Abstract:
The invention relates to an actuating mechanism for a swivel-mounted actuating arm, especially for driving a lid of an item of furniture. Said mechanism comprises a spring device including a biased actuating element and a translatory mechanism which translates the movement of the actuating element into a swiveling movement of the actuating arm. Said translatory mechanism comprises at least one adjusting device for varying the translation ratio between the movement of the actuating element and the swiveling movement of the actuating arm.

Description:
This application is a continuation of International Application of PCT/AT2005/000142, filed Apr. 27, 2005. 
    
    
     BACKGROUND OF THE INVENTION 
     The present invention relates to an actuating mechanism for a pivotably mounted actuating arm, in particular for driving a flap of a piece of furniture. The actuating mechanism includes a spring device having a spring-loaded setting member and a transmission mechanism which converts the movement of the setting member into a pivoting movement of the actuating arm. 
     Actuating mechanisms of this type are known in the art in many designs and serve chiefly to move flaps or lifting doors of furniture which are mounted on a horizontal pivoting axis, from the closed position into an open position or in the opposite direction, and to retain the flap in a certain position. For example, DE 26 53 106 A discloses a flap holder of this type, which has two actuating arms acted upon by a spring device. Two cam sections of different design on an actuating arm end run off at a contact face on the second actuating arm. A technical refinement is shown in U.S. Pat. No. 5,904,411, which discloses a flap holder with a pivoting flap, in which a spring-loaded setting part is directly coupled via a rigid connecting arm to a pivoting actuating arm. A translational movement of the setting part is thereby converted into a rotational movement of the actuating arm, which in turn moves the furniture flap into its open or closed position respectively. German published application DE 101 45 856 shows a folding lid for a cupboard, in which a spring-loaded setting part runs off at a setting contour of a cam, which in turn is coupled with an actuating arm to move the furniture flap. 
     Despite the advantageous technical improvements of the aforementioned publications, one fact, for example, proves to be disadvantageous. Namely, it has emerged that when furniture flaps of different weights are used, the same actuating process takes place. Lighter furniture flaps are moved or damped by the same spring force as heavier furniture flaps, so it is not possible to guarantee a favorable movement or damping process corresponding to the different weight of the furniture flaps. 
     SUMMARY OF THE INVENTION 
     It is therefore an object of the present invention to avoid the aforementioned disadvantage of the state of the art. 
     This is achieved according to the invention in an advantageous embodiment in that the transmission mechanism comprises at least one adjusting device to alter the transmission ratio between the movement of the setting member and the pivoting movement of the actuating arm. 
     The transmission ratio is preferably defined as the ratio of the path covered by the setting member to the angle of rotation of the actuating arm. DE 101 45 856 for example shows a transmission ratio which varies over the closing or opening path due to the curved design of the setting contour, but this is already pre-determined by the construction of the setting contour. The present invention, contrary to this, has a separately disposed adjustment device, which allows a precise and controlled adjustment of the transmission ratio. The transmission ratio can be varied in such a way that one and the same actuating mechanism can be provided for advantageous movement or damping of furniture flaps of different weights. 
     One advantageous embodiment of the invention is produced by the fact that the transmission mechanism comprises a pivotably mounted interlever, which is acted, on the one hand, upon by the spring-loaded setting member and on the other hand abuts on a setting contour surface formed on or attached to the actuating arm—preferably via a thrust roller. The lever ratios and thus the transmission ratio of the setting member to the actuating arm can be modified by the pivotably mounted interlever, where for preference a continuous adjustment is provided. It may thereby be advantageous if the position of the point of application of the spring-loaded setting member on the interlever is adjustable, to produce different lever ratios. In this connection it may also be advantageous that the distance of the point of application of the spring-loaded setting member from the axis of rotation of the interlever can be adjusted. 
     There are various ways to realize the spring device. It may be designed in such a way that the spring device comprises at least two or more—preferably disposed in parallel—tension springs. In a further advantageous embodiment of the invention, provision may also be made that the spring device comprises at least two or more—preferably disposed in parallel—compression springs. Obviously this also includes spring devices which consist of at least one tension spring and at least one compression spring. The spring device may be hingedly supported so that it can pivot in order to equalize tensions. This means that the pre-tensioning force in the direction of the setting member may be advantageously varied or adjusted. A hydropneumatic accumulator can also advantageously be used as a spring device. 
     According to a further embodiment, provision is made that the adjustment device is disposed or formed on the interlever, by means of which the point of application of the spring-loaded setting member with respect to the interlever can be adjusted. The pre-tension force of the spring device can be varied by the adjustment device such that the respective positions of the individual fulcrums change. Through the resultant lever ratios, the actuating mechanism can be adapted to match various sizes and/or weights of the movable furniture flaps. The design can advantageously be made such that the adjusting device comprises a rod or a threaded spindle along which the point of application of the setting member is displaceable. 
     A further advantageous embodiment of the invention is produced by the fact that the interlever comprises a crank guide along which the spring-loaded setting member can be guided. For example, a curve shape can be provided in the crank guide—preferably a side facing away from the spring device—through which the pre-tensioning of the spring device or its characteristic curve area can be varied. By the adjustability of the operative range or of the spring force area thus achieved, the transmission ratio can be defined in a controlled way within the specified crank guide. 
     Provision is advantageously made that the transmission mechanism comprises at least two adjustment devices to change the transmission ratio between the movement of the setting member and the pivoting movement of the actuating arm. It may then be advantageous if two separate adjustment devices are disposed, for coarse and fine adjustment of the transmission ratio respectively. 
     The inventive arrangement is characterized by a movable furniture part, in particular a furniture flap, with an actuating mechanism according to the invention. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       Further details and advantages of the present invention will be explained in more detail with the aid of the description of the figures while making reference to the drawings, which show: 
         FIG. 1   a ,  1   b  a schematic lateral sectional view through a furniture body with an inventive actuating mechanism in the closed position, with the spring device designed as a compression spring pack, and detail B from  FIG. 1   a,    
         FIG. 2   a ,  2   b  the actuating mechanism from  FIG. 1   a ,  1   b  in a half-open position, and detail A from  FIG. 2   a,    
         FIG. 3   a ,  3   b  the actuating mechanism shown in  FIG. 1   a ,  1   b  and  FIG. 2   a ,  2   b  respectively in the open position, and detail C from  FIG. 3   a,    
         FIG. 4   a ,  4   b , a further embodiment of a actuating mechanism in the open position in lateral view and in perspective view, where the spring device is designed as a tension spring pack, 
         FIG. 5   a ,  5   b  a lateral view and a perspective view of the actuating mechanism from  FIG. 4   a ,  4   b  in a half-opened position, 
         FIG. 6   a ,  6   b  a lateral view and a perspective view of the actuating mechanism from  FIG. 4   a ,  4   b  and  FIG. 5   a ,  5   b  respectively in the closed position, 
         FIG. 7   a ,  7   b  a lateral view and a perspective view of the actuating mechanism from  FIG. 4   a ,  4   b  to  FIG. 6   a ,  6   b  with altered transmission ratio, 
         FIGS. 8   a - 8   d ,  8   a ′- 8   d ′ various potential applications of the inventive actuating mechanism, 
         FIG. 9   a ,  9   b  a schematic exploded view and an assembled view of an inventive actuating mechanism with a compression spring pack as spring device, 
         FIG. 10   a ,  10   b  a schematic exploded view and an assembled view of an inventive actuating mechanism with a tension spring pack as spring device, 
         FIG. 11   a ,  11   b  a lateral view of an exemplary fold-up flap with an inventive actuating mechanism in the closed position and detail C from  FIG. 11   a,    
         FIG. 12   a ,  12   b  the fold-up flap from  FIG. 11   a ,  11   b  in the half-open position and detail B from  FIG. 12   a,    
         FIG. 13   a ,  13   b  the fold-up flap from  FIG. 11   a ,  11   b  and  FIG. 12   a ,  12   b  in the open position and detail A from  FIG. 13   a,    
         FIG. 14   a ,  14   b  a further embodiment of the invention with an adjustable transmission element, 
         FIG. 15   a ,  15   b  the embodiment from  FIG. 14   a ,  14   b  with increased transmission ratio, 
         FIG. 16  an exploded view of the embodiment from  FIG. 14  and  FIG. 15 , 
         FIG. 17   a - 17   c  perspective views of a further embodiment with two adjustment devices to modify the transmission ratio, 
         FIG. 18   a ,  18   b  lateral views of the embodiment from  FIGS. 17   a  to  17   c  in detail, and with cover removed, 
         FIG. 19   a ,  19   b  views during the coarse adjustment of the transmission ratio, 
         FIG. 20   a - 20   c  views during the fine adjustment of the transmission ratio, 
         FIG. 21   a ,  21   b  an exploded view of the transmission mechanism and an enlarged detail view, 
         FIG. 22  a further embodiment of the invention with two levers hingedly connected to each other, 
         FIG. 23  a perspective view of the embodiment from  FIG. 22 , 
         FIG. 24   a ,  24   b  lateral views of the embodiment from  FIG. 22  and  FIG. 23  with the pivoting arm in the fully open position and in a half-open position. 
     
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
       FIG. 1   a  shows a schematic view of an embodiment of an inventive actuating mechanism  1  in the closed position with a flap  3  pivotable about a horizontal axis,  FIG. 1   b  shows an enlarged view of detail B from  FIG. 1   a . This actuating mechanism  1  is fixed by means of a suspension device  15  on one vertical inner wall of a body of furniture  4 . The actuating mechanism  1  has a pivotably mounted actuating arm  2 , which is provided with the flexibly connected levers  2 ′,  2 ″ to move the flap  3  between an open and a closed position. The spring device  5  in the embodiment shown is designed as a compression spring pack, which has at least one or more compression springs—preferably arranged in parallel. The spring device  5  acts on a movably mounted setting member  13  with a force which acts in the direction of (toward) the flap  3 . The setting member  13  is thus linearly displaced in proportion to the loading of the spring device  5 . A transmission mechanism  7  converts the linear motion of the setting member  13  into a pivoting motion, which in turn acts on the actuating arm  2  to move the flap  3 . The transmission mechanism  7  comprises an adjustment device  8  to alter the transmission ratio between the linear motion of the setting member  13  and the pivoting motion of the actuating arm  2 . In the figure shown the transmission mechanism  7  comprises an interlever  9  so as to pivot mounted about the axis of rotation  14 , the interlever  9  being acted on from one side by the spring-loaded setting member  13  and on the other side abutting on a setting contour surface  12  formed on or attached to the actuating arm  2  via a thrust roller  11 . The setting contour surface  12  is formed or arranged on the end of the actuating arm  2  in the form of a curved control cam  10 . The control cam  10  is mounted on the axis of rotation  17 , and when the flap  3  is moved, it meshes with the thrust roller  11 . The interlever  9  is thereby pivoted by the spring-loaded setting member  13  clockwise about the axis of rotation  14 , as made clear in the following figures. 
       FIG. 2   a  shows the actuating mechanism  1  from  FIG. 1   a ,  1   b  in a half-open position.  FIG. 2   b  shows an enlarged view of detail A from  FIG. 2   a . The actuating mechanism  1  comprises a spring device  5  which is designed as a compression spring pack. The spring device  5  in the view shown is already partly unloaded in comparison to the spring device  5  from  FIG. 1 . The control cam  10  mounted on the fulcrum (axis of rotation)  17  rolls along the thrust roller  11 , as a result of which the interlever  9  mounted at the axis of rotation  14  is rotated clockwise by the spring-loaded setting member  13 . The application force of the thrust roller  11  is determined by the tension force of the spring device  5  and by the respective position of the control cam  10  with the setting contour surface  12  relative to the thrust roller  11 . 
       FIG. 3   a  shows the actuating mechanism  1  from  FIG. 1   a ,  1   b  and  FIG. 2   a ,  2   b  respectively in the open position.  FIG. 3   b  shows an enlarged view of detail C from  FIG. 3   a . The compression springs of the spring device  5  are essentially in a relaxed condition, whereby however a certain force acts at all times on the interlever  9 , so that the furniture flap  3  can be held in any position over at least a part of the pivoting path. In  FIGS. 1 to 3 , for reasons of clarity, the transmission ratio has not been changed by the adjustment device  8 , since the point of application  6  has not been displaced within the crank guide  18 . 
       FIGS. 4   a  and  4   b  show a further embodiment of the invention in a lateral and in a perspective view. The spring device  5 , unlike those in  FIGS. 1 to 3 , is designed as a tension spring pack. The spring-loaded setting member  13  in the figure shown is displaceably mounted along the guide rod  51 . The spring-loaded setting member  13  acts upon a trough-shaped push rod  54 , which is coupled at its other end with the interlever  9 . The relevant point here is that the push rod  54  is not connected with the spring suspension  55 , i.e. the trough-shaped push rod  54  is displaceably guided behind the spring suspension  55 . The interlever  9  is pivotably mounted on its axis of rotation  14 , whereby the spring device  5 , via the push rod  54 , exerts a counter-clockwise force on the interlever  9 . The actuating arm  2  (and thus a flap  3 , not shown) in the figure shown is in the open position. The actuating arm  2  is pivotably mounted on the fulcrum  17  and has a control cam  10  with a setting contour surface  12 . The thrust roller  11  is pressed by the force of the spring device  5  onto the setting contour surface  12 . When the actuating arm  2  is now moved downwards, the setting contour surface  12  rolls down along the thrust roller  11 , so that the interlever  9  is pivoted clockwise about the axis of rotation  14 . This also displaces the push rod  54  to the left and pushes the spring-loaded setting member  13 , in the direction of the arrow A shown, gradually to the left, as the result of which the spring device  5  is tensioned. The spring suspension  55  is mounted in an essentially fixed position by the two pins  53 , allowing only slight play compensation by the two longitudinal hole type guides  52 . In principle, the spring suspension  55  could also be disposed completely fixed. But since the guide rod  51  is movably mounted on the pivoting axis  16  opposite the suspension device  18 , a compensating movement of the spring suspension  55  can be enabled by the longitudinal hole type guides  52 . The adjustment device  8  for adjusting the transmission ratio comprises a rod  19  or a threaded spindle mounted on the interlever  9  along which the point of application  6  of the push rod  54  is displaceably mounted. 
       FIG. 5   a  and  FIG. 5   b  show the actuating mechanism  1  from  FIG. 4   a ,  4   b  in a half-open position of the actuating arm  2 . It can be seen that the interlever  9  mounted on the axis of rotation  14  has been pivoted clockwise by the closing movement of the actuating arm  2 . This movement has also caused the trough-shaped push rod  54  to be moved further to the left against the spring-loaded setting member  13  linked thereto. The springs of the spring device  5  are gradually tensioned in this process and the resultant force presses the thrust roller  11  against the setting contour surface  12  of the actuating arm  2 . This force can be measured by the adjustability of the transmission ratio to compensate for the weight of the flap  3 , so that the flap  3  is preferably held in every pivoted position of the actuating arm  2 . 
       FIG. 6   a  and  FIG. 6   b  show the actuating mechanism  1  from  FIG. 4   a ,  4   b  and  FIG. 5   a ,  5   b  in the fully closed position of the actuating arm  2  (and with it a flap  3 , not shown). The interlever  9  mounted on the axis of rotation  14  has been pivoted still further clockwise by the closing movement of the actuating arm  2 . This has pushed the trough-shaped push rod  54 , no longer visible, behind the fix-mounted spring suspension  55 , so that the spring-loaded setting member  13  is in the outermost end position relative to the guide rod  51 , so that the springs of the spring device  5  are also in a condition of maximum tension. In  FIGS. 4 to 6  the transmission ratio has not been changed for reasons of clarity, since the point of application  6  has not been moved in its position relative to the rod  19 . 
       FIG. 7   a  and  FIG. 7   b  show the actuating mechanism  1  from  FIG. 4   a ,  4   b  to  FIG. 6   a ,  6   b  with a tension spring pack as spring device  5 . In the figure shown, the transmission ratio has been altered by a displacement of the point of application  6  on the interlever  9 , which is achieved by the adjustment device  8  on the interlever  9 . The point of application  6  is displaceably mounted on a rod  19 , whereby the rod  19  is preferably designed as a threaded spindle. A geared wheel  25 —preferably a toothed wheel—which can be adjusted with a hexagonal member  26 , is provided to adjust the point of application  6 . The gear wheel  25  meshes with an intermediate wheel  27 , which is integrally fixed to the threaded spindle  19 . The point of application  6  is displaced via a bolt  28 , not shown, inside the coupling piece  20 , the bolt  28  being provided with an internal thread. Any rotation of the hexagonal member  26  thus effects a rotation of the gear wheel  25 , which moves the intermediate wheel  27  integrally mounted on the threaded spindle  19 , whereby the rotation of the threaded spindle brings about a height (location) adjustment of a bolt  28  (i.e., location of bolt  28  along spindle  19 ) provided with an inner thread. A self-locking worm gear with play-free, or at least with minimal play, can hereby be enabled to displace the point of application  6 . The adjustment of the hexagonal member  26  can obviously also be done without tools, for example with a knurled screw turned by hand. The point of application  6  can thereby also be displaceably guided within a crank guide  18 . The crank guide  18  can also have a curved shape or a curvature, as the result of which the tensioning of the spring device  5  and with it the characteristic curve area thereof, can be altered. Different lever ratios are created by the altered position of the point of application  6 , since the relative positions of the individual points of rotation are also altered. In the figure shown, the pressure of the thrust roller  11  on the setting contour surface  12  is reduced due to the displaced position of the point of application  6 , so that lighter furniture flaps  3  can be advantageously moved and damped according to their weights. 
       FIGS. 8   a - 8   d  and  FIGS. 8   a ′- 8   d ′ show various potential applications of the inventive actuating mechanisms  1 . The views each show a lateral view of the furniture bodies  4  on which a furniture flap  3  opening upwards is disposed. The upper rows according to  FIGS. 8   a - 8   d  each show the closed position of the furniture flap  3 , while the lower views in  FIGS. 8   a ′- 8   d ′ show a lift-up flap, in  FIG. 8   b ′ a bifold upward flap, in  FIG. 8   c ′ a high-lift flap and in  FIG. 8   d ′ a swing-up flap in an open position. 
       FIG. 9   a  and  FIG. 10   a  show exploded views of the actuating mechanism  1  from  FIGS. 1 to 3  (compression spring pack) and the actuating mechanism  1  from  FIGS. 4 to 6  (tension spring pack),  FIG. 9   b  and  FIG. 10   b  show the respective actuating mechanism  1  in mounted condition. The actuating mechanisms  1  are mounted on the furniture body  4  by means of a suspension device  15 . The threaded spindle  19  is passed through a rod end bearing and integrally connected to an intermediate wheel  27 . Also to be seen is the bolt  28 , which has an inner thread and sits within the coupling piece  20 . The threaded spindle  19  engages in the thread of the bolt  28 , so as to displace the setting member  13  in the axial direction of the threaded spindle  19 . A fitting  21  is provided to link both levers  2 ,  2 ′ with the flap  3 . 
       FIG. 11   a  shows a lateral view of an exemplary bifold flap  3  arranged so as to open upwardly with an inventive actuating mechanism  1  in the closed position.  FIG. 11   b  shows the enlarged detail C from  FIG. 11   a . The actuating mechanism  1  is fixed via a suspension device  15  to one vertical side wall of the furniture body  4 . A furniture flap  3  is disposed on its pivotably mounted actuating arm  2  at a hinge point  22 . The furniture flap  3  is flexibly attached via a horizontal pivoting axis  24  to the flap part  3 ′. To pivot the flap part  3 ′ in relation to the furniture body  4 , a hinge  23  with at least two hinge arms is provided, which allows a pivoting motion about a horizontal axis.  FIGS. 12   a ,  12   b  show the actuating mechanism  1  in the open position. In this case the design can be such that the actuating arm  2  is acted upon over at least a part of the pivoting path by a torque which allows the flap  3 ,  3 ′ to dwell in any position between an open and a closed position. 
       FIGS. 14   a  and  14   b  show the lateral view of the actuating mechanism  1  according to a further embodiment of the invention. The actuating arm  2  in  FIG. 14   a  is in a slightly open position, and in  FIG. 14   b  in a further opened position. The actuating mechanism  1  is fixed by means of a suspension device  15  to a vertical side wall of a furniture body. The spring device  5  is pivotably mounted on a fixed swiveling axis  16 . This spring device  5  comprises a compression spring pack, which acts on the setting member  13  with a force in the direction of (toward) the setting contour surface  12  of the control cam  10 . The setting member  13 , contrary to the linear movement shown in  FIG. 1 to 13 , performs a pivoting movement. The transmission mechanism  7  in the figure shown has two levers  33 ,  33 ′ which are rotatably and fixed-mounted respectively on a fulcrum  34 ,  34 ′. A transmission element  32  which can be adjusted by a user is disposed between the two levers  33 ,  33 ′, with the position of the transmission element  32  determining the transmission ratio of the path of the setting member to the angle of rotation of the actuating arm  2 . If the transmission element  32  is being adjusted further downwards between these two levers  33 ,  33 ′, the setting member  13  can move further to the right. This increases the expansion path and with it the range of action of the spring pack  5 . The lever  33 ′ has a thrust roller  11  on its end facing away from the fulcrum  34 ′, the roller  11  being pressed against the setting contour surface  12  of the control cam  10 . The control cam  10  is rotatably fixed on its fulcrum  17 . The control cam  10  is disposed or formed on the end of the actuating arm  2 , by which a flap  3  is movable into the open or closed position. 
       FIGS. 15   a  and  15   b  show the embodiment from  FIG. 14   a  and  FIG. 14   b  respectively with transmission element  32  moved further downwards. By adjusting the transmission element  32  in the direction of the fulcrum  34  of the lever  33 , the setting member  13  can be displaced further to the right, which results in a greater expansion path for the spring device  5  and an increase in the transmission ratio. The transmission ratio can thus be adjusted in simple fashion, depending on the position of the transmission element  32 . In the embodiment shown, the lever  33 ′ has at least one longitudinal hole  36 , along which the transmission element  32  can be guided. This is fixed with the aid of the locking screw  35 . However, the transmission element  32  can be attached just as well on the lever  33  connected with the setting member  13 . 
       FIG. 16  shows an exploded view of the inventive embodiment from  FIGS. 14   a, b  and  FIGS. 15   a, b . The two levers  33 ,  33 ′ can be seen, their stationary fulcrums  34 ,  34 ′ being offset with respect to the suspension device  15 . The lever  33 ′ has a longitudinal hole  36 , while a locking screw  35  passes through the lever  33 ′ and the transmission element  32  and fixes these in place. The length of the longitudinal hole  36  determines the upper and lower end range of the transmission ratio. 
       FIG. 17   a  shows a further embodiment of the invention.  FIGS. 17   b  and  17   c  each show enlarged detail views. The setting member  13  on which the force of the spring device  5  acts is coupled with the actuating arm  2  via an interlever  9  and via the control cam  10 . In this embodiment, provision is made that the transmission mechanism  7  comprises at least two adjustment devices  8   a  and  8   b  to vary the transmission ratio between the movement of the setting member  13  and the pivoting movement of the actuating arm  2 , as shown in  FIGS. 17   b  and  17   c  respectively. The position of the bearing point of the setting member  13  on the interlever  9  can be adjusted by the adjustment device  8   a  and  8   b , so that the transmission ratio can be exactly defined. The interlever  9  is fixed and pivotably mounted on the fulcrum  40 . Advantageously, provision is made that the transmission ratio is differentially adjustable by the at least two adjustment devices  8   a  and  8   b . The design can thereby be made such that adjustment device  8   a  is provided for coarse adjustment and adjustment device  8   b  for fine adjustment of the transmission ratio. The position of the point of application of the setting member  13  on the interlever  9  can be exactly set by the adjustment devices  8   a  and  8   b , and thus also the transmission ratio.  FIG. 17   c  shows an enlarged detail view from  FIG. 17   b  in the transitional area between the setting member  13  and the interlever  9 . The adjustment device  8   a  provided for coarse adjustment comprises a rack  37  connected with the interlever  9 , which engages an adjustable element  38  with at least one detent tooth  39  (not shown), adjustable by a user. The detent tooth  39  is lifted out of a gap in the rack  17  by torsion of the adjustment device  8   a  and replaced in an adjacent gap. The fine adjustment device  8   b  comprises an eccentric cam  30 , where provision is advantageously made that the regulating range of the eccentric cam  30  corresponds to the tooth width of the rack  37 , thus enabling a continuous adjustment range of the position of the bearing point of the setting member  13  on the interlever  9 . 
       FIG. 18   a  shows a lateral view of the transmission mechanism  7  fixed onto the suspension device  15  from  FIGS. 17   a  and  17   b  respectively.  FIG. 18   b  shows the same transmission mechanism  7  without cover, so that the internal parts are visible. The spring-loaded setting member  13  is adjustably mounted on the interlever  9 . The interlever  9  is pivotably mounted on a fulcrum  40 . The actuating arm  2  is in the fully open position so that the control cam  10  of the thrust roller  11  can be brought out of engagement. The detent tooth  39  belonging to the adjustment device  8   a  engages in the rack  37  disposed or formed on the interlever  9 . The adjustment device  8   a  is provided for coarse adjustment of the transmission ratio. The adjustment device  8   b  also acts on the rack  37 , whereby an eccentric cam  30  alters the position of the bearing point of the setting member  13  on the interlever  9 . The adjustment device  8   b  is provided for fine adjustment of the transmission ratio. 
       FIG. 19   a  shows the coarse adjustment of the transmission ratio by means of a screwdriver  41 , and  FIG. 19   b  an enlarged detail view from  FIG. 19   a . The adjustment device  8   a  is actuated with the screwdriver  41  in order to alter the position of the bearing point of the setting member  13  on the interlever  9 . In order best to counterbalance the various sizes of the flaps  3  and thus various weights, the force on the setting contour surface  12  of the control cam  10  must be adjustable. By turning the adjustment device  8   a , this winds down the rack  37 , the setting member  13  is lifted out of the toothing at a rotation of 45° and the detent tooth  39  re-engages following a rotation of the adjustment device  8   a  by 90°. 
       FIG. 20   a  shows the fine adjustment of the transmission ratio using a screwdriver  41 ,  FIG. 8   b  and  FIG. 8   c  each showing enlarged detail views. Once the coarse adjustment has been performed as described in  FIG. 19   a ,  19   b , the screwdriver  41  is positioned on the adjustment device  8   b . This fine adjustment of the transmission ratio occurs via the previously described eccentric cam  30 . The area of adjustment of the eccentric cam  30  preferably corresponds to the tooth width of the rack  37 . A smooth adjustment of force is possible due to the combination of coarse and fine adjustment. 
       FIG. 21   a  shows an exploded view of the two-stage adjustable transmission mechanism  7  from  FIGS. 17 to 20 ; and  FIG. 21   b  shows an enlarged detail view. The setting member  13  loaded by the spring device  5  is displaceably coupled to the rack  37  via the bolt  42  (adjustment device  8   a ) and with the eccentric cam  30  (adjustment device  8   b ). The bolt  42  projects through the adjustable element  38 , on which at least one detent tooth  39  is disposed. The eccentric cam  30  projects, in the mounted state, through the opening  43  in the rack  37 . By turning the bolt  42  and the eccentric cam  30 , the transmission ratio can be varied precisely by a smooth force adjustment. The front end of the interlever  9  forms a cover plate  44 . 
       FIG. 22  shows a further embodiment of the invention in a lateral view. Instead of a setting contour  12 , the setting member  13  is connected via at least two levers  31 ,  31 ′, flexibly joined together, with the actuating arm  2 . To adjust the transmission ratio, the position of the bearing point of the setting member  13  on at least one of the levers  31 ,  31 ′ is adjustable. The adjustment devices  8   a  and  8   b  known from  FIGS. 17 to 21  are used for coarse and fine adjustment respectively of the transmission ratio. The setting member  13  can be displaced by the adjustment devices  8   a  and  8   b  along the surface  49 . To prevent or at least to reduce striking noises when closing the flap  3 , a damping device  47  may be provided. Here, for example, a linear damper can be used, which rests on a tab  48  on its side facing away from the flap. On its front end the damping device  47  has a stop  46 , which co-operates with a projection  45  disposed or formed on the actuating arm  2  when closing the flap  3 . A piston rod connected with the stop  46  is displaced by the projection  45  into the interior of the damping device  47 . It is advantageous in this case if a fluid cylinder is provided, but in principle all other damping devices known according to the state of the art can be used (for example rotation dampers). 
       FIG. 23  shows a perspective view of the embodiment from  FIG. 22 . Two levers  31 ,  31 ′ are linked to the outside of the lever  31 , which are connected with the actuating arm  2  fastened to the axis of rotation  17 . Actuation of the adjustment devices  8   a  and  8   b  leads to a change in the position of the setting member  13  on the surface  49  of the lever  31 . When the flap  3  is closing, the projection  45  presses against the stop  46  of the damper  47 , whereby the final closing path of the flap  3  is damped. 
       FIG. 24   a  and  FIG. 24   b  show the embodiment from  FIG. 21  and  FIG. 22  respectively in lateral views, where the actuating arm  2  is in the fully open position in  FIG. 24   a  and in a half-open position in  FIG. 24   b . To prevent any collision with the levers  31 ′,  31 ″ when the actuating arm  2  is fully open, a cavity  50  is provided on both levers  31 ′,  31 ″. The articulated hinge with the axis of rotation  17  of the actuating arm  2  can be seated, at least partly, in the cavity  50 . 
     The present invention is not limited to the examples shown, but covers or extends to all variants or technical equivalents which may fall within the scope of the following claims. The position details selected in the description, such as for example above, below, lateral etc., relate to the usual mounting position of the actuating mechanism  1  or to the figure directly described and shown, and should be transferred accordingly to the new position, when there is any change in position. The actuating mechanism  1  was realized in the drawings shown as a lever solution. It is, however, equally conceivable and possible to use a toothed wheel variant. It may also be advantageous to dispose the inventive actuating mechanism  1  on both sides of a cupboard-type piece of furniture. In the figures shown, a translational movement or a pivoting movement of the spring-loaded setting member  13  is shown. However, it also lies within the scope of the invention to convert a rotational movement of the setting member  13  (e.g. by a torsion spring) into a pivoting movement of the actuating arm  2 , in which case an exact and defined adjustment of the transmission ratio is provided by the adjustment device  8 . The invention also makes provision for the inventive actuating mechanism  1  to be used with absolutely identical construction on both side walls (left/right) of a piece of furniture, i.e. without mirror-image components, and with completely identical design thereof.