GB2525444A

GB2525444A - Damped Hinge

Info

Publication number: GB2525444A
Application number: GB1407351.4A
Authority: GB
Inventors: Chung Chow
Original assignee: BESTKO PREC Ltd
Current assignee: BESTKO PREC Ltd
Priority date: 2014-04-25
Filing date: 2014-04-25
Publication date: 2015-10-28
Also published as: CN105178753A; TWM516638U; CN204826975U; GB201407351D0; HK1216768A1

Abstract

A damping arrangement for a hinge comprises a spindle 10 having a cam surface 22 that engages a follower surface 28 on a damping piston 25 located in a housing 1. The cam surface is configured to urge the damping piston away from the spindle axis as the hinge moves to a closed position. The flow of hydraulic fluid through a circuit, which may be controlled by at least one adjustable valve, damps the closing movement. The configuration of the cam surface and follower surface are selected so that displacement of the damping piston caused by incremental angular rotation of the spindle is at a maximum value as the closed position is approached. A closing piston may be included to apply a closing force to the hinge. The profile of the cam surface may have a maximum radial dimension at a location engaging the cam follower when the hinge is closed.

Description

I

DAMPED HINGE

This invention relates to a damping arrangement for a hinge for a door or other closure. The invention relates particularly to a damped hinge or closer for a framed or frameless glass door or a wooden door. The invention also relates to a damped closer for attachment to a door. The invention relates particularly, but not exclusively, to internal hinges for 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 an external latch or stop arrangement. Such doors may include an internal door stop, as disclosed for example in US 6560821 or W0201 1/020630.

Although various damping arrangements have been disclosed, it is desired that a hinge or closer may provide a controlled degree of enhanced damping as it nears the closed position. In such an arrangement, damage due to slamming of a door is avoided without impeding normal closing of the door.

According to the present invention, a damping arrangement for control of rotational movement of a hinge from an open position to a closed position comprises: a spindle mounted on an axis and rotatable with respect to a housing; the housing including a damping piston engaging the spindle, the spindle having a cam surface; the damping piston being moveable within a bore, the bore extending radially with respect to the spindle; the damping piston having a follower surface or cam follower surface, the follower surface being urged by a spring into engagement with the cam surface of the spindle; the cam surface being configured to urge the damping piston away from the spindle axis as the hinge moves to the closed position; the damping arrangement finther including a circuit for hydraulic fluid arranged so that movement of the damping piston from a closed position causes a free flow of fluid within the circuit and further arranged so that movement of the damping piston from an open position to a closed position causes a restricted flow of fluid to damp the closing of movement; wherein the configuration of the cam surface and foflower surface are selected so that displacement of the damping piston caused by incremental angular rotation of the spindle is at a maximum value as the the closed position is approached.

A hinge in accordance with this invention 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.

A pair of clamps may be provided to secure a door panel to the hinge. Movement of the hinge to an opened or closed position correspondingly moves the door to an opened or closed position.

Alternatively, a door closer in accordance with this invention may be conveniently secured to the top edge of a wooden or other door and having an articulated arm sccured to the door frame. In another arrangement. the spindle is mounted within a housing for rotation about an axis extending through the housing and in spaced relation to the hinge axis of the door. The damping arrangement is described in this specification in relation to a damped hinge, although it will be appreciated that the configuration of the damping piston and spindle may be the same for a door closer arrangement.

An incremental rotation may be through an angle of, for example, 100, the displacement of the piston being determined for each 10° rotational increment. In the present invention, the displacement of the fluid during rotation from 20° to 10° or 10° toO° is greater than for a previous 10° increment in the range between 90° and 20°.

In a first embodiment, the hinge may further comprise a closing piston diametrically opposed or parallel to the damping piston and arranged to act on a closing cam surface of the spindle.

Alternatively, the damping and closing pistons may be located on separate hinges as of a door, so that one hinge provides a closing force and the other hinge provides a force to damp the closing movement, particularly during the final stage of the closing movement.

In preferred embodiments, the cam follower surface and closing cam surface both extend between two locations on the spindle axis.

Preferably the cam surfaces extend uninterrupted along the frill height or axial length of the damping and closing cam surfaces of the spindle. This makes the spindle and io the damping piston easy and economical to manufacture and reduces wear.

It is particularly preferred that the hinge may rotate through 90°in one or both directions relative to the spindle during movement from a fully closed to a fully opened position. Such an arrangement allows stop surfaces to be provided perpendicular to the closing cam surface on the spindle if required.

In a preferred embodiment, the damping arrangement is arranged to increase displacement of the damping piston during a final stage of closing of the hinge. For example, displacement of the damping piston away from the spindle axis may be increased during rotation through an incremental angle of 200 to 0°, preferably from 10° to 0°, more preferably from 5° to 0°.This provides a greater pressure on the fluid displaced by the damping piston. However, fluid flow is restricted by the adjustable valve or valves so that a damping force is applied to the spindle reducing the rate of rotation and damping movement of the door. The rate of rotation of the spindle decreases as the 0° position is approached because the damping circuit imposes a maximum limit on the fluid flow.

The configuration, particularly the radial profiles, of the cam and cam follower surfaces of the hinge are advantageously selected to control the distance moved by the damping piston during final angular increments as the hinge approaches the closed position.

The profile of the damping cam surface and configuration of the follower are preferably selected to control the distance of the damping piston from the spindle axis during rotation, particularly so that the piston is at a maximum distance at the fully closed position. Preferably the distance increases sharply adjacent the closed position.

In previously known damped hinges or closers, control of the damping force applied during the final 10 degrees of closing may be problematic due to the need for exact manufacturing tolerances, for example a tolerance of ±0.2mm for the flat contact surface.

The present invention may reduce the need to rely on exact manufacturing tolerances in comparison to previously known arrangements.

The cam follower surface is preferably fixed to and integral with the piston. Use of io a roller or otherwise movable contact surface is not preferred due to a difficulty in maintaining manufacturing precision to accurately control the damping force and to avoid wear during prolonged use.

In a particularly preferred embodiment, the cam follower surface is generally perpendicular to the piston axis but has a raised follower head preferably located centrally of the piston. The follower head may extend parallel to the spindle axis. The adjacent cam follower surface may be generally planar or concave. Alternatively, the surface may be otherwise profiled to control the distance of the piston from the spindle axis.

The cam follower surface may have a width selected to engage the cam surface of the spindle at an angular orientation required to provide increased damping, typically adjacent the fully closed position.

The follower head of the cam follower preferably extends from the plane of the adjacent follower surface towards the spindle axis and may have a maximum dimension in the direction along the piston axis and towards the spindle axis. The rate of increase of the axial dimension of the central part of the follower during rotation of the spindle may be controlled to allow corresponding control of the fluid pressure in the damping circuit.

so The profile of the cam surface of the spindle in plan view may be eccentric, having a maximum radial dimension at a location which engages the cam follower surface, particularly the follower head, in the fully closed position of the hinge. The cam surface is preferably symmetrical about a centre line which passes through the centre line of the piston when in the IhIly closed position.

The main closing and damping cam surfaces may together forn a heart shaped or pear shaped cam profile. However, in a preferred embodiment the profile is a mitre shape wherein two convex surfaces extend from a generally planar base to form an apex; wherein s the closing cam surface comprises the base and the damping cam surfaces extend from the base to an apex at the fully closed contact position.

Alternatively, the spindle may be triangular in cross-section in plan view.

In a first embodiment the closing and damping cam surfaces are at the same location 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 cam surfaces may be arranged at different axial locations so that one is above the other along the spindle axis within the housing. Preferably, the closing and damping pistons may extend parallel on the same side of the spindle axis. Such an arrangement is disclosed in GB 2484527, the disclosure of which is incorporated into this specification by reference for all purposes.

In preferred embodiments, the closing and damping arrangements extend radially from the spindle axis in opposite directions.

In a further alternative embodiment the spindle may have a damping cam surface located axially between two closing cam surfaces, the closing pusher head comprising two plate like members which extend toward the spindle to engage the two closing cam surfaces.

Conversely, a closing cam surface may be located between two damping cam follower surfaces, the damping piston having two cam follower members which extend toward the spindle to engage the two follower surfaces.

In these arrangements, the wear on the spindle is reduced as each piston only engages a respective cam surface. However, such an arrangement may be less robust.

as Use of 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 of each arrangement 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 piston on the opposite side of the spindle to the closing piston 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 internal stop surfacessince the edges of these surfaces may become worn if the spindle is not accurately aligned.

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

The working fluid is preferably oil or hydraulic fluid.

In preferred embodiments an adjustable valve is located in the housing; a first duct communicating between a first chamber on one side of the damping piston and the adjustable valve; a second duct communicating between a second chamber on the other side of the damping piston 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.

so Use of a single adjustable valve is preferred. However, two or more adjustable valves may be used, if desired. When two valves are used, one valve may be open during the entire closing movement of the hinge and the other valve may be closed by movement of the damping position at a selected angular position of the hinge, for example as the hinge approaches the fully closed position.

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

One or more adjustable valves may be located on the exterior of the housing permitting simple and convenient adjustment.

The closing arrangement, located in a separate chamber within the housing, may be filled 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 circulation 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.

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 is an exploded view of a hinge in accordance with this invention; Figure 2shows various views of the damping piston of the hinge shown in Figure 1; Figure 3 shows the spindle of the hinge shown in Figure 1; Figure 4 is a diagram illustrating the spindle and closing and damping pistons; Figures 5 and 6 are cross-sectional views of the hinge; Figure 7 is a plan view illustrating movement of the hinge; Figure 8 shows an alternative damping piston; Figure 9shows the damping piston of Figure 8 in conjunction with a spindleS and closing piston; Figure 10 shows the damping piston of Figure 8 in conjunction with an alternative spindle; Figure 11 is a diagram showing a further alternative arrangement of the closing piston, damping piston and spindle; S Figure 12 shows an alternative damping piston; and Figure 13 shows an alternative spindle.

The hinge shown in Figure 1 comprises a housing (1) having cover plates (2,3) and a channel member (4) having one or more channels to receive glass plates of a door. A io floor plate (5) has a socket (6) and cover (7). The floor plate has boltholes for fixing to a floor. The socket (6) has a key socket (8) to receive a correspondingly shaped projection of a spindle (10). The spindle (10) is received in a bore (as shown in Figure 5) of the housing (1) and is mounted on bearings (11,12) to allow the housing to rotate in use while maintaining an oil tight seal.

In an alternative embodiment, the housing may be arranged to be located in a recess in the floor or ceiling and the mounting plate may be adapted to be secured to the lower or upper edge of a door so that the spindle rotates with the door in relation to the fixed housing. However, the function of the damping arrangement is the same in both embodiments.

A closing piston (13) is slidably received within a bore (17) of the housing (1), being urged towards the spindle (10) by inner (14) and outer (15) springs. The bore (17) is closed by end cap (16) to provide a sealed structure.

The piston (13) has a hollow cylindrical body, dimensioned to receive the springs (14,15). A pusher head (18) has parallel planar upper and lower surfaces (19,20) as shown in Figure 5.

The pusher head (18) has a planar contact surface (21) extending transversely of the piston, perpendicular to the upper and lower surfaces (19,20) and parallel to the spindle axis to form a plate-like configuration.

The spindle (10) is formed with a seating arrangement comprising a planar cam as surface (22) and lower guide surfaces (23,24) arranged to receive and fully engage the corresponding surfaces (19,20,2 1) of the pusher head to form a seat for the piston in which the piston is received in a stable configuration in the fifily closed position of the hinge.

S The force applied by the springs (14,15) onto the piston urges the hinge into the closed, centred, portion in use.

The damping arrangement comprises a damping piston (25) received in a bore (not shown) in the housing (1). The damping piston is urged towards the spindle (10) by a io spring (26). An end cap (27) encloses and seals the bore. A one-way valve (128) and valve seat (129) within the hollow piston body (25) allows a flow of oil or other hydraulic fluid as the damping piston moves along the bore towards the spindle as the hinge rotates to an open position, but prevents flow of hydraulic fluid as the piston moves away from the spindle during closing. In this way the opening of the hinge is not damped. During closing the fluid is forced through a damping circuit containing one or more adjustable valves as described below.

The configuration of the damping piston and spindle are shown in Figures 2-4.

Figure 2 shows a perspective view, plan view and two elevations of the damping piston. The cylindrical piston body (25) has a forwardly extending support formation (29) with a cam follower surface shown generally as (28). The support formation (29) serves to support the follower surface (33) and has a variable vertical dimension. Laterally outward parts (30) of the support have a maximum vertical dimension in order to reduce twisting of the piston in use. Region (31) has a reduced dimension and a central follower head (32) has a greater vertical dimension. The follower head (32) serves as a follower for the damping cam surface (33) of the spindle (10). The cam follower surface (28) has a raised central part (32) which extends from the generally planar adjacent surface (33) of the end of the damping piston to form a head (32) extending vertically along the surface (33) parallel to the spindle axis. The head (32) forms an elongate cam follower for engagement with the apex of the damping cam surface of the spindle at or adjacent the fully closed position. The cross-sectional profile or the height and width of the head (32) are selected so that the damping piston is pushed away from the spindle by an appropriate distance so that the pressure of hydraulic fluid within the damping circuit increases to provide a greater damping force. This serves to counteract the closing force provided by the closing piston as the binge nears the fully closed orientation.

The follower head has upper and lower ends (34,35) to provide an elongate contact surface to transmit the rotational force from the spindle to increase the pressure of the hydraulic fluid in the chamber defined by the rear internal surface of damper piston (25), the bore and end cap (27) during closing of the hinge.

Figure 3 shows various views of the spindle (10). A shaft (36) has a projection (9) at a lower end to engage the key socket (8) of the floor plate (5). Cylindrical collars (37,3 8) are arranged to engage the internal surface of the bore (not shown) in the housing in order to ensure correct alignment of the spindle. An upper end (39) of the shaft is received bearing (12) located in the socket of the housing.

The spindle has a main planar closing cam surface (22) extending generally across the spindle axis. Upper and lower guide surfaces (23,24) extend radially above and below the cam surface (22) to form a parallel sided seat for the plate like pusher head (18) in the closed position of the hinge. Hold open stop surfaces (41,42) perpendicular to the main cam surface (22) are located on each side of the spindle to engage the contact surface (21) of the pusher head (18) in the fully opened position of the hinge.

A damping cam surface (40) extends radially outwardly of the spindle and has a bilaterally symmetrical mitre shape configuration with an apex (45) facing towards the damping piston in the fully closed position of the hinge. Upper and lower guide plates are located above and below the cam surface (40) to receive and locate the follower (28) of the damping piston (25). The guide plates have a greater radial dimension than the cam surface (40) and comprise mitre shaped cam surfaces (48,49,51,52) each with rearwardly facing apex (50).

Figures 5 and 6 are cross-sectional views of the hinge and illustrate the circuit for hydraulic fluid. Adjustable screw threaded needle valves (53,54) located in the upper surface of housing (1) are used to regulate a flow of hydraulic fluid displaced by the damping piston as the hinge moves to a closed position. When the hinge closes, the damping piston (25) is pushed away from the spindle axis by rotation of the cam (40).

One-way valve (128,129) is closed by the hydraulic pressure within the first chamber so that fluid is forced through passages (56,57,58) through the adjustable valves (54,53) and into the second chamber between the front of the damping piston head and the spindle.

Adjustment of the aperture of the valves (53,54) provides control of the maximum rate of fluid flow and further provides control of the degree of damping of the hinge.

As the hinge rotates from the fully opened 900 position to the fufly closed 00 position, the spindle rotates relative to the housing through angular increments, for io example 100. The mitre shaped curvature and radial dimension of the cam surface (40) is sciected so that the generally planar sw-face of the cam follower is moved away from the spindle axis by an equidistant or slightly increasing distance for each 100 increment, e.g. from 90° to 800, 800 to 70° etc. As the apex (45) of the cam approaches the central position, typically in the 20° to 10° increment, the end part of the cam surface (40) engages the follower head (32) increasing the rate at which the piston is moved away from the spindle axis. This increases the pressure of hydraulic fluid in the first chamber and reduces the maximum speed at which the hinge may be closed.

As the final angular increment from 10° to 0° is reached, the apex (45) contacts the 2D follower head, causing the rate of movement of the piston within the bore to increase until a maximum damping force is provided as the fully closed, 0°, position is attained. By this means the maximum fluid flow rate and hence the damping force increases sharply to prevent slamming of a door to which the hinge is attached.

Figure 7 is a series of plan views illustrating movement of the damping piston as shown in Figures 8 or 10 upon incremental rotation of the spindle.

Figure 8 shows a perspective view, plan and elevations of an alternative damping piston. The piston has a cylindrical body (60) and a cam follower head extending across so the head of the piston. A central follower head (61) extends diametrically vertically across the piston, parallel to the spindle axis. Rebates (62,63) extend laterally from the head (61) to form vertically extending portions located at a greater radial distance from the spindle axis. The cross-sectional profiles of the rebates are selected to form cam follower surfaces to co-operate with the rotating spindle to control axial movement of the piston.

Planar lands (64,65) are provided on the lateral outer edges of the piston head.

These raised formations serve to reduce any tendency of the piston to twist in the bore in use and also to rebut against stop surfaces (66) (shown in Figure 5) of the housing to prevent over extension of the damping piston towards the spindle axis in use.

Figure 9 is a diagram showing a hinge arrangement in which the closing piston (67) and damping piston (63) are as described with respect to Figure 8, located in parallel to io engage respective cam surfaces (69,70) of spindle (71). This arrangement is for use with a hingc as disclosed in GB 2484527, the disclosure of which is incorporated herein by reference for all purposes.

Figure 10 is a further arrangement in which the damping piston of Figure 8 is used in a hinge which provides only a damping function. The piston (72) engages a cam surface of spindle (73) described above. A separate closing hinge may be provided.

Figure 11 is a diagram showing an alternative arrangement in which a damping piston in accordance with this invention is used in conjunction with a closing piston (75) having two, upper and lower, plate like pusher heads (77), each having respective upper and lower cam surfaces (78,79) located on spindle (80) above and below the damping cam surface (81). The cam surfaces are bounded by upper and lower cylindrical plates (83,84,85) so that the follower (87) of damping piston (86) is received between adjacent (83,84). The planar follower surface (88) has a centrally located follower head (39) extending vertically parallel to the spindle axis.

Figure 12 shows a ftirther alternative damping piston comprising a cylindrical piston body (90) having a cylindrical follower support (91) extending forwardly, towards the spindle axis. The follower support (91) has a smaller diameter than the damping piston body (90). The central surface of the follower has a follower head (92) extending vertically parallel to the spindle axis as previously described. Rebates (93,94) lie on either side of the head (92) and stop portions (95,96) are located on the lateral edges of the follower surface.

Figure 13 shows another spindle configuration, similar to the one shown in Figure 3but not having the guide plate 48, 49, 51, 52, so that the damping cam surfaces 100, 101 extend the full heightor axial length of the closing cam surface.

Claims

CLAIMS1. A damping arrangement for control of rotational movement of a hinge from an open position to a closed position comprising: a spindle mounted on an axis and rotatable with respect to a housing; ia the housing including a damping piston engaging a spindle, the spindle having a cam surface; the damping piston being moveable within a bore, the bore extending radially with respect to the spindle; the damping piston having a follower surface, the follower surface being urged by a spring into engagement with the cam surface of the spindle; the cam surface being configured to urge the damping piston away from the spindle axis as the hinge moves to the closed position; the damping arrangement including a circuit for hydraulic fluid arranged so that movement of the damping piston from a closed position causes a free flow of fluid within the circuit and further arranged so that movement of the damping piston from an open position to a closed position causes a restricted flow of fluid to damp the closing movement; wherein the configuration of the cam surface and follower surface are selected so that displacement of the damping piston caused by incremental angular rotation of the spindle is at a maximum value as the closed position is approached.
2. An arrangement as claimed in claim 1, the spindle having a cam surface and further comprising a closing piston located diametrically opposed or in parallel relation to the damping piston and arranged to act on the cam surface. 3D
3. An arrangement as claimed in claim 1 as part of a hinge system for a door further comprising separate hinge including a closing piston and a spindle having a cam surface arranged to apply a closing force to the door.
4. An arrangement as claimed in any preceding claim wherein the cam follower is a generally planar, a central part of the cam follower forming a head extending from the planar surface towards the spindle axis.
5. An arrangement as claimed in any preceding claim, wherein the profile of the cam surface in plan view has a maximum radial dimension at a location which engages the cam follower in the fully closed position of the hinge.
6. An arrangement as claimed in claim 5, wherein the cam surface is io symmetrical about a centre line passing through the axis of the piston in the fully closed position.
7. An arrangement as claimed in claim 5 or 6, wherein the cam surface comprises two convex surfaces forming an apex.
8. An arrangement as claimed in claim7, wherein thc cam surface of the spindle has a mitre shaped profile.
9. An arrangement s claimed in any of claims 1-7, wherein the spindle is triangular in cross-section.
10. An arrangement as claimed in any preceding claim, wherein closing and damping cam surfaces are located at the same position along the spindle axis.
11. An arrangement as claimed in any of claims 1 to 9, wherein the closing and damping cam surfaces are arranged at different locations on the spindle axis.
12. An arrangement as claimed in any preceding claim, wherein an adjustable valve is located in the housing; a first duct communicating between a first chamber on one side of the damping piston and the adjustable valve; a second duct communicating between a second chamber on the other side of the damping piston 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.
13. An arrangement as claimed in claim 12, comprising one or more adjustable valves.