claimed in any of claims II to 17 wherein the closing cam surface is located between two damping cam surfaces.
20. A hinge as claimed in any of claims 11 to 17 wherein the damping cam surface is located between two closing cam surfaces.s 21. A hinge as claimed in any preceding claim wherein the spindle further comprises a stop surface perpendicular to the closing cam surface.22. A hinge as claimed in claim 21 comprising two parallel stop surfaces.23. A hinge as claimed in any preceding claim wherein an adjustable valve is located in the housing; a first duct communicating between the first chamber and the adjustable valve; a second duct communicating between the second chamber and the adjustable valve; whereby adjustment of the valve controls flow of working fluid from the first chamber to is the second chamber to damping movement of the hinge toward the closed or centred position.24, A hinge as claimed in claim 23 wherein the adjustable valve is located on the exterior of the housing.25. A hinge as claimed in claim 23 or 24 comprising two adjustable valves.26. A hinge as claimed in any preceding claim wherein the closing member comprises a piston slidably movable within a cylinder, the piston comprising a piston head and a sleeve, the piston head having a projection with a contact surface, a spring located within the sleeve being arranged to engage a rear surface of the piston to urge the contact surface into engagement with the cam surface of the spindle.27. A hinge as claimed in any preceding claim wherein the spindle comprises an axially extending member having a closing cam surface and one or more damping cam surfaces disposed at the same location on the spindle axis.28. A hinge as claimed in any preceding claim wherein the damping anangement comprises a circuit for working fluid, comprising a duct extending from the chamber in which the spring is located to an adjustable valve, and from the adjustable va've to a chamber in which the exterior front surface of the damping piston engages the centenng s suiface of the spindle.29, A hinge substantially as hereinbefore described with reference to the accompanying drawings.Amendments to the claims have been filed as followsCLAIMS1. A door hinge having a self-centering internal door stop arrangement comprising: a housing; a mount for coupling the housing to a support member; attachment means for attaching a door to the housing to form a hinge connection so that the door can rotate about a main hinge axis; a spindle mounted vertically within the housing, the spindle having a spindle axis located in parallel spaced relation to the hinge axis; * a closing arrangement within the housing and adapted to engage the spindle to urge is the hinge to a closed or centred position; * ** S S * a damping arrangement within the housing and adapted to engage the spindle to S. S. * .. damp movement of the hinge toward the closed position; wherein the spindle has a vertical axis and first and second earn surfaces, the cam * ** surfaces being arranged to urge the closing or damping arrangements respectively away * S S from the axis as the housing rotates in relation to the spindle; wherein the closing arrangement comprises a pusher head having at least one closing contact surface and a spring, the spring being arranged to urge the contact surface into engagement with the first cam surface; wherein the damping arrangement comprises working fluid and a piston, the piston comprising a piston head slidably mounted within a cylinder, a spring located within the cylinder, the piston having a damping contact surface, the damping contact surface being urged by the spring into engagement with the second cam surface of the spindle; the piston including a non-return valve; wherein the closing and damping arrangements extend radially from the spindle axis; and wherein the spindle is connected to the mount by a linkage arranged so that the spindle is caused to rotate simultaneously as the hinge rotates on the hinge axis.2. A hinge as claimed in claim 1 wherein the linkage comprises a gear train.3. A hinge as claimed in claim 2 wherein the gear train comprises a toothed gear connected to the spindle and a toothed gear connected to the mount on the hinge axis.4. A hinge as claimed in any of claims 2 to 3 further comprising an intermediate gear.5. A hinge as claimed in claim 1 wherein the linkage comprises cranks mounted on the spindle and housing, the cranks being connected by a connecting member.6. A hinge as claimed in claim 5 wherein an interior surface of the damping piston, and cylinder form a first chamber and the exterior surface of the damping piston head, bore and spindle form a second chamber for working fluid; working fluid disposed in the second chamber passing through the non-return valve in the damping piston as the damping piston moves towards the spindle axis in use, return flow through the non-return valve being prevented as the damping piston moves away : * from the spindle axis.S S * S.7. A hinge as claimed in any preceding claim, wherein an interior surface of the damping piston, and cylinder form a first chamber and the exterior surface of the damping piston head, bore and spindle form a second chamber for working fluid; working fluid disposed in the second chamber passing through the non-return valve in the damping piston as the damping piston moves towards the spindle axis in use, return flow through the non-return valve being prevented as the damping piston moves away from the spindle axis; and wherein the second cam surface has a radius from the spindle axis which increases from a minimum value at a location in which the damping contact surface engages the cam surface in a fully open position of the hinge to a maximum value at a location in which the damping contact surface engages the cam surface in the fully closed position of the hinge.8. A hinge as claimed in claim 7 wherein the radius of the second cam surface has minimum values at locations on opposite sides of the spindle.9. A hinge as claimed in claim 6 or 7 wherein the.proflle of the second cam surface is symmctrical.10. A hinge as claimed in any of claims 7 to 9 wherein the damping force changes with the angular disposition of the housing.11. A hinge as claimed in any of claims 7 to 10 wherein the second cam surfaces are convex.12. A hinge as claimed in any of claims 7 to 11 wherein the second cam surfaces comprise two convex surfaces extend from a generally planar first cam surface to form an Is apex.r* : 13. A hinge as claimed in any of claims 7 to 11 wherein the second cam surfaces are planar. * S.14. A hinge as claimed in any of claims 7 to 13 wherein the closing and damping cam * surfaces are at the same location along the axis of the spindle.15. A hinge as claimed in any of claims 7 to 13 wherein the closing cam surface is located between two damping cam surfaces.16. A hinge as claimed in any of claims 7 to 13 wherein the damping cam surface is located between two closing cam surfaces.17. A hinge as claimed in any preceding claim wherein the spindle further comprises a stop surface perpendicular to the closing cam surface.18. A hinge as claimed in claim 17 comprising two parallel stop surfaces.19. A hinge as claimed in any preceding claim wherein an adjustable valve is located in the housing; a first duct communicating between the first chamber and the adjustable valve; a second duct comniunicating between the second chamber and the adjustable valve; whereby adjustment of the valve controls flow of working fluid from the first chamber to the second chamber to damping movement of the hinge toward the closed or centred position.io 20. A hinge as claimed in claim 19 wherein the adjustable valve is located on the exterior of the housing.
21. A hinge as claimed in claim 19 or 20 comprising two adjustable valves. * * * *is
22. A hinge as claimed in any preceding claim wherein the closing member comprises * a piston slidably movable within a cylinder, the piston comprising a piston head and a sleeve, the piston head having a projection with a contact surface, a spring located within the sleeve being arranged to engage a rear surface of the piston to urge the contact surface into engagement with the cam surface of the spindle.**.s 20 ** * * *
23. A hinge as claimed in any preceding claim wherein the spindle comprises an axially extending member having a closing cam surface and one or more damping cam surfaces disposed at the same location on the spindle axis.
24. A hinge as claimed in any preceding claim wherein the damping arrangement comprises a circuit for working fluid, comprising a duct extending from the chamber in which the spring is located to an adjustable valve, and from the adjustable valve to a chamber in which the exterior front surface of the damping piston engages the centering surface of the spindle.
25. A hinge substantially as hereinbefore described with reference to the accompanying drawings.