EP2176486A1

EP2176486A1 - Hinge

Info

Publication number: EP2176486A1
Application number: EP08775089A
Authority: EP
Inventors: Eduard Thielmann; Wolfgang Beckmann; Ulrich Beneke; Jörn KLEFFMANN; Cord Rommelmann; Kai Michael Stuke
Original assignee: Hettich ONI GmbH and Co KG
Current assignee: Hettich ONI GmbH and Co KG
Priority date: 2007-08-10
Filing date: 2008-07-15
Publication date: 2010-04-21
Anticipated expiration: 2028-07-15
Also published as: AU2008286296A9; TWI421402B; JP5493134B2; ATE544930T1; DE202007011194U1; ES2385802T3; TW200925380A; CN101861441B; WO2009021799A1; JP2010535955A; EP2176486B1; AU2008286296B2; CN101861441A; AU2008286296A1

Abstract

A hinge (1), in particular for an item of furniture, comprises a hinge part (2) which can be fixed to a door (6) or flap and is mounted pivotably on a side part (3) via a supporting lever (7) and a guide lever (8), wherein the side part (3) is mounted on an installation plate (4), which can be fitted to a furniture body (5), and at least one spring (18) by means of which the hinge part (2) is prestressed into a closed position in an automatic tightening region, and a linear damper (11) with a piston rod (13) which is movable relative to a damper housing (12) and is intended for damping a closing movement of the hinge part (2), wherein the damper (11) is designed as a compression damper, and a deflecting element (10) is provided, said deflecting element being coupled to the damper (11) and being movable via a tension lever (9) during a closing movement of the hinge part (2).

Description

hinge

The present invention relates to a hinge, in particular for furniture with a lockable on a door or flap hinge part, which is mounted on a support lever and a guide lever pivotally mounted on a side part, wherein the side part is held on a mountable to a furniture body mounting plate, and at least one spring, by means of which the hinge part is biased in a self-closing range in a closed position, and a linear damper with a relative to a damper housing movable piston rod for damping a closing movement of the hinge part.

DE 20 2006 003 196 discloses a furniture hinge in which a hinge part is pivotally mounted on a support lever and a guide lever. On the guide lever, a boom is provided with a piston rod of a

Damper is coupled. Upon a closing movement of the hinge part of the damper is effective, the piston rod pulls the piston out of the damper housing so that it acts as a damper. Although this furniture hinge has a compact design, it has the disadvantage that the damping curve is not adjusted so sensitively by the direct coupling of the piston rod to the guide lever. In particular, there is also the problem that the dampers acting on the train are subject to wear in the sealing area, so that the damping properties can change.

EP 1 555 372 discloses a furniture hinge in which a hinge part is mounted on a side part via a guide lever and a support lever. In the side part of a linear damper is received, the piston rod protruding, which is connected in the manner of a link chain with a boom on the guide lever. This allows the geometry of the boom and the connecting elements to modify the damping properties when closing the hinge part, but the problem remains that over the life of the damper, the damping properties change, especially because exposed to the open side of the damper housing, the seal wear is and therefore the capacity of the damper is limited. If the damping force is too sudden lϊch occurs, then there is the problem that a furniture door springs back during the closing movement, which is perceived by the user as disturbing. If the damping setting is too weak, a bang can occur due to the furniture door being hit against a furniture carcass.

It is therefore an object of the present invention to provide a hinge, especially for furniture, which allows a reliable damping of the hinge part when closing even after many closing operations and in which the damping effect is optimally adapted to different installation situations.

This object is achieved by a hinge with the features of claim 1.

According to the invention, the damper is designed as a pressure damper and there is provided a deflecting steering element, which is coupled to the damper and is movable by a pulling lever during a closing movement of the hinge part. As a result, a tensile force on the pull lever is converted into a compressive force when closing the hinge part, which acts on the damper when closing. The damper is only subjected to pressure during the closing movement, so that a load on the seal arranged around the piston rod turns out to be comparatively small.

Because the pressure force acts only on the closed side of the potfföπnigen housing, which is relatively stable. At least it does not claim the housing closing seal, which is arranged around a movable piston rod. This ensures a long service life and, moreover, the damping characteristics remain almost the same even after a large number of actuation cycles.

According to a preferred embodiment of the invention, the deflecting element is rotatably mounted on the side part and at a tensile force by the pulling lever a compressive force is exerted on the damper. In this case, the deflecting element can be coupled directly to one end of the piston rod, so that the rotational movement of the deflecting element is converted into a linear lifting movement of the piston rod. For this purpose, the damper is pivotally mounted on the closed end of the damper housing. Preferably, the damper is effective between an opening angle of at least 25 °, preferably at least 40 ° and a closed position of the hinge part, so that-damping takes place over a comparatively long pivoting path. This allows for a defined closing of the hinge part, which is comparatively independent of the initial closing speed of the hinge part and any weight forces of the component connected to the hinge part. Because the damper absorbs an initial kinetic energy until the closing parameters predetermined by the spring and the damper are reached.

In order to realize a long damping path effectively, the stroke of the damper is 4 to 20 mm, preferably 5 to 10 mm. As a result, with a compact construction, sufficient damping can be obtained when closing the hinge part.

In order to effect a predetermined damping curve on the hinge, the gear ratio in a closing movement of the carousel in a range of 15 ° before the closed position to the closed position is preferably selected such that between the pivoting angle of the hinge part and the stroke of the damper per Degree closing movement a stroke of 0.05 mm to 0.24 mm, preferably 0.14 mm to 0.18 mm is achieved. Especially in the end region before the closing position of the damper to ensure a defined closing a door or a flap, so that here comparatively high damping forces and thus a large stroke of the damper must be present based on the closing movement. However, the stroke must not be too large, otherwise there is a risk of damage to the hinge due to overload forces. In this respect, it is advantageous if the damping increases steadily when closing the hinge part, so that shocks are avoided. In addition, in an opening region between the closed position and an opening angle of 30 °, the damper can be moved more than 60%, preferably more than 70%, of its entire stroke, so that a high damping is achieved in an end region in front of the closed position. In the opening direction, the Dämpfüngswirkung despite corresponding movement of the piston rod of the damper is low, but this through corresponding design of the piston is achieved in the damper housing. Such substantially unidirectional damper are known.

Preferably, by the effectiveness of the spring self-tightening of the hinge part is achieved by the hinge part is automatically moved to the closed position. A Selbstanzugsbereich is that area in which the hinge part is moved only by the force of a spring in the closed position and no further forces are necessary for movement. It ends where the force of the spring is insufficient to move the hinge part to the closed position. This self-tightening area can, for example, in a range between

Start 20 ° and 50 °, preferably 30 ° to 45 ° and act to the closed position.

In order to make handling with a built-in hinge as pleasant as possible, the spring is preferably effective in a first opening area adjacent to the closing position in the closing direction (self-tightening) and in a second opening area, the spring biases the hinge part in the opening direction.

The spring force may preferably reach a maximum value in an opening angle range of 15 ° to 45 °, in particular 20 ° to 40 °, and may decrease again in other areas. As a result, the material stress of the spring

Opening the hinge part kept low, which increases the life.

The spring may be formed as a leg spring having a first leg coupled to the hinge part and a second leg coupled to an axis on a cantilever of the guide lever. In order to enable tracking of the spring, the spring can be rotatably mounted on an axis of the support lever.

In order to reduce the material load when moving the hinge part on the spring, the leg of the spring coupled to the deflection element can be attached to a spring

Abut pulley. The deflection roller reduces the frictional forces on the usually comparatively short leg of the spring in which high loads occur. As a result, the life of the spring and thus of the entire hinge is considerably increased. In a further advantageous embodiment of the invention damper and spring are designed so that in a closing movement of the hinge part in an opening range between 4 ° and 0 °, preferably 8 ° and 0 ° a substantially constant closing speed is present. Because by appropriate

Tuning the damper and the spring and the transmission ratio, it is possible to damp a kinetic energy of a closing door or door so that regardless of an initial closing speed in an opening area shortly before the closed position, the closing speed almost exclusively of the spring force and the damper depends and thus can be optimized. This is achieved in that the damper generates forces against the closing direction even at a larger opening angle.

The invention will be explained in more detail using an exemplary embodiment with reference to the attached drawings. Show it:

Figure 1 is a side view of an invention eπ hinge in the installed position;

Figure 2 is a perspective view of the hinge of Figure 1;

Figure 3 is a sectional side view of the hinge of Figure 1;

Figure 4 is an exploded perspective view of the hinge of Figure 1;

Figure 5 A to 5 G several sectional side views of the hinge of the

Figure 1 in different opening positions;

Figure 6 is a graphical representation of the damping path depending on the opening angle of the hinge;

Figure 7 is a graphical representation of the closing force of the spring of

Hinges, depending on the opening angle, and Figure 8 is a graphical representation of the closing speed of the spring of the hinge, depending on the Öffhungswinkel.

A hinge 1 comprises a hinge part 2, which is pivotable on a side part

3 is stored. The side part 3 is held on a mounting plate 4, which is mounted on a furniture body 5, such as a cabinet. On the hinge part 2, a door, flap or other component is defined. As shown in FIG. the door 6 can be moved from a closed position to an open position 6 'shown in dashed lines, wherein the maximum opening angle p is in a range between 90 ° and 120 °, preferably 100 ° to 110 °.

In Figures 2 and 3, the hinge 1 is shown, in which the side part 3 is adjustable, with a first adjusting screw 16 for a displacement of the side part 3 relative to the mounting plate 4 and a further adjusting screw 17 is provided for a support adjustment ,

The hinge part 2 is rotatably mounted on a support lever 7 and a guide lever 8, wherein the boom 25 of the guide lever 8, a pull lever 9 is articulated. The pull lever 9 is connected to a rotatable deflection element 10, which is coupled to a linear damper 1 1.

The damper 11 has a pot-shaped damper housing 12, from which a piston rod 13 protrudes. The piston rod 13 is pivotally connected to the deflecting element 10. At the side facing away from the piston rod 13 side of the damper housing 12 this is rotatably mounted on the side part 3. The side part 3 is fixed by a spring-loaded locking lever 15 on the mounting plate 4.

In FIG. 4, the hinge with its individual parts is shown in an exploded view. Between the support lever 7 and the guide lever 8, a spring 18 is provided which has two legs 19 and 20 and can bias the hinge part 2 in an open or closed position. In FIGS. 5A to 5G, the part of the hinge 1 relevant for the damping behavior during the closing movement of the hinge part 2 is shown. The hinge part 2 is connected via an axis 21 with the support lever 7 and via an axis 22 with the guide lever 8. Between the support lever 7 and guide lever 8, the spring 18 is arranged, wherein the spring 18 is designed as a leg spring and is rotatably mounted in its helical region about an axis 23, wherein the axis 23 also forms the pivot bearing of the support lever 7 on the side part 3. The guide lever 8 is rotatably mounted on the side part 3 via an axis 24.

On the guide lever 8, a boom 25 is formed on which an axis 26 is provided, on which the pull lever 9 is rotatably mounted. At the opposite end of the pull lever 9, an axis 29 is provided which connects the pull lever 9 with the lever 10. The deflecting element 10 is mounted on the side part 3 about an axis 27, the axis 27 being arranged between the axis 29 for connection to the pull lever 9 and an axis 28 for coupling the deflecting element 10 to the piston rod 13. Furthermore, a latching receptacle 30 is still shown on the damper housing 12 on the side facing away from the piston rod 13, so that the damper housing 12 is rotatably connected to the locking receptacle 30 with the side part 3 and transverse forces are avoided on the piston rod 13. By an embodiment of the connection between the piston rod 13 and

Axle 28 as Rastau fn ahme the damper 11 can also be retrofitted.

In Figure 5A, the hinge part 2 is shown in the maximum opening position, in which a first leg 19 of the spring 18 rests on the axis 22 and the second leg 20 on a deflection roller 40 (Figure 4), which is mounted on the axis 26.

In Figure 5B, the position of the hinge part 2 is shown, in which the hinge part 2 has been moved from the maximum opening position to an opening angle of about 85 °. The leg 19 of the spring 18 now abuts both the axis 22 and the axis 21 and is in this position "transferred" from the axis 22 to the axis 21. From the maximum open position up to the opening angle of 85 ° is Spring 18 no spring force introduced, since the spring 18 is indeed tense, but rotates about the axis 26 and the angular position of the legs 19 and 20 remains substantially constant. In a further closing movement of the hinge part 2, the leg 19 is moved through the axis 21, so that the spring 18 is further tensioned. The opposite leg 20 continues to abut against the deflection roller 40 on the axis 26. The spring 18 thus acts in a range between about 85 ° and 55 ° (see

5C) in the opening direction of the door or the hinge part 2, i. contrary to the closing movement. The damper acts only slightly in this hinge position, since the angular positions of the coupling members boom 25 on the guide lever 8, pull lever 9 and lever 10 so pretend.

In FIG. 5D, the opening position of the hinge part is shown at an angle of approximately 55 °. Upon reaching this opening angle, the axes 21, 22 and 24 form a line. The spring 18 is in the maximum tensioned position in which the legs 19 and 20 are maximally spread. When this position is passed, and the hinge part 2 is moved further in the closing direction, the spring begins

18 to act in the closing direction and it enters the so-called self-suit. However, since at the beginning by friction, tolerances and other influences, the slight force of the spring 18 is not felt, the real self-tightening angle, in which the hinge part 2 is biased in the closed position, at about 40 °.

The damper 11 is actuated by the deflecting element 10 from an opening angle of about 45 ° noticeably, with a certain idle stroke, tolerances and other influences a damping only noticeably noticeable at an angle between 30 ° and 40 °. This is due to the fact that the damper 11 in an opening area, between an opening angle of 30 ° and the

Closed position is moved by more than 60%, preferably more than 70%, of its entire stroke, but in the opening area outside 30 ° performs only a small lifting movement.

In order to reduce the working stroke of the spring 18 after exceeding the extended position, and at the same time keep the forces acting on the system in the closing direction sufficiently high, the leg 20 is nachfühlt on the guide roller 40, that is, after passing through the extended position of the leg 20 through the Bearing of the guide roller 40 on the axis 26 moves counterclockwise, while the leg 19 is also moved by bearing on the axis 21 in the counterclockwise direction. The relative movement of the legs 19 and 20 is thus very low and the spring 18 is pivoted about the axis 23. Insofar it is possible to first increase the spring force when closing the hinge part 2 and then let it fall off again.

In Figure 5F, the hinge part 2 is shown in an open position of about 25 °. The spring 18 now presses the hinge part 2 in the closed position, wherein the spring 18 is stretched over the legs 19 and 20. In this position, the deflecting element 10 is then rotated about the axis 27 when closing and causes a larger working stroke of the piston rod 13 relative to the damper housing 12 than in the previous closing movement of the hinge part. 2

In Figure 5G, the hinge is shown in an ex tending angle, in which the hinge part 2 has already been slightly moved over the closed position. Only in this Überschließposition the spring 18 no longer exerts force on the legs 19 and 20 on the hinge part 2. This ensures that at normal closing angle (0 °), the hinge part 2 is biased by the spring 18 in the closed position. In the closed position, the piston rod 13 is arranged in the almost maximum retracted position in the damper 12.

As a damper, a linear damper can be used, as it is disclosed for example in the application PCT / EP 2007/051849. Other types of linear dampers can be used.

In FIG. 6, a representation of the damping path is dependent on the opening angle of the hinge 2. The translation of the closing movement of the hinge part 2 by the guide lever 8, the pull lever 9, the deflection element 10 onto the damper 11 results in predetermined transmission ratios depending on the opening angle that ensure optimal closing. As can be seen from the graph, takes place up to an opening angle of 45 ° in a closing movement less than 10% of the total stroke of the damper, so that the piston rod 13 moves only slightly in the damper housing 12. There are barely noticeable damping forces generated, but at higher speed already achieve an effect so that a moving furniture part is braked down without preventing the secure closure. For most linear dampers, an idle stroke of approx. 0.8 mm to 1.5 mm, in particular 1 mm to 1.3 mm, must also be taken into account. As a result, it is ensured in the construction that the damper is only noticeably effective in an angle range between 30 ° and 45 °.

The hinge is designed so that the damper initially generates weak damping forces during a closing movement, which then increase at a constant closing speed. Because the working stroke of the damper rises in an opening range between an opening angle of 25 ° and the closed position almost linearly, while at larger opening angles of the damper is hardly moved relative to the closing movement. The gear ratio is selected so that in an opening region between the closed position and an opening position of 15 ° per degree closing movement of the hinge part a working stroke between 0.05 mm to 0.2 mm, preferably 0.08 mm to 0, 12 mm takes place.

The working stroke of the damper does not stop abruptly, but rises in curves. This ensures that no shock-like forces act on the damper, but the kinetic energy of a furniture door is initially slightly damped.

The changing translation of the pivoting movement of the hinge part 2 on the damper stroke is achieved by the angular positions of boom 25 on the guide lever 8, 9 and lever lever 10 to each other. With a large opening angle, these are almost in line, in particular boom 25 and pull lever 9, but at right angles with small opening angles, as a result of which the pull lever 9 transmits the movement of the boom 25 very directly to the deflection lever 10.

The ratio between the hinge part 2 and the damper 11 is such that at an opening angle of the hinge part 2 of approximately 80 ° to 110 °, the angular positions of the boom 25 on the guide lever 8 and pull lever 9 approximately 180 °, ie the axis 24 of the Guide lever 8, the axis 26 for supporting one side of the pull lever 9 and the axis 29 for supporting the opposite side of the pull lever 9 on the lever 10th lie in about a line. In this case, the deflection lever 10 forms an acute angle with the pull lever 9 forms. At an opening angle of the hinge part 2 of approximately 0 ° to 40 °, the angular positions of boom 25 on the guide lever 8 and pull lever 9 approximately form a right angle of 90 °, in particular the connecting lines of the axes 24, 26 and 29, wherein the lever 10 also forms a right angle with the pull lever 9, in which case the axes 26, 29 and 27 can be connected to each other via two approximately at right angles intersecting lines.

In Figure 7, the closing force of the spring 18 is shown relative to the opening angle. As can be seen from the graph, the spring 18 presses the hinge part 2 in a self-tightening area in the closed position. The force of the spring 18 has a maximum value in an opening angle range between 15 ° to 25 °, and then decreases until the force of the spring 18 reaches a minimum value between 50 ° and 75 °. As a result, the maximum stress of the spring 18 is limited.

FIG. 8 shows the speed of the closing speed relative to the opening angle, wherein different initial closing speeds are present. Depending on the speed of the closing movement, damping must first be applied to slow down the door. The braking range is approximately between 45 ° and 15 °. The higher the initial speed, the later a low final speed is achieved. At a smaller angle, the damping force increases due to the changing leverage (see Figure 6), which ensures that is effectively decelerated even at very high initial speeds.

The closing speed is just before the closing position, for example in a range between 0 ° and at least 3 ° approximately linearly constant. After slowing down the kinetic energy, the system works autonomously, ie the

Force of the spring 18 and the damper determine the closing speed.

Before the linear final speed is reached, small "undershoots" are drawn in, ie an undershooting of the final closing speed. This Swingarms are due to the elastic behavior of individual hinge components. During heavy deceleration they are tensioned by the movement and then spring back as soon as the damping force subsides. Thanks to the rigid design of all components and in particular the articulated connections, the result is a low "rebound" effect without zero crossing of the speed, so there is no knocking back of the hinge part 2.

As can be seen in FIG. 8, the self-tightening begins at approximately 45 ° by the spring 18, braked by the damper.

Since the damper provides a speed-dependent force against the closing direction and the spring but a speed-independent force in the closing direction, higher closing Anfangsgeschwindigkeiteπ are effectively braked down so that in the last angular range before closing the closing speed is independent of the initial S chließgesch wind speed.

Claims

claims

1. hinge (1), in particular for furniture, with a hinged to a door (6) or flap hinge part (2) via a support lever (7) and a guide lever (8) pivotally mounted on a side part (3) is, the

Side part (3) on a mounting on a furniture body (5) mounting plate (4) is held, at least one spring (18) by means of which the hinge part (2) is biased in a Selbstanzugsbereich in a closed position and a linear damper (1 1 ) with a relative to a damper housing (12) movable piston rod (13) for damping a closing movement of

Hinge parts (2), characterized in that the damper (11) is designed as a pressure damper and a deflecting element (10) is provided, which is coupled to the damper (1 1) and during a closing movement of the hinge part (2) via a pull lever ( 9) is movable.

2. Hinge according to claim 1, characterized in that the deflecting element (10) is rotatably mounted on the side part (3) and converted by the deflecting element (10) a tensile force by the pull lever (9) in a compressive force on the damper (11) becomes.

3. Hinge according to claim 1 or 2, characterized in that the damper (11) during the closing process between an opening angle of the hinge part (2) of at least 25 °, preferably at least 40 ° and a closed position is effective.

4. Hinge according to one of claims 1 to 3, characterized in that the damper (I I) is moved in an opening region between an opening angle of 30 ° and the closed position by more than 60%, preferably more than 70% of its total stroke.

5. Hinge according to one of claims 1 to 4, characterized in that the stroke of the damper (11) in a range between 4 to 20 mm, preferably 5 to 10 mm.

6. Hinge according to one of claims 1 to 5, characterized in that the transmission ratio between the pivot angle of the hinge part (2) and stroke of the damper (11) during a closing movement of the hinge part (2) in a range up to 15 ° before the closed position per Degree of closing movement is 0.06 to 0.24 mm, preferably 0.14 to 0.18 mm.

7. Hinge according to one of claims 1 to 6, characterized in that the spring (18) in a first Öffnungsb area adjacent to the closed position in the closing direction is effective and in a second Öffnungsb area the spring (18) the hinge part (2) in Biases opening direction.

8. Hinge according to one of claims 1 to 7, characterized in that the spring (18) is designed as a leg spring having a first with the hinge part (2) coupled leg (19) and a second with an axis (26) on the Boom (25) of the guide lever (8) coupled leg (20).

9. Hinge according to one of claims 1 to 8, characterized in that the spring (18) is rotatably mounted on an axis (23) of the support lever (7).

10. Hinge according to one of claims 1 to 9, characterized in that the spring (18) is nachgefühlt to avoid overstretching during pivoting of the hinge part (2) in the maximum opening position.

11. Hinge according to one of claims 1 to 10, characterized in that the spring force of the spring (18) in an opening angle range between 15 ° to 45 °, preferably 20 ° to 40 °, reaches a maximum value.

12, hinge according to one of claims 1 to 11, characterized in that with the axis (26) coupled leg (20) of the spring (18) on a deflection roller (40).

13. Hinge according to one of claims 1 to 12, characterized in that the self-tightening angle of the hinge part (2) by the spring (18) in a range between 20 ° to 50 °, preferably between 25 ° to 35 °.

14. Hinge according to one of claims 1 to 13, characterized in that the damper (11) and the spring (18) are designed so that during a closing movement of the hinge part (2) in an opening range between 0 ° and 4 °, preferably 0 ° and 8 ° a substantially linearly constant closing speed is present.

15. Hinge according to one of claims 1 to 14, characterized in that the deflecting element (10) with the piston rod (13) is coupled, which is displaceably guided in the cup-shaped damper housing (12).

16. Hinge according to one of claims 1 to 15, characterized in that the damper housing (12) is rotatably mounted on the piston rod (13) facing away from the side part (3).

17. Hinge according to one of claims 1 to 16, characterized in that the damper housing (12) and / or the piston rod (13) is connected via latching means with the deflecting element or the side part.

18. Hinge according to one of claims 1 to 17, characterized in that the transmission ratio between the hinge part (2) and damper (11) is such that at an opening angle of the hinge part (2) of approximately 80 ° to 110 °, the angular positions of Boom (25) on the guide lever (8) and pull lever (9) approximately 180 °, wherein the reversing lever (10) forms an acute angle with the pull lever (9), and at an opening angle of the hinge part (2) of approximately 0 ° to 40 °, the angular positions of the arm (25) on the guide lever (8) and pull lever (9) approximately 90 °, wherein the reversing lever (10) also forms an approximately 90 ° angle with the pull lever (9).