WO2011131955A1

WO2011131955A1 - Damped self-closing hinge

Info

Publication number: WO2011131955A1
Application number: PCT/GB2011/050426
Authority: WO
Inventors: Chung Chow
Original assignee: Chung Chow
Priority date: 2010-04-19
Filing date: 2011-03-04
Publication date: 2011-10-27
Also published as: GB201019931D0; GB2479804A

Abstract

A damped hinge comprising: a first leaf (32) for securing the hinge to a fixed support; a second leaf (35) for securing a moveable closure to the hinge; a barrel (33) secured to the first leaf (32), the barrel (33) including an axial bore (34); a piston (30) mounted for axial movement within the bore (34), the piston (30) including a cam surface (45); an axially extending member (39) constrained to rotate with the second leaf (35), the member (39) including a cam follower (42) arranged to engage the cam surface (45); the cam surface extending axially so that the piston (30) moves axially within the bore as the second leaf is rotated in relation to the first leaf; a hydraulic fluid contained within the bore (34); at least one of the piston (30) and member (39) including a passageway through which the hydraulic fluid may flow as the piston moves within the bore; wherein the passageway includes an adjustable valve (48, 49) to restrict the flow of fluid to damp opening or closing of the hinge.

Description

DAMPED SELF-CLOSING HINGE

This invention relates to a damped self-closing hinge, particularly but not exclusively for use with a door or other closure wherein the closure rotates in a vertical axis.

Self-closing doors may include a spiral cam surface against which a cam follower is urged by the weight of the door, to cause the door to rotate from an open to a closed position.

US-A-5419013 discloses a hydraulic hinge for use with a washing machine or toilet seat lid having a rotatable shaft and a linearly moveable plug forming fluid chambers, arranged so that the lid may be opened quickly but it closes at a slower speed.

According to the present invention, a damped hinge comprises:

a first leaf for securing the hinge to a fixed support;

a second leaf for securing a moveable closure to the hinge;

a barrel secured to the first leaf, the barrel including an axial bore;

a piston mounted for axial movement within the bore, the piston including a cam surface;

an axially extending member constrained to rotate with the second leaf, the member including a cam follower arranged to engage the cam surface;

the cam surface having a variable axial dimension so that the piston moves axially within the bore as the second leaf is rotated in relation to the first leaf;

a hydraulic fluid contained within the bore;

at least one of the piston and member including a passageway through which the hydraulic fluid may flow as the piston moves within the bore;

wherein the passageway includes an adjustable valve to restrict the flow of fluid to damp opening or closing of the hinge.

The closure is preferably a door, for example a wooden or glass door for a building. The closure may comprise a lid or cover. In a preferred embodiment the piston extends around the circumference of the member, the axial dimension of the cam surface varying angularly around the circumference.

The hinge is preferably mounted for rotation in a vertical axis. The invention is described for convenience in relation to a vertically extending hinge. However, it will be appreciated that the hinge may be arranged with the axis extending horizontally or in any other convenient direction. Orientation of the hinge in the vertical axis is advantageous because the weight of the door or other closure does not influence the closing or damping mechanisms.

The piston preferably has first and second ends, the first end forming a first sealed cavity within the bore and the second end forming a second sealed cavity within the bore, the passageway communicating between the first and second cavities.

Preferably the first cavity is an upper cavity above the piston and the second cavity is a lower cavity below the piston.

An elastomeric valve may be provided to seal the piston to the wall of the bore.

The elastomeric valve may comprise an annular member shaped to permit flow of fluid in one direction but to impede flow in the other direction.

In a preferred embodiment the elastomeric valve is arranged to be expanded by pressure of hydraulic fluid as the hinge is moved to a closed position, for example when the piston is pushed downwardly. The arrangement has the advantage that the fluid is forced through the passageway as the hinge is closed but may pass around the outer surface of the piston as the hinge is opened.

The piston is preferably prevented from rotation within the bore. A spline may extend lengthwise of the bore to engage a longitudinally extending slot in the piston. Alternatively, a projection of the piston may be received in a longitudinally extending slot in the bore. Preferably the outer surface of the piston has one or more planar portions, the inner surface of the barrel having corresponding shaped planar portions.

The needle valve preferably comprises a screw threaded member arranged when closed to restrict the cross-sectional area of the passageway for hydraulic fluid between the cavities. This may allow for easy adjustment of the valve using a screwdriver. The valve comprises a needle valve arranged to engage a circular valve seat when closed.

The passageway and valve may be provided within the axial spindle or member. Preferably the valve is provided within the member. This allows the valve to be rotated axially of the hinge.

In a preferred embodiment, the axially extending member may comprise a spindle mounted for axial rotation within the bore, the piston having an axial aperture through which the spindle extends.

The piston may comprise a cylindrical sleeve or collar having a cam surface preferably located at the upper or first end, which engages a cam follower of the spindle.

Alternatively the piston and internal surface of the barrel may have a non-cylindrical shape to prevent rotation of the piston relative to the barrel. For example the piston and barrel may be polygonal, for example hexagonal or may be formed with flat portions to prevent rotation.

The spindle preferably includes a first passageway communicating between the first sealed cavity and the valve and a second passageway communicating between the valve and the second sealed cavity.

The first and second passageways may communicate directly with the first and second sealed cavities respectively.

Alternatively in a preferred embodiment the second passageway may communicate with a piston passageway. The piston passageway may comprise one or more tubular ducts. More preferably the piston passageway may comprise a cylindrical or annular cutaway portion of the piston communicating with the second sealed cavity. For example a rebate may be formed at the lower end of the inner cylindrical surface of the piston.

The hinge preferably includes a variable damping valve arranged to control the damping force dependent on the angle between the leaves. In a preferred embodiment maximum damping is provided when the leaves is almost closed, for example 10° to 30° , preferably 15°.

The piston passageway may be configured so that communication with the second passageway portion of the spindle is prevented when the hinge is in a predetermined angular position. In the illustrated embodiment the piston is located in a lower position in this configuration. In this position flow of fluid past the piston is prevented. In this embodiment the communication between the second passageway and the piston passageway acts as a variable damping valve.

The use of a variable damping valve increases the damping of the hinge to a maximum value as the door or other closure reaches the fully closed position. Preferably the variable damping valve is arranged to reopen to reduce the damping force as hinge reaches the fully closed position to prevent slamming of the door. In this way the damping mechanism does not prevent latching or locking of the door. The hinge therefore provides a variable damping force. A constant damping force may be provided as the door is closed from a fully opened position with a greater damping force being provided at the final stage of the closing rotational movement. In this way slamming of the door is prevented without making it difficult to completely close and latch the door.

In a further advantageous modification, the variable damping valve is arranged to reopen as the hinge moves from an almost closed position to a fully closed position. In preferred hinges in accordance with this invention the cam of the piston is configured so that the axial movement of the piston opens or closes the variable damping valve to control the communication between the second passageway and the piston passageway. The configuration of the cam surface may be selected to provide closing and opening of the variable damping valve at a predetermined angle of the hinge leaves. A preferred angle is between about 10° to about 30°, or preferably about 15° . A closing hinge may be additionally provided to give a self closing door assembly.

In a preferred aspect of this invention there is provided a combination of a damped hinge assembly as previously disclosed, together with one or more sell closing hinges.

A spring may be provided to urge the piston within the bore towards the first or upper cavity. The spring may be located within the second or lower cavity extending between a lower end of the bore and the lower surface of the piston.

In a preferred embodiment, the cam surface comprises one or more spiral slots. The cam follower may comprise one or more projections extending radially from the spindle and located within a spiral slot. In preferred embodiments, two cam followers extend diametrically from the spindle within the bore and are engaged within respective spiral slots. The cam surfaces may be arranged to provide a horizontal portion so that the door may remain in an opened position but further arranged so that the door is urged into the closed position when displaced from the open position.

A door or other closure may be mounted on two or more hinges, a first damping hinge being constructed in accordance with this invention. A second closing hinge may be provided to facilitate automatic or self closing of the closure. The closing hinge may have a similar construction to the damped hinge but without the hydraulic fluid and valve arrangement.

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 is an exploded view of a closing hinge;

Figure 2 is an exploded view of a damped hinge in accordance with this invention;

Figure 3 comprises views of the pistons of the closing and damped hinges;

Figures 4-11 comprise cross-sectional views of the closing and damped hinges at different angular orientations;

Figure 12 shows the gasket at different angular orientations during opening of the hinge; Figure 13 shows the gasket at different angular orientations during closing of the hinge;

Figure 14 illustrates a gasket for use in a hinge in accordance with this invention; Figure 15 shows an alternative piston and barrel configuration for a closing hinge; and

Figure 16 shows a further alternative piston and barrel configuration for a damping hinge.

Figure 1 illustrates a closing hinge for use in a combination in accordance with this invention.

A leaf (1) is integrally secured to a cylindrical barrel (2) having an axial bore (3). In the illustrated embodiment the hinge is mounted for rotation in a vertical axis. The invention is described for simplicity with reference to a vertical axis. A second leaf (4) is integrally secured to upper (6) and lower (5) sleeves having an aperture (7) between them dimensioned to receive the barrel (2) to form a continuous hinge body.

A spindle (8) extends axially within the axial bore (3). The spindle has a key portion (9) arranged to be received in a socket (10) in order to constrain the spindle to rotate together with the second leaf (4) and sleeves (5,6) or to be held immobile as the leaf (1) rotates. A pair of diametrically opposed projections (11) extend radially from the spindle (8).

A cylindrical piston or slider (12) having an axial bore (13) is mounted for axial sliding movement on the spindle (8). Rotation of the piston is prevented by engagement of a channel (14) with a spline extending inwardly from the internal wall of the bore (3). The piston is urged upwardly by a spring (14). The hinge assembly is sealed by bearings (16,17) and sealing rings (18,19).

A pair of spiral slots (20) extend axially downwardly from the upper surface (21) of the piston (12). The cylindrical projections (11) are received within slots (20). The upwardly extending force of the spring (15) acting on the piston and slots (20) provides a pair of cam surfaces to urge rotation of the projections (11) into the closed position of the hinge as shown in Figure 4. In this way the closing hinge provides a self-closing arrangement. Successive steps of opening of the hinge are shown in the left hand drawings of Figures 4-11.

In Figure 8 the hinge is opened to 90 degrees and the projection (11) has reached the upper surface (21) of the piston (12). As the hinge opens further, as shown in Figures 9- 11, no further closing force is provided because the spring is fully compressed and cannot extend. In the fully open position shown in Figure 11 the projection (11) abuts against stop member (22) preventing further opening of the hinge.

Figure 2 is an exploded view of a damping hinge in accordance with this invention. The construction is similar to that of the closing hinge shown in Figure 1, although the piston (3) and spindle (31) are differently configured to accommodate the passages and valve assembly as described below.

A first leaf (32) is integrally connected to cylindrical barrel (33) having a cylindrical axial bore (34). A second leaf (35) is integrally secured to upper and lower sleeves (36,37) which have an aperture (38) between them to receive the barrel (33) to form a continuous hinge body. In use the second leaf may be screwed to a door frame and the first leaf to a door, or vice versa.

A spindle (39) extends axially within bore (34). The spindle has a key portion (40) shaped to receive and engage within socket (41) so that the spindle is constrained to rotate with the second leaf and sleeves (36,37). A pair of diametrically opposed cylindrical projections (42) extend radially from the spindle (39).

A piston (30) having an axial bore (43) is slidably mounted on the spindle (39). The piston (30) is urged upwardly by spring (44) to maintain engagement between the cam surface (45) and the cam follower projections (42). Projections (42) extend diametrically from the spindle and engage within the cam slots (45) as the hinge opens or closes.

Seals (46) and bearings (47) prevent leakage of hydraulic fluid from the hinge assembly. A threaded member (48) having a needle valve (49) is provided in top cap (50). An annular elastomeric valve (51) is mounted in a slot (52) extending circumferentially around a lower part of piston (30) to contact the inner wall of the bore in use. A plurality of apertures, for example 6 as illustrated allow fluid communication between the lower surface of slot (52) and the lower sealed cavity (60). This permits hydraulic fluid to inflate the valve (51) as the piston moves downwardly compressing fluid in the cavity (60).

Rotation of the piston (30) is prevented by engagement of a slot (52) with a projection (54) extending inwardly from the bore (33). This arrangement permits axial sliding of the piston within the bore without permitting rotation of the piston.

Threaded member (48) is mounted in a threaded bore in the top of spindle (39). A needle valve (49) located axially of the hinge extends axially from the threaded portion to close a first passageway (55) which communicates with a first sealed cavity (56). This is an upper cavity as illustrated between the upper surface of piston (30) and the top cap assembly of the hinge.

A second passageway (57) extends from the needle valve (49) to an outlet (58) on a lower part of the spindle. The outlet (58) communicates with a cylindrical cavity (59) in the lower part of the internal bore of the piston. The cylindrical cavity (59) communicates with a second (lower as shown) sealed cavity (60) located between the lower end of the piston and the sleeve (37) at the bottom of the hinge assembly.

Annular gasket (51) shown in Figure 14 comprises a ring having a downwardly opening annular channel (61). This arrangement causes the gasket (51) to expand radially and provide a tighter seal against the internal bore of the barrel as the piston moves downwardly when the hinge is closing to a predetermined acute angle. When the piston moves upwardly the gasket can contract so that the sealing engagement is less tight. This allows free return of the piston as the hinge is opened.

The maximum rate of flow of hydraulic fluid through the spindle and piston assembly may be controlled by screwing the threaded member (48) to open or close the needle valve (49). A variable damping valve is provided by selective opening or closing of the communication between the outlet (58) of the second passageway (57) of the spindle (39) and the annular cavity (59) of the piston (30) as shown in detail in Figures 12 and 13. Successive stages in opening or closing of the hinge are shown in Figures 4-11. The arrangement with the hinge closed at an angle of 0 degrees is shown in Figure 4. In this position the closing hinge has the spring (15) fully extended to urge the piston into the upper position (as shown). The projection (11) is at the bottom of the spiral cam channel (20).

The projections (42) of the damping hinge have passed the maximum axial extent (61) of the cam surface. The variable damping valve (58,59) is open.

In Figure 5 the hinge has opened to 15 degrees. The spring of the closing hinge is slightly compressed. The projections (42) have reached the over centre pass at the maximum axial extent (61) of the cam surfaces. The spring (44) is fully compressed and the second passageway (57) is disconnected from the cylindrical cavity (59). In this position the variable damping valve is closed so that the hydraulic fluid cannot pass between the first cavity (56) and the second cavity (60). The hinge is fully damped.

In Figure 6 the hinge is at an angle of 30 degrees. The projection (42) has passed the over centre maximum axial point (61) so that the compression of spring (44) is slightly released. The piston moves upwardly so that the variable damping valve (58,59) is opened. The upward movement of the piston compresses hydraulic fluid in the first cavity (56). The projections (42) enter the spiral cam slots (45) so that the piston (30) continues to move upwardly so that the pressure on the hydraulic fluid is increased to force the fluid to flow through the first passageway (55), through the needle valve (49) and through the second passageway (57) and cylindrical cavity (59) into the second cavity (60).

In Figure 7 the hinge is at an angle of 85 degrees. The projections (42) continue to enter the spiral cam slots (45) so that the piston is urged upwardly (as shown) by spring (44). The hydraulic fluid is pumped from the first cavity (56), through passageway (55), needle valve (49), passageway (57) and through the cylindrical aperture (59) into the second cavity (60). The maximum rate of flow of the hydraulic fluid may be controlled by opening or closing the needle valve. In this way the damping of the hinge can be adjusted to accommodate the weight of a door or other closure or to compensate for the conditions in which the door is used.

In Figure 8 the hinge is at an angle of 90 degrees. In this position the projections (11) of the closing hinge have reached an axially level part of the cam surface (21) so that no further closing force is exerted on the hinge and the door may be further opened without resistance.

The damping hinge remains with the variable damping valve open so that a damping force is applied preventing sudden opening or closing of the door.

In Figures 8 or 9 the opening movement is continued to angles of 135 degrees and 150 degrees respectively. Damping of the rotation of the hinge is continued as previously described.

In Figure 11 the hinge is fully open to an angle of 180 degrees.

During closing of the hinge the stage is illustrated in the Figures are reversed with maximum damping being achieved at an acute angle of 15° immediately prior to final closing the door or other closure by the closing hinge arrangement. In this way slamming is prevented without impeding closing and latching of the door.

Figure 15 shows various views of the barrel and slider arrangement for an alternative closing hinge. The barrel (70) is formed with hexagonal flat portions extending axially of the piston with corresponding hexagonal flat portions (73) extending axially of the interior bore of the barrel (74) attached to the leaf (75) as previously described. A spiral slot (72) is provided as previously described. It will be appreciated that the configuration of the external surface (70) of the barrel may be varied as convenient. For example, a cylindrical piston may be provided with one or more flat surfaces. Figure 16 shows an alternative configuration for a damping hinge in accordance with this invention. The piston (80) has a cylindrical surface into which a hexagonal array of flat surfaces (81) has been cut. The barrel (82) connected to leaf (83) has a corresponding series of hexagonal surfaces extending from the bore 84. In this arrangement, the piston (80) may slide within a limited range of the bore but is prevented from rotation by engagement of the respective hexagonal surfaces (81,85).

An annular rebate (86) serves to accommodate the elastomeric valve (not shown). A plurality, for example six, axially extending apertures (87) communicate with the lower cavity so that hydraulic fluid is forced into the annular space (86) to inflate the valve causing sealing of the cavity between the piston and bore. The axial cylindrical bore (88) serves to receive the spindle (not shown) as in the previously illustrated embodiments.

Claims

1. According to the present invention, a damped hinge comprises:

a first leaf for securing the hinge to a fixed support;

a second leaf for securing a moveable closure to the hinge;

a barrel secured to the first leaf, the barrel including an axial bore;

a hydraulic fluid contained within the bore;

2. A hinge as claimed in claim 1 wherein the piston has first and second ends, the first end defining a first sealed cavity within the bore and a second end defining a second sealed cavity within the bore, the passageway communicating between the first and second cavities.

3. A hinge as claimed in claim 2, wherein the first cavity is an upper cavity above the piston and the second cavity is a lower cavity below the piston.

4. A hinge as claimed in any preceding claim, further comprising an elstomeric valve to seal the piston to the wall of the bore.

5. A hinge as claimed in claim 4, wherein the elastomeric valve is arranged to be expanded by pressure of hydraulic fluid as the hinge is moved to a closed position.

6. A hinge as claimed in claim 5, wherein the elastomeric valve is a ring having an annular channel.

7. A hinge as claimed in any preceding claim, wherein the piston is prevented from rotation within the bore.

8. A hinge as claimed in claim 7 wherein the piston has one or more planar portions, the inner surface of the barrel having corresponding planar portions.

9. A hinge as claimed in claim 8 wherein the piston has polygonal outer surfaces.

10. A hinge as claimed in any preceding claim wherein the valve is a screw threaded valve.

11. A hinge as claimed in claim 10 wherein the valve is a needle valve located axially of the spindle.

12. A hinge as claimed in any preceding claim wherein the spindle includes a first passageway communication between the first sealed cavity and the valve and a second passageway communication between the valve and the second sealed passageway.

13. A hinge as claimed in claim 12 wherein the first and second passageways communicate directly with the first and second sealed cavities respectively.

14. A hinge as claimed in claim 12 wherein the second passageway communicates with a piston passageway, the piston passageway comprising one or more ducts communicating with the second sealed cavity.

15. A hinge as claimed in claim 14 wherein the piston passageway is an annular cutaway portion of the piston.

16. A hinge as claimed in any preceding claim including a variable damping valve arranged to control the damping force dependent on the angle between the leaves.

17. A hinge as claimed in claim 16 wherein the variable damping valve provides maximum damping when the leaves are at an acute angle.

18. A hinge as claimed in claim 17 wherein the acute angle is from 10° to 30°, preferably 15°.

19. A hinge as claimed in any of claims 14-18 wherein the piston passageway is configured so that communication with the second passageway portion of the spindle is prevented when the hinge is in a predetermined angular position.

20. A hinge arrangement comprising a combination of a hinge as claimed in any preceding claim together with one or more self-closing hinges.

21. A hinge or hinge arrangement substantially as hereinbefore described with reference to and as illustrated in the accompanying drawings.