Furniture hinge

Abstract

The invention relates to a furniture hinge comprising a fastening section and a hinge arm, with a multi-axle articulation enabling movement of the hinge arm in an opening motion and a closing motion, and an energy storage providing for a driving force supporting at least part of the opening and the closing motion, wherein the multi-axle articulation comprises an articulation lever assembly guiding the opening and closing motion, and a transmission lever assembly transmitting the driving force from the energy storage to the articulation lever assembly. Reliable and smooth operation is achieved in that a closing force adjustment mechanism is provided which allows for an adjustment of a degree of support of the closing motion relative to a degree of support of the opening motion provided by the energy storage by means of a positional adjustment of an adjustable joint of the transmission lever assembly relative to the fastening section.

Description

[0001] Furniture hinge

[0002] The invention relates to a furniture hinge, in particular a flap fitting, comprising a fastening section for fastening to a piece of furniture and a hinge arm for fastening to a movable furniture part, in particular a flap, wherein a multi-axle articulation is provided which connects the hinge arm to the fastening section and enables movement of the hinge arm from a closed position to an open position in an opening motion and from the open position to the closed position in a closing motion, wherein an energy storage is provided which provides for a driving force supporting at least part of the opening and the closing motion, wherein the multi-axle articulation comprises an articulation lever assembly forming at least part of a linkage which guides the opening and closing motion, and a transmission lever assembly comprising multiple joints and multiple transmission levers, which transmission lever assembly forms at least part of a linkage transmitting the driving force from the energy storage to the articulation lever assembly.

[0003] DE 10 2014 113 967 A1 discloses a furniture hinge in the form of a flap fitting which comprises a fastening section for fastening to a furniture corpus and a hinge part for fastening to a flap. The flap fitting further comprises a multi-axle articulation which enables movement of the hinge part relative to the fastening section. The multi-axle articulation comprises a plurality of levers interconnected by joints. To support an opening and a closing motion, the flap fitting further comprises a spring that is coupled to the multi-axle articulation.

[0004] In furniture hinges of the type mentioned in the beginning, the amount of support required for both the support of the opening as well as the closing motion may depend on the intended use. In particular, the amount of required support may depend on a size and / or a weight of the movable furniture part to be connected to the furniture hinge. Furthermore, depending on the intended installation situation, it may be the case that different requirements arise for the support for the closing and for the support of the opening motion. For instance, in the case of a flap fitting which is intended for flaps opening upwards against the force of gravity, a larger degree of support of the opening motion may required and a lesser degree of support of the closing motion may be required. As another example, in the case of a flap or door fitting which is intended for opening in a horizontal direction, such as in an upright cabinet, the amount of support required for both motions may be equal. As yet another example, a flap intended to open downwards may require more support for the closing than for the opening motion. These differences in requirements for support of the opening in contrast to the closing motion may be more pronounced with heavier doors or flaps. Further, if a damper is provided for damping the opening and / or the closing motion, the support of the opening and / or closing motion should be sufficient to reliably open and / or close the flap or door against the force of the damper. On the other hand, in order to provide for smooth opening and / or closing of the flap or door, the support should not be so strong that it overpowers the damper. Consequently, it may be desirable that the amount of support provided by the energy storage is adjustable to the characteristics of the damper.

[0005] It is also conceivable that, over a period of use, wear of components of the furniture hinge, such as the energy storage and / or the damper, may lead to the necessity of a readjustment of the degree of support of the closing motion relative to the degree of support of the opening motion.

[0006] Summarizing, requirements regarding support of the closing and the opening force may vary due to a number of reasons, for instance the weight of the flap / door to be connected, the installation situation and / or wear of components of the hinge. It is desirable that these varying requirements may be accommodated by the furniture hinge.

[0007] Therefore, the object of the invention is to provide a furniture hinge of the type mentioned in the beginning that enables reliable and smooth opening and closing even when requirements regarding support of the closing and the opening motion vary.

[0008] This object is achieved in that a closing force adjustment mechanism is provided which allows for an adjustment of a degree of support of the closing motion relative to a degree of support of the opening motion provided by the energy storage by means of a positional adjustment of an adjustable joint of the transmission lever assembly relative to the fastening section. The adjustment of the degree of support of the closing motion relative to the degree of support of the opening motion may be referred to as closing force adjustment. Consequently, the invention provides the advantage that closing force adjustment can be achieved in a way that is both structurally simple and robust. Further, closing force adjustment can be easily performed by a user because it may be achieved by simply adjusting the adjustable joint.

[0009] An opening angle may reflect an angular position of the hinge arm between the closed and the open position. The opening angle may be defined to, in the closed position, have a value of zero. In the open position, the opening angle may have a non-zero value. For instance, the opening angle may be at least 90°, preferably at least 100°, more preferably at least 110° in the open position. During the opening and the closing motion, there may exist a force reversal point in which a switch occurs between the support of the opening and the support of the closing motion. The force reversal point may correspond to an opening angle of the hinge arm in which the line of action the force transmitted at the eighth joint intersects the pivot axis of the first joint. Preferably, the opening angle at the force reversal point may correspond to a range between 10° and 30°, more preferably, and as in the present embodiment, between 15° and 25°.

[0010] As a consequence of the support of the opening and closing motion, the user may need to, in order to move the hinge arm from the closed position, overcome the closing force exerted by the driving force until the force reversal point is reached. During the opening motion, after the force reversal point, support of the opening motion may take place. Preferably, the support of the opening motion is such that the further opening motion is performed without further actuation by the user. Similarly, in order to move the hinge arm from the open position, the user may need to overcome the support of the opening motion until the force reversal point is reached. During the closing motion, after the force reversal point, support of the closing motion may take place. Preferably, the support of the closing motion is such that the further closing motion is performed without further actuation by the user.

[0011] According to a preferred variant of the invention, it is proposed that the transmission lever assembly comprises at least one stationary joint which remains stationary relative to the fastening section at least during the opening and the closing motion. A stationary hinge may, nonetheless, be adjustable, in particular positionally adjustable relative to the fastening section. Preferably, the transmission lever assembly may comprise two stationary joints. Advantageously, the adjustable joint may be a stationary joint. This way, the adjustable joint may, on the one hand, remain stationary relative to the fastening section during operation (i.e., during at least the opening and closing motion) such that a mechanically reliable operation is ensured. On the other hand, the adjustable joint may be easily adjusted for closing force adjustment. Preferably, the adjustable joint may be adjusted when the hinge arm is in the open position, which may provide for easy access to the adjustable joint.

[0012] Preferably, it may be provided that the energy storage is, directly or indirectly, pivotably coupled to an actuating lever of the transmission lever assembly. A working angle may be defined between a line of action of the driving force and a lever axis of the actuating lever. The lever axis may be a straight line connecting two lever pivot axes associated with the actuating lever. By further provision for one of these lever pivot axes to be the lever pivot axis of the adjustable joint, it may be achieved in a structurally simple and mechanically robust manner that the positional adjustment results in an adjustment of the working angle.

[0013] The working angle may change during the opening and the closing motion. In other words, the working angle may not be a constant during operation of the furniture hinge. In this context, it is proposed that that the positional adjustment results in an adjustment of the working angle at least one of in the closed position, in the open position, during the opening motion, during the closing motion, at a force reversal point, in which a switch occurs between the support of the opening and the support of the closing motion.

[0014] In accordance with an advantageous further development of the invention the working angle may be a function of an opening angle of the hinge arm, which opening angle reflects an angular position of the hinge arm between the closed and the open position. In the context of the functional relationship between the working angle and the opening angle, closing force adjustment may be achieved in an advantageous manner if the positional adjustment alters the functional relationship between the working angle and the opening angle.

[0015] In this context, it may further be provided that a first moment arm of the driving force with respect to an actuating lever pivot axis around which the actuating lever is pivotable is a function of the working angle, preferably a function comprising a trigonometric function of the working angle. In particular, the first moment arm may be proportional to sin(working angle). Closing force adjustment may preferably be achieved in that, by altering the functional relationship between the working angle and the opening angle, a ratio of a maximum of the first moment arm occurring during support of the closing motion to a maximum of the first moment arm occurring during support the opening motion is modified. Consequently, the closing force adjustment may be based on and / or comprise effects of altered lengths of the first moment arm during the support of the opening and closing motion.

[0016] To achieve a compact design of the furniture hinge as well as an efficiently modifiable functional relationship between the working angle and the opening angle, it is proposed that the working angle, as a function of the opening angle, exhibits an extremum during the opening and closing motion. The extremum may correspond to the force reversal point, in which a switch occurs between the support of the opening and the support of the closing motion. The force reversal point may preferably correspond to an opening angle between 10 and 30°, more preferably between 15° and 25°.

[0017] Additionally or alternatively, closing force adjustment may be advantageously achieved in that a connecting angle is formed between lever axes of two of the transmission levers, which transmission levers are pivotably connected to one another at a joint, wherein the lever axes are straight lines connecting two lever pivot axes of joints associated with the respective transmission lever. In this context, it may be preferable that the positional adjustment of the adjustable joint results in an adjustment of the connecting angle.

[0018] The connecting angle may change during the opening and the closing motion. In other words, the connecting angle may not be a constant during operation of the furniture hinge. In this context, it is proposed that in that the that the positional adjustment results in an adjustment of the connecting angle at least one of in the closed position, in the open position, during the opening motion, during the closing motion, at a force reversal point, in which a switch occurs between the support of the opening and the support of the closing motion.

[0019] In accordance with an advantageous further development of the invention the connecting angle may be a function of the / an opening angle of the hinge arm, which opening angle reflects the angular position of the hinge arm between the closed and the open position. In the context of the functional relationship between the connecting angle and the opening angle, closing force adjustment may be achieved in an advantageous manner if the positional adjustment of the adjustable joint alters the functional relationship between the connecting angle and the opening angle.

[0020] In this context, it may further be provided that a second moment arm of a force transmitted at the joint connecting the two of the transmission levers relative to the pivot axis of another joint associated with one of the two of the transmission levers is a function of the connecting angle, preferably a function comprising a trigonometric function of the connecting angle. In particular the second moment arm may be proportional to cos(180°-connecting angle). Closing force adjustment may preferably achieved in that, by altering the functional relationship between the connecting angle and the opening angle, a ratio of a maximum of the second moment arm occurring during the closing motion to a maximum of the second moment arm occurring during the opening motion can be modified. Consequently, the closing force adjustment may be based on and / or comprise effects of altered lengths of the second moment arm during the support of the opening and closing motion.

[0021] To achieve a compact design of the furniture hinge as well as an efficiently modifiable functional relationship between the connecting angle and the opening angle, it is proposed that the connecting angle, as a function of the opening angle, exhibits an extremum during the opening and closing motion. The extremum may correspond to the force reversal point, in which a switch occurs between the support of the opening and the support of the closing motion, wherein the force reversal point preferably corresponds to an opening angle between 10° and 30°, more preferably between 15° and 25°.

[0022] Adjustability of the adjustable joint may be achieved by simple and reliable means if it is provided that the position of the adjustable joint relative to the fastening section is adjustable in a linear direction. The linear direction may have at least a predominant component parallel to the line of action of the driving force.

[0023] In a particularly preferred variant of the invention, the adjustable joint may be provided on a connecting part, wherein the connecting part is displaceably held at a support member, which support member is provided stationary relative to the fastening section. In order to accommodate for different settings of the closing force adjustment, it may be provided that the connecting part can be fixed, preferably releasably, to the support member in a plurality of positions by means of a fixing element. For instance, the fixing element may be a bolt which may enable clamping of the connecting part to the support member in a plurality of relative positions.

[0024] In this context, it is further proposed that the support member comprises a receiving space in which the connecting part is partially received. Linear adjustability and releasable positioning of the connecting part may be achieved in that the support member comprises an elongated slot providing for an access to the receiving space, and in that the fixing element is guided through the slot toward the connecting part.

[0025] The invention will be further described by way of example with reference to the drawings, in which:

[0026] Fig. 1 is a schematic view of a furniture hinge with a hinge arm in a closed position, Fig. 2 is a schematic view of the furniture hinge with the hinge arm in an open position,

[0027] Fig. 3 is an even more schematic view of the furniture hinge with the hinge arm in the closed position,

[0028] Fig. 4 is an even more schematic view of the furniture hinge with the hinge arm in the open position,

[0029] Fig. 5 is a schematic view of a damper and a damper support,

[0030] Fig. 6 shows exemplary values which may represent a measure of a second moment arm plotted over an opening angle of the hinge arm, and

[0031] Fig. 7 shows exemplary values which may represent a measure of a first moment arm plotted over the opening angle.

[0032] Figure 1 shows a schematic view of a furniture hinge 1 according to a preferred embodiment. Generally, the furniture hinge 1 comprises a fastening section 100 for fastening to a piece of furniture and a hinge arm 15 for fastening to a movable furniture part. The piece of furniture may, for instance, be a closet, a cabinet or the like. The movable furniture part may, for instance, be a door, a flap or the like. Neither the piece of furniture nor the movable furniture part are shown in the drawings.

[0033] The furniture hinge 1 may be adapted to enable fastening the movable furniture part to the piece of furniture such that it can be moved, in particular pivoted or displaced, preferably moved in a combined translational and rotational manner, between an opened state and a closed state. The opened state of the movable furniture part may correspond to a state in which access to an interior of the piece of furniture is enabled, and the closed state may correspond to a state where access to the interior is blocked by the movable furniture part. As can be gathered from Figure 1 , the furniture hinge 1 may in particular be a flap fitting.

[0034] The configuration shown in Figure 1 may correspond to the closed state of the movable furniture piece. The closed state of the movable furniture piece may correspond to a closed position of the hinge arm 15. The configuration shown in Figure 2 may correspond to the opened state of the movable furniture piece. The opened state of the movable furniture piece may correspond to an open position of the hinge arm 15. An opening motion may refer to a movement of the hinge arm 15 from the closed to the open position. A closing motion may refer to a movement of the hinge arm 15 from the open to the closed position. Closing motion and / or opening motion may be referred to as the operation of the furniture hinge 1. In particular, the furniture hinge 1 may comprise a multi-axle articulation 110 which connects the hinge arm 15 to the fastening section 100 and enables the opening and the closing motion.

[0035] Figures 3 and 4 show more schematic views of the furniture hinge 1 in the states depicted in Figures 1 and 2, respectively. Note that these more schematic drawings do not include all of the features of the furniture hinge 1 shown in Figures 1 and 2. For instance, the fastening section 100 is not shown in Figures 3 and 4. From Figure 4 it is evident that an opening angle y may be defined. The opening angle y may reflect an angular position of the hinge arm 15 between the closed and the open position. For instance, the opening angle y may be defined to, in the closed position as shown in Figures 1 and 3, have a value of zero. In the open position as shown in Figures 2 and 4, the opening angle y may have a non-zero value. For instance, the opening angle y may be at least 90°, preferably at least 100°, more preferably at least 110° in the open position.

[0036] Generally, the opening angle y may be defined between a longitudinal axis of the hinge arm 15 in the closed position and a longitudinal axis of the hinge arm 15 in the open position. As can be seen in the drawings, the hinge arm 15 may be coupled to the multi-axle articulation 110 by means of two joints 11 , 12. Hence, alternatively or similarly, the opening angle y may be defined between a straight line connecting pivot axes of the joints 11 , 12 connected to the hinge arm 15 in the closed and a straight line connecting pivot axes of the joints 11 , 12 connected to the hinge arm 15 in the open state.

[0037] Referring to Figures 1 and 2, the fastening section 100 may comprise a plate shaped member and / or may itself generally be plate shaped. The furniture hinge 1 may comprise a housing (not shown) in which at least a part of the components of the furniture hinge 1 are at least partially received. For instance, the fastening section 100 may be received at least partially in the housing. It is further conceivable that the fastening section 100 may form a part of the housing of the furniture hinge 1. In this sense, the illustrations in Figures 1 and 2 may represent an assembly state wherein parts of the housing and / or the entire housing may be removed and / or opened.

[0038] As indicated above, the furniture hinge 1 may comprise a multi-axle articulation 110 which connects the hinge arm 15 to the fastening section 100 and enables the opening and the closing motion. To this end, according to the preferred embodiment shown in the drawings, the multi-axle articulation 110 may comprise an articulation lever assembly 111. The articulation lever assembly 111 may form at least part of a linkage which guides the opening and the closing motion of the hinge arm 15. The articulation lever assembly 111 may comprise multiple joints 6, 7, 8, 9, 10, 11 , 12 and articulation levers 2, 3, 4, 5 which form parts of the linkage. As already indicated above, the hinge arm 15 may be coupled to the articulation lever assembly 111 , in particular by means of at least one, preferably two joints 11 , 12. In this sense, the hinge arm 15 may be considered to form a part, in particular a lever, of the linkage. In particular, the hinge arm 15 may be considered to be a part of the articulation lever assembly 111 , more particularly be considered an articulation lever. In this context, the fastening section (100) or partial regions of the fastening section (100) may be considered a ground link or ground links of the linkage guiding the opening and the closing motion of the hinge arm 15.

[0039] As is evident from the drawings, each of the articulation levers 2, 3, 4, 5 may be pivotably coupled to at least one other of the articulation levers 2, 3, 4, 5 by means of at least one joint 2, 3, 4, 5. It is further preferable that, as in the embodiment shown, at least one joint, more preferably two joints 6, 7 pivotably connects a respective one of the articulation levers 2, 3 to the fastening section 100.

[0040] More specifically, as can be gathered from the drawings, the articulation lever assembly 111 may comprise a first articulation lever 2, a second articulation lever 3, a third articulation lever 4 and a fourth articulation lever 5.

[0041] The first articulation lever 2 may be coupled to the fastening section 100 by means of a first joint 6. In this sense, the first articulation lever 2 may be rotatable about a pivot axis of the first joint 6, wherein preferably the first joint 6 is stationary relative to the fastening section 100. That is, besides rotatability about a pivot axis of a joint that is stationary relative to the fastening section 100, the first articulation lever 2 may be stationary relative to the fastening section 100 during operation of the furniture hinge 1 .

[0042] Similarly, the second articulation lever 3 may be coupled to the fastening section 100 by means of a second joint 7. Consequently, the second articulation lever 3 may be rotatable about a pivot axis of the second joint 7, wherein preferably the second joint 7 is stationary relative to the fastening section 100. Again, besides rotatability about a pivot axis of a joint that is stationary relative to the fastening section 100, the second articulation lever 3 may be stationary relative to the fastening section 100 during operation of the furniture hinge 1 .

[0043] A lever which can be pivoted but otherwise is not displaced with respect to the fastening section during operation of the furniture hinge 1 may be referred to as an anchored lever. In other words, an anchored lever may be intended for pure rotation about one pivot axis which is stationary relative to the fastening section 100. The first articulation lever 2 and the second articulation lever 3 of the embodiment shown may thus be identified as anchored levers.

[0044] Contrastingly, a lever which is displaceable relative to the fastening section 100 in its entirety, i.e., that is not intended for pure rotation about a pivot axis that is stationary relative to the fastening section 100, may be referred to as a floating lever.

[0045] In the embodiment shown in the drawings, the third articulation lever 4 and the fourth articulation lever 5 are floating levers. As can be seen in the Figures, the third articulation lever 4 may be pivotably coupled to the first articulation lever 2 by means of a third joint 8. The pivot axis of the third joint 8 may be spaced apart from the pivot axis of the first joint 6 along a first lever axis 2.11 of the first articulation lever 2. A lever axis may be defined as a straight and direct line connecting two pivot axes of joints associated with the lever being considered. Consequently, a first lever axis 2.11 of the first articulation lever 2 may be a straight and direct line connecting the pivot axes of the first joint 6 and the third joint 8.

[0046] The third articulation lever 4 may further be pivotably coupled to the second articulation lever 3 by means of a fourth joint 9. The pivot axis of the fourth joint 9 may be spaced apart from the pivot axis of the second joint 7 along a lever axis of the second articulation lever 3.

[0047] As can be seen in Figures 1 and 2, the third articulation lever 4 may comprise a first portion 4.1 and a second portion 4.2. The first portion 4.1 and the second portion 4.2 may be rigidly connected to one another, in particular the third articulation lever 4 may be designed as an integral part comprising the first portion 4.1 and the second portion 4.2. The third joint 8 may be associated with the second portion 4.2. Preferably, the fourth joint 9 may be associated with a transitional region between the first portion 4.1 and the second portion 4.2. A straight line directly connecting pivot axes of the third joint 8 and the fourth joint 9 may thus be referred to as a second portion lever axis 4.21 of the third articulation lever 4.

[0048] The third articulation lever 4 may further be coupled to the hinge arm 15 by means of a sixth joint 11 . The sixth joint 11 may be associated with the first portion 4.1 of the third articulation lever 4. A straight line directly connecting pivot axes of the fourth joint 9 and the sixth joint 11 may be referred to as a first portion lever axis 4.11 of the third articulation lever 4.

[0049] As in the preferred embodiment shown in the drawings, the first portion 4.1 and the second portion 4.2 of the third articulation lever 4 are preferably arranged at an angle to one another. A straight line directly connecting pivot axes of the third joint 8 and the fourth joint 9 may thus be referred to as a second portion lever axis 4.21 of the third articulation lever 4. A straight line directly connecting pivot axes of the fourth joint 9 and the sixth joint 11 may be referred to as a first portion lever axis 4.11 of the second articulation lever 3. In particular, the first portion lever axis 4.11 and the second portion lever axis 4.21 of the third articulation lever 4 may be arranged at an angle to one another.

[0050] The fourth articulation lever 5 may be pivotably coupled to the second articulation lever 3 by means of a fifth joint 10 which is preferably spaced apart from the fourth joint 9. The fourth articulation lever 5 may further be pivotably coupled to the hinge arm 15 by means of a seventh joint 12. Preferably, the seventh joint 12 is spaced apart from the sixth joint 11 .

[0051] Similarly to the third articulation lever 4, the second articulation lever 3 may comprise a first portion 3.1 and a second portion 3.2. The fifth joint 10 may be associated with the second portion 3.2 of the second articulation lever 3, whereas the fourth joint 9 may be associated with a transitional region between the first portion 3.1 and the second portion 3.2 of the second articulation lever 3. The second joint 7 may be associated with the first portion 4.1 of the second articulation lever 3. The first portion 3.1 and the second portion 3.2 may be rigidly connected to one another, in particular the second articulation lever 3 may be designed as an integral part comprising the first portion 3.1 and the second portion 3.2. A straight line directly connecting pivot axes of the fourth joint 9 and the fifth joint 10 may thus be referred to as a second portion lever axis 3.21 of the second articulation lever 3. A straight line directly connecting pivot axes of the second joint 7 and the fourth joint 9 may be referred to as a first portion lever axis 3.11 of the second articulation lever 3.

[0052] Besides the articulation lever assembly 111 , the multi-axle articulation 110 may further comprise a transmission lever assembly 112. The transmission lever assembly 112 may form a linkage that transmits a driving force DF of an energy storage 45 to the articulation lever assembly 111. The energy storage 45 and the driving force DF will be explained in more detail further below. The transmission lever assembly 112 may comprise multiple joints 26, 27, 28, 29, 30, 31 and multiple transmission levers 22, 23, 24, 25 which form parts of the linkage. In this context, the fastening section 100 or partial regions of the fastening section 100 may be considered a ground link or ground links of the linkage transmitting the driving force DF to the articulation lever assembly 111.

[0053] Preferably, and as shown in the drawings, at least one transmission lever is pivotably coupled to at least one articulation lever by means of a joint. More specifically, a first transmission lever 22 may be coupled to the first articulation lever 2 by means of an eighth joint 26. Therefore, the articulation lever assembly 111 may be coupled to the transmission lever assembly 112. In consequence, the linkage transmitting the driving force may be coupled the linkage guiding the opening and the closing motion. Hence, in a wider sense, the multi-axle articulation 110 may, in particular in conjunction with the fastening section 100 as a ground link, be considered a superordinate linkage comprising both the linkage transmitting the driving force as well as the linkage guiding the opening and the closing motion.

[0054] As is evident from the drawings, each of the transmission levers 22, 23, 24, 25 may be pivotably coupled to at least one other of the transmission levers 22, 23, 24, 25 by means of at least one joint 26, 27, 28, 29, 30, 31 . It is further preferable that, as in the embodiment shown, at least one joint, more preferably two joints 28, 31 pivotably connect(s) a respective one of the transmission levers 23, 25 to the fastening section 100.

[0055] More specifically, as can be gathered from the drawings, the transmission lever assembly 112 may comprise a first transmission lever 22, a second transmission lever 23, a third transmission lever 24 and a fourth transmission lever 25, which fourth transmission lever 25 may be referred to as actuating lever 25.

[0056] The first transmission lever 22 may be pivotably coupled to the first articulation lever 2 by means of an eighth joint 26. Preferably, the eighth joint 26 is provided spaced apart from the third joint 8. As can be seen in Figure 2, the eighth joint 26 may be associated with a second lever axis 2.21 of the first articulation lever 2. The second lever axis 2.21 of the first articulation lever 2 may be a straight and direct line connecting the pivot axes of the first joint 6 and the eighth joint 26. The first lever axis 2.11 and the second lever axis 2.21 may preferably be arranged at an angle to one another.

[0057] Spaced apart from the eighth joint 26, the first transmission lever 22 may be pivotably connected to a second transmission lever 23 by means of a ninth joint 27. As can be gathered from a comparison of the closed position as depicted in Figure 1 and the open position as depicted in Figure 2, the first transmission lever 22 may be a floating lever and may be referred to as first floating transmission lever 22.

[0058] The second transmission lever 23 may be pivotably connected to the fastening section 100 by means of a tenth joint 28. Preferably, the tenth joint 28 is stationary relative to the fastening section 100 at least during operation of the furniture hinge 1. The second transmission lever 23 may thus be pivotable about a pivot axis 28.1 of the tenth joint 28 but otherwise not be displaced relative to the fastening section 100. Hence, the second transmission lever 23 may be considered an anchored lever and may be referred to as first anchored transmission lever 23.

[0059] The ninth joint 27 may be spaced apart from the tenth joint 28. A straight and direct line connecting the pivot axis 28.1 of the tenth joint 28 with the pivot axis of the ninth joint 27 may be referred to as a second lever axis 23.21 of the second transmission lever 23.

[0060] The second transmission lever 23 may further be pivotably connected to the third transmission lever 24 by means of an eleventh joint 29. Preferably, the eleventh joint 29 is spaced apart both from the tenth joint 28 and the ninth joint 27. A straight and direct line connecting the pivot axis 28.1 of the tenth joint 28 and a pivot axis 29.1 of the eleventh joint

[0061] 29 may be referred to as a first lever axis 23.11 of the second transmission lever 23. As can be gathered from the drawings, the first lever axis 23.11 and the second lever axis 23.21 are preferably arranged at an angle to one another.

[0062] Spaced apart from the eleventh joint 29, the third transmission lever 24 may be pivotably coupled to the actuating lever 25 by means of a twelfth joint 30. A straight and direct line connecting a pivot axis 29.1 of the eleventh joint 29 and a pivot axis 30.1 of the twelfth joint

[0063] 30 may be referred to as a lever axis 24.1 of the third transmission lever 24. As can be gathered from a comparison of Figures 1 and 2, the third transmission lever 24 may be a floating lever. The third transmission lever 24 may thus be referred to as second floating transmission lever 24. The lever axis 24.1 of the third transmission lever 24 may be parallel, in particular collinear with a force transmitted FT at the eleventh joint 29 connecting the third transmission lever 24 and the second transmission lever 23. The force transmitted FT will be discussed in more detail further below.

[0064] The actuating lever 25 may further be pivotably coupled to the fastening section 100 directly or indirectly by means of a joint 31 , which may be referred to as actuating lever pivot 31 . The actuating lever pivot 31 may spaced apart from the twelfth joint 30. A straight and direct line connecting the twelfth joint 30 and the actuating lever pivot 31 may be referred to as a longitudinal axis 25.1 of the actuating lever 25.

[0065] The actuating lever pivot 31 may be positionally adjustable relative to the fastening section 100. Therefore, the actuating lever pivot 31 is hereinafter referred to as the adjustable joint 31. In particular, the adjustable joint 31 may form part of a closing force adjustment mechanism 60, which closing force adjustment mechanism 60 will be discussed in more detail further below. Generally, the adjustable joint 31 may be stationary at least during operation of the furniture hinge 1 , such that the actuating lever 25 may be rotatable about a stationary actuating lever pivot axis 31.1 but otherwise not be displaceable relative to the fastening section 100 during operation of the furniture hinge 1. As such, the actuating lever 25 may be an anchored lever and thus may be referred to as second anchored transmission lever 25.

[0066] As already indicated above, the furniture hinge 1 may comprise an energy storage 45. The energy storage 45 may provide for a driving force DF which supports at least a part of the opening and / or the closing motion. Preferably, and as in the embodiment shown, the driving force DF supports both opening and closing motion as will be explained further below.

[0067] Referring to Figures 1 and 2, the energy storage 45 may comprise a spring arrangement 46. In the embodiment shown in the drawings, the spring arrangement 46 comprises a first spring 47 and a second spring 48. Any other number of springs is conceivable. The spring(s) is / are preferably designed as (a) tension spring(s). As in the embodiment shown, the first spring 47 and the second spring 48 may be helical springs.

[0068] The energy storage 45 may further comprise a first spring retainer 49 and a second spring retainer 51 . The first spring 47 and the second spring 48 may be attached to each the first spring retainer 49 and the second spring retainer 51 at respective opposing spring ends by any suitable means. For example, they may be clamped or hooked to the respective spring retainer. In any case, it is preferable that, as in the embodiment of the drawings, the spring arrangement 46 is held between the first spring retainer 49 and the second spring retainer 51 such that a spring force of the spring arrangement 46 may act between the first spring retainer 49 and the second spring retainer 51 . The spring force may correspond to the driving force DF.

[0069] The first spring retainer 49 may be coupled to a spring support 41 of the energy storage 45 which may be provided stationary relative to the fastening section 100. In particular, as per the embodiment of the drawings, the spring support 41 may be fixed to the fastening section 100. The spring support 41 may thus serve to transmit spring forces to the fastening section 100, thereby directly or indirectly forming an anchor for the spring arrangement 46.

[0070] The second spring retainer 51 may be directly or indirectly coupled to the actuating lever 25. This way, the driving force DF may be transmitted from the energy storage 45 to the transmission lever assembly 112. In the preferred embodiment, the second spring retainer 51 is pivotably coupled to the actuating lever 25 at a coupling point 52 so as to allow for an angular alignment of the spring arrangement 46, in particular of longitudinal axes of the first spring 47 and the second spring 48 with the line of action LA of the driving force DF.

[0071] The coupling of the second spring retainer 51 to the actuating lever 25 may be achieved by means of a connecting piece 53 that is connected to, in particular held at, the actuating lever 25. The connecting piece 53 may be pivotably connected to the second spring retainer 51 at the coupling point 52.

[0072] A furniture hinge 1 according to the invention may further comprise a damping arrangement 80 which provides for a damping of the opening and / or the closing motion along at least part of the opening and / or the closing motion. Preferably, as in the embodiment shown in the drawings, the damping arrangement 80 provides for damping both the opening and the closing motion along part of the opening and the closing motion, respectively.

[0073] As evident from Figure 4, the damping arrangement 80 may comprise a damper 90. The damper 90 may preferably be a damper configured for damping a linear motion. As in the embodiment shown in the drawings, the damper 90 may be a fluid damper. In particular, the damper 90 may comprise a cylinder 92 and a piston 93, which piston 93 may be movably guided in the cylinder 92. The damper 90 may further comprise a first actuating piece 84. The first actuating piece 84 may be coupled to the cylinder 92. In particular, first actuating piece 84 may be fixedly attached to the cylinder 92. The first actuating piece 84 may be in the form of a rod. At an end facing away from the cylinder 92, the first actuating piece 84 may comprise a first counter surface 85.

[0074] Further to the first actuating piece 84, the damper 90 may also comprise a second actuating piece 82, which second actuating piece 82 may be coupled to the piston 93. In particular, the second actuating piece 82 may be formed by a piston rod or attached to a piston rod, in particular serve as an extension of the piston rod. At its end facing away from the piston 93, the second actuating piece 82 may comprise a second counter surface 83.

[0075] The damper 90 may be actuated in a first actuating direction AD1 and a second actuating direction AD2, which may be linear directions. Generally, the first actuating direction AD1 and the second actuating direction AD2 may be opposed to one another. Preferably, they are parallel and opposed.

[0076] The damper 90 may further comprise a spring 95 which may serve for providing a restoring force to the damper. In other words, the piston 93 may be displaced relative to the cylinder 92 by an actuation of the damper 90, and the spring 95 may serve to reset the piston 93 to its original position when actuating forces are no longer present.

[0077] The damper 90 may be held by means of a damper support 91. Preferably, as per Figure 4, the damper support 91 may comprise a housing 81 , in particular may be in the form of a housing 81 at least partially receiving the damper 90. The housing 81 may comprise an interior 81.3 wherein the damper 90 is at least partially received, preferably at least with its cylinder 92. The housing 81 may comprise a first opening 81.1 and a second opening 81.2, through which the first actuating piece 84 and the second actuating piece 82 may be guided out of the interior 81 .3, respectively.

[0078] From Figure 4, it can further be gathered that the cylinder 92 may be displaceable relative to the damper support 91 in the first actuating direction AD1 and the second actuating direction AD2. To this end, the damper support 91 may enable a limited displacement of the cylinder 92 relative to the first actuating direction AD1. As shown in the drawings, a displacement of the cylinder 92 relative to the damper support 91 in the first actuating direction AD1 may be limited by means of a first counter contact member 81.4. The first counter contact member 81.4 may be provided stationary relative to the damper support 91. Limitation of the displacement of the cylinder 92 may be achieved in that a first contact member 92.1 that is connected to the cylinder 92 abuts the first counter contact member 81 .4. Preferably the first contact member 92.1 is formed by an end face of the cylinder 92 facing in the first actuating direction AD1. The first counter contact member 81.4 may be formed by a surface of the damper support 91 , preferably by a surface area of the housing 81 in vicinity of the first opening 81.1.

[0079] Further, the damper support 91 may provide for delimiting a displacement of the second actuating piece 82 relative to the damper support 91 in the second actuating direction AD2. To this end, a second counter contact member 81.5 may be provided stationary with the damper support 91 against which a second contact member 96 connected to the second actuating piece 82 may abut. For instance, the second counter contact member 81 .5 may be formed by a surface adjacent to the second opening 81 .2 of the housing. The second contact member 96 may be formed as a collar at the second actuating piece 82.

[0080] Referring now to Figures 1 and 2, the damping arrangement 80 may be provided on the first transmission lever 22. For instance, the damper support 91 , in particular the housing 81 may be attached to the first transmission lever 22. On the first articulation lever 2, a first actuating counter element 13 may be provided. A second actuating counter element 33 may be provided on the second transmission lever 23. The first and second actuating counter elements 13 may provide for actuation of the damper 90 by engagement with the first and second actuating pieces 84, 83 as will be described in more detail below.

[0081] The furniture hinge 1 may comprise force adjustment means that allow for an adjustment of a degree of support of at least part of the opening and / or closing motion of the hinge arm 15. Preferably, as in the embodiment shown, both the opening and the closing motion are supported by the driving force DF and both the amount of support for the closing and the opening motion are adjustable by means of the force adjustment means.

[0082] The force adjustment means of the present invention may comprise a first force adjustment mechanism 40 and a second force adjustment mechanism 55. The first force adjustment mechanism 40 may provide for the adjustability of a magnitude of the driving force DF.

[0083] To this end, the first force adjustment mechanism 40 may provide for an adjustability of a relative position of the first spring retainer 49 to the second spring retainer 51 , preferably of a distance therebetween. To be clear, the relative position of the first spring retainer 49 to the second spring retainer 51 may change depending on the state of the furniture hinge 1 , i.e., if the hinge arm 15 is in the open position, the closed position, or in between. Thus, the relative position may change depending on the opening angle y. However, by means of the first force adjustment mechanism 40 a different relative position can be changed for at least one of the open position, the closed position and a position in between.

[0084] As in the embodiment of the drawings, the first force adjustment mechanism 40 may be realized in that the first spring retainer 49 is coupled to the spring support 41 by means of an adjustment element 43. Preferably, the adjustment element 43 is a threaded bolt. The adjustment element 43 may be partially received in a threaded bore 50 of the first spring retainer 49. Further, it may be guided through a through hole 42 provided on the spring support 41 . In particular, an actuation element 44, which may preferably be a head of the adjustment element 43, in particular of the threaded bolt, may rest on a surface of the spring support 41 facing away from the first spring retainer 49.

[0085] Preferably, a surface of the actuation element 44 facing the spring support 41 may comprise a convex, in particular a spherical shape, and a corresponding surface portion of the spring support 41 which the actuation element 44 rests on may comprise an at least partially corresponding shape. This way, the adjustment element 43 may be tiltable relative to the spring support 41 to a degree such that the spring support 41 and / or the spring arrangement 46 can align with respect to the line of action LA of the driving force DF.

[0086] The actuation element 44 of the adjustment element 43 may be designed to be actuated by a user so as to rotate the adjustment element 43 about its longitudinal axis. Therefore, by rotation of the adjustment element 43 about its longitudinal axis, and by engagement of the adjustment element 43 with the threaded bore 50 of the first spring retainer 49, the first spring retainer 49 can be urged towards and / or away from the spring support 41 . Thereby, the distance between the first spring retainer 49 and the second spring retainer 51 may be adjusted. Consequently, a prestress of the spring arrangement 46 can be altered which provides for an adjustment of the magnitude of the driving force DF that can be provided by the energy storage 45.

[0087] As indicated above, the force adjustment means may comprise a second force adjustment mechanism 55. The second force adjustment mechanism 55 may provide for adjustability of a first moment arm MA1 of the driving force DF with respect to the actuating lever pivot axis 31.1 about which the actuating lever 25 is rotatable.

[0088] To this end, the connecting piece 53 may provide for adjustability of the position of the coupling point 52 relative to the actuating lever pivot axis 31.1. In particular, as indicated above, the coupling point 52 may be provided on the connecting piece 53. The coupling point 52 may be the point of transmission of the driving force DF from the energy storage 45 to the transmission lever assembly 112.

[0089] Further, the connecting piece 53 may be displaceable along the longitudinal axis 25.1 of the actuating lever 25. As best visible in Figures 1 and 2, a fixing element 54 may be provided which may serve to releasably secure the connecting piece 53 in various positions along the lever axis 25.1 of the actuating lever 25. For instance, the fixing element 54 may be a bolt that serves to clamp the connecting piece 53 against the connecting piece 53.

[0090] The connecting piece 53 may be essentially plate shaped. As seen in Figures 1 and 2, the connecting piece 53 may rest with an essentially planar surface on an essentially planar actuating lever surface of the actuating lever 25, which actuating lever surface may be normal to the actuating lever pivot axis 31 .1 . For secure guidance of the connecting piece 53 along the actuating lever 25, a guide element 53.1 may be provided on the connecting piece 53. As depicted in the drawings, the guide element 53.1 may be provided on said surface of the connecting piece 53 resting on the actuating lever surface. In particular, the guide element 53.1 may be formed as a protrusion, preferably a shoulder, extending to some length along the lever axis 25.1 of the actuating lever 25. At least one or two shoulders may be provided which rest against and / or are slidable along one side surface or opposed side surfaces of the actuating lever 25 that extend transverse to the actuating lever surface and preferably parallel to the actuating lever pivot axis 31.1 and / or the lever axis 25.1 of the actuating lever 25.

[0091] The furniture hinge 1 according to the invention may further comprise a closing force adjustment mechanism 60 which allows for an adjustment of a degree of support of the closing motion relative to a degree of support of the opening motion provided by the energy storage 45. This may be achieved by means of a positional adjustment of the adjustable joint 31 of the transmission lever assembly 112 relative to the fastening section 100. The effects of such a positional adjustment will be explained in detail later.

[0092] As seen in Figures 1 and 2, the adjustable joint 31 may be provided on a connecting part 62. The connecting part 62 may be an essentially plate shaped member. The connecting part 62 may be held at a support member 61 , which support member 61 may be connected to the fastening section 100 in a stationary manner. The connecting part 62 may be displaceable relative to the support member 61 , wherein preferably the direction of displacement has at least a predominant component parallel to the line of action LA of the driving force DF. Preferably it is provided that the connecting part 62 can be fixed in various positions of displacement.

[0093] To this end, according to the embodiment of the Figures, an adjustment device 63 may be provided. The connecting part 62 may, with an end region facing away from the adjustable joint 31 , be received in a receiving space of the support member 61. The support member may comprise a slot 64 which provides access to the receiving space. A fixing element 65 may be guided through the slot 64 to the support member 61. For instance, the fixing element 65 may be a bolt that engages with a threaded bore in the support member 61. Therefore, the support member 61 may be displaced relative to the support member 61 , wherein the fixing element 65 follows the displacement and moves along the slot 64. When the desired displacement is achieved, the support member 61 may be fixed in position by tightening the fixing element 65.

[0094] In the following, the operation of the furniture hinge 1 according to the embodiment shown in the figures is further explained. In particular, the general operation of the furniture hinge 1 in the context of the opening and closing motion, the function of the damping arrangement 80, the function of the first force adjustment mechanism 40, the function of the second force adjustment mechanism 55 and the function of the closing force adjustment mechanism 60 will be discussed.

[0095] Regarding the opening and closing motions, reference is made to Figures 1 and 2 which show the closed and the open position of the hinge arm 15, respectively.

[0096] As indicated above, the articulation lever assembly 111 provides for articulation of the hinge arm 15 relative to the fastening section 100 during operation, i.e. during the opening and the closing motion. During an opening motion starting from the closed position as shown in Figure 1 , the first articulation lever 2 is pivoted about the pivot axis of the first joint 6. Similarly, the second articulation lever 3 is pivoted about the pivot axis of the second joint 7. Further, the third articulation lever 4, being pivotably connected to the first articulation lever 2 at the third joint 8 and to the second articulation lever 3 at the fourth joint 9, is both displaced relative to the fastening section 100 and pivoted relative to the first articulation lever 2 and the second articulation lever 3. Similarly, the fourth articulation lever 5, being pivotably connected to the second articulation lever 3 at the fifth joint 10, is both displaced relative to the fastening section 100 and pivoted relative to the second articulation lever 3. The hinge arm 15, being pivotably connected to the third articulation lever 4 at the sixth joint 11 and to the fourth articulation lever 5 at the seventh joint 12, is both displaced relative to the fastening section 100 as well as rotated. In particular, during the opening motion, the opening angle y of the hinge arm 15 is changed. At the end of the opening motion, the open position as shown in Figure 2 may be reached.

[0097] Applied to the view of Figure 1 , pivoting of the first articulation lever 2 and the second articulation lever 3 may take place in a counterclockwise direction. Similarly, pivoting of the third articulation lever 4 relative to the first articulation lever 2 and the second articulation lever 3 as well as of the fourth articulation lever 5 relative to the second articulation lever 3 may take place in a counterclockwise direction.

[0098] From the open position, the closing motion may correspond to a reversed opening motion and may end when the closed position of the hinge arm 15 is achieved again.

[0099] The closing motion may be stopped once the closed position has been reached by the engagement of the first transmission lever 22 with a stop 32 provided on the fastening section 100, as seen in Figure 1. Furthermore, the opening motion may be stopped once the open position has been reached by engagement of the second transmission lever 23 with the stop 32, as seen in Figure 2. Of course, it is conceivable to provide for other means to delimit the opening and / or closing motions. For instance, more than one stop may be provided. As another example, the linkages formed by the articulation lever assembly 111 and / or the transmission lever assembly 112 may be designed such that they achieve a state of selflocking once the open and / or the closed position has / have been reached.

[0100] As indicated above, the energy storage 45 may provide for a driving force DF supporting at least part of the opening and closing motion. In the embodiment of the drawings, both the opening and the closing motion are supported by the driving force DF of the energy storage 45 during a part of the respective motion. As can gathered form Figures 1 and 2, the spring arrangement 46 provides for a tensile force that biases the first spring retainer 49 and the second spring retainer 51 towards one another. Therefore, as the first spring retainer 49 is connected to the spring support 41 , which spring support 41 is secured to the fastening section 100, the tensile force acts to bias the second spring retainer 51 toward the right in Figures 1 and 2. The tensile force provided by the spring arrangement 46 may correspond to the driving force DF. Due to the second spring retainer 51 being connected to the connecting piece 53 at the coupling point 52 and the connecting piece 53 being connected to the actuating lever 25, the driving force DF is transmitted from the energy storage 45 to the actuating lever 25. In Figures 1 and 2, the driving force DF urges the actuating lever 25 to pivot about the actuating lever pivot axis 31.1 in a clockwise direction. This urging is due to a moment of the driving force DF relative to the actuating lever pivot axis 31.1 which results from the first moment arm MA1 of the driving force DF relative to the actuating lever pivot axis 31.1.

[0101] The moment exerted on the actuating lever 25 by the driving force DF is transmitted as a force to the third transmission lever 24 at the twelfth joint 30. This transmitted force is further transmitted from the third transmission lever 24 to the second transmission lever 23 at the eleventh joint 29. Thereby, the second transmission lever 23 is urged to pivot about the pivot axis 28.1 of the tenth joint 28, in the view of Figures 1 and 2 to pivot in the counterclockwise direction. From the second transmission lever 23, the force is further transmitted to the first transmission lever 22 at the ninth joint 27. Finally, the force is transmitted from the first transmission lever 22 to the first articulation lever 2 at the eighth joint 26.

[0102] In the closed position as shown in Figure 1 , a line of action the force transmitted at the eighth joint 26, which may be substantially collinear with the lever axis 22.1 of the first transmission lever 22, is arranged such that it urges the first articulation lever 2 to pivot about the first joint 6 in a closing direction, i.e., in Figure 1 in a clockwise direction. Consequently, in the closed position of the hinge arm 15, the driving force DF provides for a closing force on the articulation lever assembly 111.

[0103] In the open position as shown in Figure 2, however, the line of action the force transmitted at the eighth joint 26 is arranged such that it urges the first articulation lever 2 to pivot about the first joint 6 in an opening direction, i.e., in Figure 1 in a counterclockwise direction. Consequently, in the open position of the hinge arm 15, the driving force DF provides for an opening force on the articulation lever assembly 111.

[0104] Consequently, during the opening and the closing motion, there exists a force reversal point in which a switch occurs between the support of the opening and the support of the closing motion. The force reversal point may correspond to an opening angle y in which the line of action the force transmitted at the eighth joint 26 intersects the pivot axis 6.1 of the first joint 6. Preferably, the opening angle y at the force reversal point may correspond to a range between 10° and 30°, more preferably, and as in the present embodiment, between 15° and 25°.

[0105] As a consequence of the above-described support of the opening and closing motion, the user needs to, in order to move the hinge arm 15 from the closed position, overcome the closing force exerted by the driving force DF until the force reversal point is reached. After the force reversal point, the further opening motion is supported by the driving force DF, preferably such that the further opening motion is performed without further actuation by the user. Similarly, in order to move the hinge arm 15 from the open position, the user needs to overcome the support of the opening motion until the force reversal point is reached. After the force reversal point, the further closing motion is supported by the driving force DF, preferably such that the further closing motion is performed without further actuation by the user.

[0106] As previously described, support of the closing and the opening motion may be provided by the energy storage 45. Further, the opening and the closing motion may be delimited by suitable means, for instance the interaction of the second transmission lever 23 and the first transmission lever 22 with a stop 32 provided on the fastening section 100. To provide for a smooth operation and to avoid a violent abutment at the stop, or a violent abutment of the movable furniture part at the piece of furniture at the end of the opening and / or the closing motion, the damping arrangement 80 may provide for damping of the opening and / or the closing motion during at least a part of the opening and / or the closing motion. In the embodiment shown in the drawings the damping arrangement 80 is provided to damp both the opening and the closing motion during a last part of the opening and the closing motion, respectively.

[0107] Referring first to the opening motion, corresponding to a transition from the closed state as shown in Figure 1 to the open state as shown in Figure 2, the last part of the opening motion is damped by means of the second actuating counter element 33 provided on the second transmission lever 23 engaging with the second actuating piece 82 of the damper 90. That is, by pivoting of the second transmission lever 23 about the pivot axis 28.1 of the tenth joint 28 in the opening direction, and by pivoting the first transmission lever 22 relative to the second transmission lever 23 at the ninth joint 27, the second actuating counter element 33 and the second actuating piece 82 are moved toward each other. A stop surface 34 provided on the second actuating counter element 33 comes into contact withthe second counter surface 83 of the second actuating piece 82. During further opening, the second actuating counter element 33 thus actuates the second actuating piece 82 such that the damper 90 is actuated in a direction referred to as the first actuating direction AD1 .

[0108] Referring now to Figure 5, the state in which the damping arrangement 80 is shown may correspond to an unactuated state, which state may exist in a range of motion between the closed and the open state. In this unactuated state, none of the actuating pieces 82, 84 are actuated. The cylinder 92 may rest with its first contact member 92.1 against the first counter contact member 81.4 provided on the housing 81. The second actuating piece 82 may rest with its second contact member 96 against the second counter contact member 81.5 of the housing 81 . The second actuating piece 82 and the cylinder 92 may be held in this resting position by means of the spring 95 that provides for a restoring force of the damper 90.

[0109] As explained above, when the open position is approached, the second actuating counter element 33 may actuate the second actuating piece 82 in the first actuating direction AD1 . As a consequence, the piston 93 is moved within the cylinder 92 against the resistance of a fluid provided in the piston 93. Therefore, the opening motion is damped.

[0110] Now referring to the closing motion, corresponding to a transition from the open state as shown in Figure 2 to the closed state as shown in Figure 2, the last part of the closing motion is damped by means of the first actuating counter element 13 provided on the first articulation lever 2 engaging with the first actuating piece 84 of the damper 90. That is, by pivoting of the first articulation lever 2 about the pivot axis 6.1 of the first joint 6 in the opening direction, and by pivoting the first transmission lever 22 relative to the first articulation lever 2 at the eighth joint 26, the first actuating counter element 13 and the first actuating piece 84 are moved toward each other. A stop surface 14 provided on the first actuating counter element 13 comes into contact with a first counter surface 85 of the first actuating piece 84. During further closing, the first actuating counter element 13 thus actuates the first actuating piece 84 such that the damper 90 is actuated in a direction referred to as the second actuating direction AD2.

[0111] As evident from Figure 5, by actuation of the first actuating piece 84 in the second actuating direction AD2, cylinder 92 will move together with the first actuating piece 84 in the second actuating direction AD2. Because the second actuating piece 82 connected to the piston 93 rests on the second counter contact member 81.5 with its second contact member 96, displacement of the piston 93 relative to the damper support 91 in the second actuating direction AD2 is prevented. Therefore, the actuation of the first actuating piece 84 in the second actuating direction AD2 leads to a relative movement of the cylinder 92 and the piston 93, thereby providing fluid damping of the closing motion.

[0112] As indicated above, a first force adjustment mechanism 40 may be provided to enable the adjustability of a magnitude of the driving force DF. Preferably, the adjustment of the magnitude of the driving force DF by means of the first force adjustment mechanism 40 may be performed when the hinge arm 15 is in the open state. As best visible in Figure 2, the actuation element 44 of the adjustment element 43 may be easily accessible from a front side of the piece of furniture. To adjust the magnitude of the driving force DF the user may act on the actuation element 44 in order to rotate the adjustment element 43 to achieve a displacement of the first spring retainer 49 relative to the second spring retainer 51 as described previously. Thereby, a prestress of the spring arrangement 46 may be adjusted.

[0113] Such an adjustment may be easy to perform after fitting of the furniture hinge 1 to the piece of furniture and even for readjustment after a period of use. By use of an adjustment element 43 in the form of a threaded bolt engaging in a threaded bore 50 of the first spring retainer 49, a continuous, i.e., stepless adjustment of the magnitude of the driving force DF may be achieved.

[0114] As further indicated above, a second force adjustment mechanism 55 may be provided for adjustability of the first moment arm MA1 of the driving force DF with respect to the actuating lever pivot axis 31.1 about which the actuating lever 25 is rotatable. While such an adjustment may be performed after fitting of the furniture hinge 1 to the piece of furniture, it may be preferable that the second force adjustment mechanism 55 provides for a factory adjustment. For instance, the second force adjustment mechanism 55 may comprise a number of settings that may accommodate for different sizes, weights and / or intended uses of furniture parts to be connected therewith. The number of settings may correspond to latching positions of the connecting piece 53 in different positions along the lever axis 25.1. For example, there may be provided a setting for heavy flaps, for intermediate weight flaps and for light flaps. By enabling a factory adjustment for these intended uses, the same parts of the furniture hinge 1 may be used for furniture hinge 1 intended for different applications.

[0115] To adjust the first moment arm MA1 of the driving force DF with respect to the actuating lever pivot axis 31.1 , the fixing element 54 may be loosened such that the connecting piece 53 may be adjusted to the desired position. After adjustment, the fixing element 54 may be fixed again to secure the connecting piece 53 against the actuating lever 25.

[0116] As indicated above, the furniture hinge 1 according to the invention may further comprise a closing force adjustment mechanism 60 which allows for an adjustment of a degree of support of the closing motion relative to a degree of support of the opening motion provided by the energy storage 45. This may be achieved by means of a positional adjustment of the adjustable joint 31 of the transmission lever assembly 112 relative to the fastening section 100.

[0117] For a better understanding of the closing force adjustment mechanism 60, it should first be noted that the force transmitted FT between the third transmission lever 24 and the second transmission lever 23 exerts a moment on the second transmission lever 23, which moment depends, besides on the magnitude of the force transmitted FT, on a second moment arm MA2, which second moment arm MA2 is the moment arm of the force transmitted FT with respect to the pivot axis 28.1 of the tenth joint 28 around which the second transmission lever 23 is pivotable. Consequently, the magnitude of the force that is transmitted between the second transmission lever 23 and the first transmission lever 22 and finally transmitted to the articulation lever assembly 111 also depends on the second moment arm MA2.

[0118] It may be easily understood that, when a longer second moment arm MA2 is provided, the force transmitted FT may introduce a larger moment and thus ultimately lead to a stronger support of the opening and / or the closing motion. The opposite is true for a shorter second moment arm MA2. From Figure 3, it may further be understood that the second moment arm MA2 depends on the value of a connecting angle 5 between the third transmission lever 24 and the second transmission lever 23, which connecting angle 5 may be defined as an angle between the lever axis 24.1 of the third transmission lever 24 and the first lever axis 23.11 of the second transmission lever 23. It should be noted that connecting angle 5 could also be defined using a different lever axis of the second transmission lever 23, for instance the second lever axis 23.21 , but in the following, the previously mentioned definition will be used.

[0119] The inventors have found that, by modification of a functional relationship between the connecting angle 5 and the opening angle y, the degree of support of the closing motion relative to a degree of support of the opening motion provided by the energy storage 45 may be modified.

[0120] The functional relationship between the connecting angle 5 and the opening angle y may be modified, for example, by displacing the adjustable joint 31 by means of the adjustment device 63 as explained above. For instance, it is assumed that, starting from the configuration shown in Figure 3, the adjustable joint 31 is adjusted to a direction largely parallel to the driving force DF, for example horizontally to the right in Figure 3. By this, the connecting angle 5 may be increased, which increase may persist for all values of the opening angle y. Consequently, the functional relationship may be altered, for instance by a constant or nearly constant term.

[0121] It should further be repeated that the second moment arm MA2 is also a function of the connecting angle 5, as mentioned previously. Generally, the second moment arm MA2 may be a trigonometric function, or at least comprise a trigonometric function of the connecting angle 5. In particular the second moment arm MA2 may be proportional to cos(180°-5).

[0122] Therefore, the second moment arm MA2 may also be a trigonometric function, or at least comprise a trigonometric function of the opening angle y.

[0123] Based on these findings, the inventors have identified that, trigonometric functions being functions of variable gradient, by changing the functional relationship between the connecting angle 5 and the opening angle y, maximum values of the second moment arm MA2 that arise during the support of the closing and the support of the opening motion can be adjusted such that a ratio between them can be adapted to the needs of the intended application.

[0124] In other words, the ratio of a maximum second moment arm MA2 during the support of the closing motion to a maximum second moment arm MA2 during support of the opening motion may be modified. This modification is illustrated in Figure 6. Figure 6 shows exemplary values of cos(180°-5), which may represent a measure of the second moment arm MA2 plotted over the opening angle y. The solid line represents a configuration in which the maximum second moment arm MA2 during support of the closing motion is relatively large. This configuration may correspond, in an embodiment according to the drawings to a connecting angle 5 of approximately 155° in the closed position. The dashed line represents a configuration with a relatively lesser second moment arm MA2 during support of the closing motion. This configuration may correspond to a connecting angle 5 of approximately 160° in the closed position. From this Figure it is clear that a relatively little adjustment of a starting connecting angle 5 (in the closed position) can provide for a significant change in the maximum second moment arm MA2 occurring during support of the closing motion. It is further evident from the Figure that reduction of the maximum second moment arm MA2 occurring during support of the closing motion may not reduce the maximum second moment arm MA2 occurring during support of the opening motion.

[0125] Note that in Figure 6 the force reversal point may correspond to an opening angle y of approximately 20°. Consequently, support of the closing motion may be present between an opening angle y of approximately 20° (force reversal) and the closed position (opening angle y = 0°). Support of the opening motion may thus be present between an opening angle y of approximately 20° (force reversal) and the open position which may correspond to an opening angle y of approximately 120° as seen in Figure 6.

[0126] It may be preferable that the value of opening angle y in which both curves have a minimum may correspond to the force reversal point, such that at the force reversal point the amount of force transmitted between the transmission lever assembly 112 and the multi-axle articulation 110 may be reduced in order for a smoother transition between the support of the opening and the support of the closing motion.

[0127] Additionally or alternatively, also the ratio of a maximum first moment arm MA1 occurring during support of the opening motion and a maximum first moment arm MA1 occurring during support of the closing motion may be achieved by the positional adjustment of the adjustable joint 31 . This also allows for an adjustment of the degree of support of the closing motion relative to the degree of support of the opening motion provided by the energy storage 45.

[0128] Considering the closed and open positions as shown in Figures 3 and 4, it is evident that a positional adjustment of the adjustable joint 31 may result in an adjustment of a working angle p. The working angle may be defined between the line of action LA of the driving force DF and the lever axis 25.1 of the actuating lever 25. The first moment arm MA1 may be a function of the working angle p. Consequently, the moment that can be introduced by the driving force DF into the actuating lever 25 is dependent on the working angle p.

[0129] Further, as can be gathered from a comparison of Figures 3 and 4, the working angle p may be a function of the opening angle y.

[0130] The inventors have found that, by modification of a functional relationship between the working angle and the opening angle y, the degree of support of the closing motion relative to a degree of support of the opening motion provided by the energy storage 45 may be modified.

[0131] The functional relationship between the working angle p and the opening angle y may be modified, for example, by displacing the adjustable joint 31 by means of the adjustment device 63 as explained above. For instance, it is assumed that, starting from the configuration shown in Figure 3, the adjustable joint 31 is adjusted to a direction largely parallel to the driving force DF, for example horizontally to the right in Figure 3. By this, the working angle p may be decreased, which decrease may persist for all values of the opening angle y. Consequently, the functional relationship may be altered, for instance by a constant or nearly constant term.

[0132] It should further be noted that the first moment arm MA1 is also a function of the working angle p. Generally, the first moment arm MA1 may be a trigonometric function, or at least comprise a trigonometric function of the working angle p. In particular the first moment arm MA1 may be proportional to sin(P).

[0133] Therefore, the first moment arm MA1 may also be a trigonometric function, or at least comprise a trigonometric function of the opening angle y.

[0134] Based on these findings, the inventors have identified that, by changing the functional relationship between the working angle p and the opening angle y, maximum values of the first moment arm MA1 that arise during support of the closing and the support of the opening motion can be adjusted such that a ratio between them can be adapted to the needs of the intended application.

[0135] In other words, the ratio of a maximum first moment arm MA1 during the support of the closing motion to a maximum first moment arm MA1 during the support of the opening motion may be modified. This modification is illustrated in Figure 7. Figure 7 shows exemplary values of sin(P), which may represent a measure of the first moment arm MA1 plotted over the opening angle y. The solid line represents a configuration in which the maximum first moment arm MA1 during support of the closing motion is relatively large. This configuration may correspond, in an embodiment according to the drawings, to a working angle p of approximately 69° in the closed position. The dashed line represents a configuration with a relatively lesser first moment arm MA1 during support of the closing motion. This configuration may correspond to a working angle p of approximately 59° in the closed position. From this Figure, it is clear that an adjustment of a starting working angle p (in the closed position) can provide for a significant change in the maximum first moment arm MA1 occurring during support of the closing motion. It is further evident from the Figure that reduction of the maximum first moment arm MA1 occurring during support of the closing motion may not reduce the maximum first moment arm MA1 occurring during support of the opening motion to the same degree but only to a lesser degree. Therefore, the adjustment of the working angle p may be particularly suited to reduce the support of the closing motion without substantially reducing the support of the opening motion.

[0136] Note that in Figure 7 the force reversal point may correspond to an opening angle y of approximately 20°. Consequently, support of the closing motion may be present between an opening angle y of approximately 20° (force reversal) and the closed position (opening angle Y = 0°). Support of the opening motion may thus be present between an opening angle y of approximately 20° (force reversal) and the open position which may correspond to an opening angle y of approximately 120° as seen in Figure 7.

Claims

Claims1 . A furniture hinge (1 ), in particular a flap fitting, comprising a fastening section (100) for fastening to a piece of furniture and a hinge arm (15) for fastening to a movable furniture part, in particular a flap, wherein a multi-axle articulation (110) is provided which connects the hinge arm (15) to the fastening section (100) and enables movement of the hinge arm (15) from a closed position to an open position in an opening motion and from the open position to the closed position in a closing motion, wherein an energy storage (45) is provided which provides for a driving force (DF) supporting at least part of the opening and the closing motion, wherein the multi-axle articulation (110) comprises an articulation lever assembly (111) forming at least part of a linkage which guides the opening and closing motion, and a transmission lever assembly (112) comprising multiple joints (26, 27, 28, 29, 30, 31) and multiple transmission levers (22, 23, 24, 25), which transmission lever assembly (112) forms at least part of a linkage transmitting the driving force (DF) from the energy storage (45) to the articulation lever assembly (111 ), characterized in that a closing force adjustment mechanism (60) is provided which allows for an adjustment of a degree of support of the closing motion relative to a degree of support of the opening motion provided by the energy storage (45) by means of a positional adjustment of an adjustable joint (31 ) of the transmission lever assembly (112) relative to the fastening section (100).

2. The furniture hinge (1 ) according to claim 1 , characterized in that the transmission lever assembly (112) comprises at least one, preferably two stationary joints (31 , 28) which remain(s) stationary relative to the fastening section (100) at least during the opening and the closing motion, wherein the adjustable joint (31) is such a stationary joint.

3. The furniture hinge (1 ) according to claim 1 or 2, characterized in that the energy storage (45) is, directly or indirectly, pivotably coupled to an actuating lever (25) of the transmission lever assembly (112), wherein a working angle (P) is defined between a line of action (LA) of the driving force (DF) and a lever axis (25.1) of the actuatinglever (25), which lever axis (25.1) is a straight line connecting two lever pivot axes (31.1 , 30.1) associated with the actuating lever (25), one of which lever pivot axes (31.1 , 30.1 ) preferably is the lever pivot axis (31.1 ) of the adjustable joint (31 ), and in that the positional adjustment results in an adjustment of the working angle (P).

4. The furniture hinge (1 ) according to claim 3, characterized in that the that the positional adjustment results in an adjustment of the working angle (P) at least one of- in the closed position,- in the open position,- during the opening motion,- during the closing motion,- at a force reversal point, in which a switch occurs between the support of the opening and the support of the closing motion.

5. The furniture hinge (1 ) according to claim 3 or 4, characterized in that the working angle (P) is a function of an opening angle (y) of the hinge arm (15), which opening angle (y) reflects an angular position of the hinge arm (15) between the closed and the open position, and in that the positional adjustment alters the functional relationship between the working angle (P) and the opening angle (y).

6. The furniture hinge (1 ) according to claim 5, characterized in that a first moment arm (MA1) of the driving force (DF) with respect to an actuating lever pivot axis (31.1 ) around which the actuating lever (25) is pivotable is a function of the working angle (P), preferably a function comprising a trigonometric function of the working angle (P), and in that by altering the functional relationship between the working angle (P) and the opening angle (y), a ratio of a maximum of the first moment arm (MA1 ) occurring during support of the closing motion to a maximum of the first moment arm (MA1 ) occurring during support the opening motion is modified.

7. The furniture hinge (1 ) according to claim 5 or 6, characterizedin that the working angle (P), as a function of the opening angle (y), exhibits an extremum during the opening and closing motion, which extremum corresponds to a force reversal point, in which a switch occurs between the support of the opening and the support of the closing motion, wherein the force reversal point preferably corresponds to an opening angle (y) between 10° and 30°, more preferably between 15° and 25°.

8. The furniture hinge (1 ) according to any of claims 1 to 7, characterized in that a connecting angle (5) is formed between lever axes (24.1 , 23.1 ) of two of the transmission levers (24, 23), which transmission levers (24, 23) are pivotably connected to one another at a joint (29), wherein the lever axes (24.1 , 23.1) are straight lines connecting two lever pivot axes (30.1 , 29.1 , 28.1) of joints (30, 29, 28) associated with the respective transmission lever (24, 23), and in that the positional adjustment results in an adjustment of the connecting angle (5).

9. The furniture hinge (1 ) according to claim 8, characterized in that the that the positional adjustment results in an adjustment of the connecting angle (5) at least one of in the closed position, in the open position, during the opening motion, during the closing motion, at a force reversal point, in which a switch occurs between the support of the opening and the support of the closing motion.

10. The furniture hinge (1 ) according to claim 8 or 9, characterized in that the connecting angle (5) is a function of the / an opening angle (y) of the hinge arm (15), which opening angle (y) reflects the angular position of the hinge arm (15) between the closed and the open position, and in that the positional adjustment alters the functional relationship between the connecting angle (5) and the opening angle (y).11 . The furniture hinge (1 ) according to claim 10, characterizedin that a second moment arm (MA2) of a force transmitted (FT) at the joint (29) connecting the two of the transmission levers (24, 23) relative to the pivot axis (28.1 ) of another joint (28) associated with one (23) of the two of the transmission levers (24, 23) is a function of the connecting angle (5), preferably a function comprising a trigonometric function of the connecting angle (5), and in that, by altering the functional relationship between the connecting angle (5) and the opening angle (y), a ratio of a maximum of the second moment arm (MA2) occurring during the closing motion to a maximum of the second moment arm (MA2) occurring during the opening motion can be modified.

12. The furniture hinge (1 ) according to claim 10 or 11 , characterized in that the connecting angle (5), as a function of the opening angle (y), exhibits an extremum during the opening and closing motion, which extremum corresponds to the / a force reversal point, in which a switch occurs between the support of the opening and the support of the closing motion, wherein the force reversal point preferably corresponds to an opening angle (y) between 10° and 30°, more preferably between 15° and 25°.

13. The furniture hinge (1 ) according to any of claims 1 to 12, characterized in that the position of the adjustable joint (31 ) relative to the fastening section (100) is adjustable in a linear direction, which preferably has at least a predominant component parallel to the / a line of action (LA) of the driving force (DF).

14. The furniture hinge (1 ) according to any of claims 1 to 13, characterized in that the adjustable joint (31) is provided on a connecting part (62), in that the connecting part (62) is displaceably held at a support member (61 ), and in that the support member (61) is provided stationary relative to the fastening section (100), wherein preferably the connecting part (62) can be fixed to the support member (61) in a plurality of positions by means of a fixing element (65).

15. The furniture hinge (1 ) according to claim 14, characterizedin that the support member (61) comprises a receiving space in which the connecting part (62) is partially received, in that the support member (61) comprises an elongated slot (64) providing for an access to the receiving space, and in that the / a fixing element (65) is guided through the slot (64) toward the connecting part (62).

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