Furniture hinges with cam adjustment system

A furniture hinge comprises a first (11) and a second (12) fastening element designed to be secured to two furniture parts to be hinged together, and an arm (15) which ends at one extremity with the first fastening element (11) and at the other extremity has a pivot (16) pivoting it to the second fastening element (12) to achieve the joint of the hinge. The arm (15) is made in two portions (17, 18) sliding reciprocally upon operation of adjusting means (22) composed of a cam (23) to allow adjustment of the reciprocal position of the first and second fastening element. Advantageously, the sliding surface (20) of the second portion (18) comprises an elongated housing (24) to receive the cam (23) with a lateral surface of the cam which reacts against the side walls of the housing. The sliding surface (19) of the first portion (17) comprises a through hole (25) which receives, with a minimum of side play, a control pin (26) protruding from the cam so as to be operated from the outside.

BACKGROUND OF THE INVENTION 
This invention refers to furniture hinges with a lateral adjusting device 
and in particular to single-pin cup type automatic hinges. 
Cup-type invisible hinges characterized by a single pivot have been widely 
used for some time now. In their simplest embodiment they are composed of 
four main components: a fixed portion or wing (designed to be integrally 
secured to the side of the furniture unit), a movable portion or box 
(designed to be integrally secured to the door), a pivot and a spring to 
ensure automatic closing. These simple hinges do not allow for any 
adjustment between the fixed portion and movable portion in order to 
ensure adjustability of the covering of the side panel by the door, hinges 
of the above-mentioned type have been proposed, in which the wing is made 
in two pieces, one of which bears the fastening means for fastening it to 
the side panel and the other bears the pivoting with the box. The two 
pieces are connected by means of a screw screwed into one of them and 
fitting with its shank into an elongated aperture in the other. 
When the screw is loosened the two pieces can slide reciprocally, thereby 
permitting adjustment, The subsequent retightening of the screw locks the 
pieces in the desired position. 
However, the adjustment is difficult and imprecise. In fact, when the 
fastening screw is loosened the two portions are free to slide along the 
entire length of the elongated aperture, and the desired degree of 
coverage of the side panel can only be found by trial and error. The 
adjustment is also hampered by the fact that the hinges are burdened with 
the weight of the door which tends to make the two parts slide 
inappropriately as soon as the fastening screw is loosened. 
Moreover, when the hinge is closed, the head of the screw protrudes inside 
the box in a central position, creating an obstruction which could be 
critical for housing the closing mechanism of the hinge. 
The general scope of this invention is to obviate the aforementioned 
problems by providing a hinge having a fine adjustment which is easy to 
operate and of limited dimensions. 
SUMMARY OF THE INVENTION 
This scope is achieved, according to the invention, by providing a 
furniture hinge comprising a first and a second fastening element designed 
to be secured to two furniture parts to be hinged together, and an arm 
which ends at one extremity with the first fastening element and at the 
other extremity has a pivot pivoting it to the second fastening element to 
achieve the joint of the hinge, the arm being made in two parts sliding 
reciprocally upon operation of adjusting means to allow adjustment of the 
reciprocal position of the first and second fastening element, 
characterized by the fact that the adjusting means comprise a cam with 
axis of rotation pivoted to the first part and a cam surface reacting 
against the second part to achieve said adjustment upon rotation of the 
cam. 
A further scope of this invention is to provide an adjustment of the 
aforesaid type comprising a cam devoid of instability and which permits 
uniform and precise adjustment at any point of the adjustment stroke. This 
further scope is achieved, according to the invention, by providing cam 
adjusting means in which, for any angular position of the cam in its 
active stroke around the axis, the centre of rotation of the cam is 
substantially within the region of a straight line passing through a point 
of contact between a lateral surface of the cam and a bearing surface of 
the second element, said straight line being slanted by an angle .PHI. 
identical to the angle of friction in the point of contact.

DETAILED DESCRIPTION OF THE INVENTION 
With reference to the figures, a hinge 10, made according to the invention, 
comprises a first and a second fastening element, respectively indicated 
by 11 and 12, designed to be secured to two furniture parts 13, 14 to be 
hinged together. For example, the two furniture parts can be, 
respectively, a side panel and a door of a furniture unit. The hinge 
comprises an arm 15 which ends at one extremity with the first fastening 
element 11 and at the other extremity with a pivot 16 pivoting it to the 
second fastening element to achieve the joint of the hinge. FIG. 1 shows 
the closed position of the hinge, the open position being obvious to the 
expert in the field on the basis of the aforesaid figure. 
The arm 15 is composed of two parts 17, 18 which slide reciprocally to 
enable the adjustment of the reciprocal position of the first and second 
fastening element. In particular, the first and second part have 
reciprocal sliding parts and sections 19, 20 which overlap each other. 
Advantageously, the second part 18 comprises lateral sides walls or edges 
21 which are disposed facing each other on opposing sides of the sliding 
section 20 and are shaped to form a guide channel which slidingly receives 
the sliding section or wing 19 of the first part 17. In this way, the 
first part can slide exclusively in a longitudinal direction along the 
second part. 
The first part 17 comprises the pivot 16 securing it to the second 
fastening element 12 and the second part 18 is L-shaped, one arm of the L 
forming the first fastening element 11 and the other arm of the L forming 
the sliding section 20. 
The second fastening element 12 is advantageously made in the form of a cup 
or box recessed so as to contain the pivot, made with a single pin 27 
around which the pivot end of part 17 is wound. 
The cup can also contain a spring 28 reacting between the cup and the pivot 
to define stable open and closed positions of the hinge, as is well know 
to the expert in the field. 
As can be clearly seen in FIG. 1, when the hinge is in the closed position 
the arm of the L forming the sliding section 20 is disposed parallel to 
and facing the bottom of the cup 12 and the first part 18 of the arm is 
contained in the cup. 
According to the invention, disposed between the first and second part are 
cam adjusting means 22 comprising a cam 23. 
As is also clearly shown in FIG. 2, the sliding section 20 of the second 
part 18 comprises an elongated cam housing or slot 24 for receiving the 
cam 23 so that the lateral surface of the cam can react against lateral 
walls of the housing. The sliding section 19 of the first part 17 
comprises a through hole 25 which receives, and has rotable therein, a 
pivot 26 protruding from the cam to define the axis of rotation of the 
cam. As can be clearly seen in FIG. 3, the pivot 26 has an upper end which 
faces out from the first part 17 to constitute the operating end (for 
example, by means of a screwdriver) of the cam. The cam can be shaped, for 
example, in the form of a flat disk with a diameter slightly smaller than 
the smallest dimension of the slot 24. The misalignment between cam disk 
and pivot 26 is identical to or slightly smaller than the difference 
between the maximum and minimum dimension of the slot. Said misalignment 
is equivalent to half the maximum desired adjusting stroke. 
It can be clearly seen that when the hinge is in the closed position, there 
is no further obstacle caused by the cam in the cup. 
The effect of the rotation of the cam, which has an axis of rotation 
pivoted to the first part and cam surfaces reacting against the second 
part, is obvious from FIG. 3. It is thus possible to achieve a precise and 
easy adjustment of the reciprocal position of the first and second 
element. Thanks to the use of a cam, no further locking means are 
necessary between the first and second part of the arm. Moreover, the 
first and second parts are never free to slide indiscriminately with 
respect to each other. 
FIG. 4 shows in detail a possible embodiment of the slot 24 to facilitate 
assembly of the parts 17 and 18 of the arm 15 with the cam between them. 
In particular, the slot is made deeper than the thickness of the cam 
including the pivot 26, and the bottom of the slot has an incision 29 
which divides it into two lateral wings 30 sufficiently pliable to be bent 
towards the inside of the slot by exerting the appropriate pressure. 
The assembly begins with the complanate wings 30. First the cam is inserted 
inside the slot so that the cam rests on the bottom of the slot. Since the 
overall thickness of the cam is small than the depth of the slot, the 
sliding wing of part 17 can be inserted without hindrance into the guide 
channel between the edges 21, after which the cam is pushed with a tool 
(not shown) passing through the slit. 29, so as to position the pivot 26 
in the through hole 25. At this point the cam can be locked in place by 
bending the wings 30 inwards (for example by riveting) to bring them into 
the position shown in FIG. 3. 
The foregoing description of an embodiment applying the innovative 
principles of this invention is obviously given by way of example in order 
to illustrate such innovative principles and should not therefore be 
understood as a limitation to the sphere of the invention claimed herein. 
For example, in order to fulfill particular requirements, the hinge may 
have a shape differing from the one shown. Moreover, the assembly of the 
sliding parts and the cam can be made different from that shown. For 
example, the cam can be secured in the housing by means of screws instead 
of by bending the bottom of the housing. Lastly, the cam can have a shape 
different from the circular one shown as an example. 
FIG. 5 schematically shows a cam adjusting device, generically indicated by 
30, for adjusting the position between a first part, integral with a slot 
31 containing a cam 32, and a second part integral with a housing (not 
shown) for rotation of a pivot 33 controlling the cam 32. The housing 31 
comprises an internal lateral surface 34 against which reacts a 
corresponding lateral surface 35 of the cam 32. The surface 34 of the 
housing has a substantially rectilinear section tangent to the point of 
support 36 upon it on which the surface 35 of the cam rests. A second 
internal lateral surface 37 of the housing is disposed facing the surface 
34 of the housing so as to have a rectilinear section substantially 
parallel to the rectilinear section of the first surface and to constitute 
a support for a second lateral surface 38 of the cam. As will be clear 
from the examples described further on, the housing of the pivot is 
obliged to move in a direction perpendicular to the planes 34 and 37. 
Upon rotation of the cam around the axis 48 of the pivot, the axis itself 
oscillates between an upper position of maximum distance from the lower 
wall 34 of the housing (reached when the cam has its maximum radius R2 in 
point 36) and a lower position of minimum distance from it (reached when 
the cam has its minimum radius R1 in point 36). In FIG. 5, the cam is 
represented in an intermediate position. 
Acting on the cam are a force of action, indicated by the arrow 39, applied 
in the point 36 of contact between the body of the cam and the lower wall 
of the housing, and an identical and opposing force of reaction, indicated 
by the arrow 40, which acts between the pivot 33 and its housing and which 
can be considered as passing through the centre of the pivot. 
In the known cam adjusting devices, for example comprising a cylindrical 
cam body, the lines of application of the forces of action and reaction 
coincide when the cam is in one of the extreme upper or lower positions, 
while they are misaligned in the intermediate positions. In this 
situation, the two forces generate a torque which tends to rotate the 
eccentric towards the dead centre. The friction between the cam and its 
housing and between the pivot and its housing contrast said torque, but in 
some conditions the torque can become excessive and the cam rotates 
spontaneously towards the dead centre. 
The most disadvantageous condition is when the cam is half way through the 
adjustment, since in this situation the misalignment between the forces of 
action and reaction is at its maximum. Consequently, in order to prevent 
spontaneous rotation it is necessary to ensure that in this position the 
torque does not exceed the maximum value beyond which spontaneous rotation 
occurs. This, however, sets a limit to the maximum adjustment possible for 
a cylindrical cam in relation to its size. 
This is the main reason why the problem is even more serious whenever 
considerable adjustments are required compared to the space available for 
housing the eccentric. According to the innovative principles of this 
invention, it has been found that if the centre of rotation of the cam 
moves along a particular straight line or sheaf of straight lines instead 
of, for example, along an arc of a circumference as occurs for the 
cylindrical cams, it is possible to maximize the amplitude of the 
adjustment without encountering instability. 
FIG. 6 shows a graph which explains this. The horizontal axis coincides 
with the surface 34 tangent to the surface of the cam. The vertical axis 
represents the perpendicular at the tangent point 36. The straight line 41 
is the line of friction, that is to say the line which crosses through the 
tangent point 36 and is slanted by an angle .PHI. with respect to the 
perpendicular, where .PHI. is the traditional angle of sliding friction 
between the cam and the bearing surface. 
According to the invention, in any angular position of the cam along its 
active stroke, the centre of rotation of the cam must be substantially in 
the region of the line of friction as defined above. In other words, the 
centre of rotation of the cam must lie within a strip 42 containing the 
line of friction 41. 
The best possible condition is when the centre of rotation is situated 
constantly on a boundary line 43, parallel to the line of friction and at 
a distance from it by a value b=r*fp*cos.PHI., where r is the radius of 
the pivot 33 and fp is the friction coefficient of the contact between the 
pivot and its housing. The best possible condition is understood to mean 
the condition in which the maximum possible amplitude of the adjustment is 
achieved without any point of instability in the active stroke of the cam. 
Moreover, the raising of the pivot will be substantially proportional to 
the angle of rotation of the cam and consequently uniform adjustment will 
be achieved along the entire active stroke of the cam. 
In the particular case of identical friction coefficients between the cam 
and its housing and between the pivot and its housing, that is to say when 
fp=tan.PHI., then b=r*sen.PHI.. This means that the cam must be shaped in 
such a way that, as shown in FIG. 5, a segment 44 crossing through the 
tangent point 36 and the point 45 of the pivot which is furthest away from 
the surface 34 is slanted by the angle .PHI. with respect to the 
perpendicular to the surface 34. In other words, the best possible 
condition is achieved when, for any angle of rotation of the cam within 
its active stroke, the point 45 is situated on the line of friction 41. 
This makes tracing out the cam by points particularly easy. 
In the case of a cam which, as shown in FIG. 5, rotates between two 
surfaces 34 and 37, by calculating the cam portion 35 which slides over 
the surface 34 so as to fulfill the rule indicated above, the cam portion 
38 which slides over the surface 37 can be easily calculated by simply 
ensuring that the distance L between the surfaces 37 and 34 remains 
constant in the tangent points with the cam. 
A cam with an active profile 35 according to the invention can be 
identified reasonably accurately, disregarding the radius of the pivot, by 
the envelope of straight lines distant from the centre of rotation of the 
cam by a distance Dn=Dn-1*.alpha.P*tan.alpha., with Dn identical to the 
distance from the centre of the nth line, Dn-1 identical to the distance 
of the previous line to the nth line from the centre of the cam, .alpha.P 
identical to the angular pitch of calculation of the cam (that is to say: 
.alpha.P identical to the angle between the line n and the line n-1), 
.alpha. identical to the angle of inclination (in radians) between the 
tangent to the cam and the perpendicular to the line joining the tangent 
point to the centre of the cam. The angle .alpha. must be smaller than the 
angle of friction .PHI. between the cam and its housing. In particular, 
for the best possible condition .alpha.=.PHI.. The envelope of straight 
lines on the other profile 38 of the cam is obtained by tracing the 
parallel lines at a distance L from the lines of the first envelope. FIG. 
7 shows the overall envelope. 
Said envelope can be advantageously developed by an automatic calculation 
program. 
With reference to FIG. 7, the first step in calculating the profile 
consists in tracing a straight line 46 at a distance Do from the axis 48 
of rotation of the cam, corresponding to R1, that is to say at the minimum 
distance foreseen between the axis of rotation and one of the two walls of 
the housing bearing the cam. It is obvious that the profile can be traced 
by taking the distance from the lower wall or from the upper wall of the 
housing. From the opposite part with respect to the axis of rotation, a 
straight line 47 is then traced parallel to the line 46 and at a distance 
L from it. The lines traced are then made to rotate by the angle .alpha.P 
around the centre of rotation 48 of the cam. The new distance 
D1=D*.alpha.P*tan.alpha. is then calculated and the corresponding line 
rotated by the angle .alpha.P with respect to the previous line and the 
parallel line at distance L are traced. The construction of the envelope 
proceeds repeatedly in this way until it is observed that Dn&gt;=R2, that is, 
until the desired amplitude of adjustment is achieved. This must obviously 
occur before a 180.degree. profile is traced. It is clear that to ensure 
better precision in the determination of the cam profile it is necessary 
for the angle .alpha.P to be chosen sufficiently small. 
At this point it is evident how a cam adjusting device according to the 
invention is achieved. The vicinity of the centre of the cam to the 
outermost line 43 obviously depends upon the tolerances used in 
constructing the device. In fact, it must be considered that going outside 
the strip 42 beyond the line 43 leads to the onset of instability in the 
adjustment. In general, it is consequently preferable to maintain the 
centre of rotation slightly more within the strip 42 along the entire 
adjustment stroke. 
As can be seen in FIG. 5, in addition to the active profile as described 
above, it is advantageous for the cam to have a radially protruding shank 
49 to constitute a limit stop to the rotation of the cam by its engagement 
in recesses 50, 51 in the housing 31. 
FIGS. 8 and 9 show a furniture hinge, generically indicated by 110, made 
similar to the hinge of FIG. 1, but with the adjusting device described 
above. Parts similar to those of the hinge of FIG. 1 will be indicated 
using the same numbers as in FIG. 1, The hinge 110 comprises a first and 
second fastening element, respectively indicated by 11 and 12, designed to 
be secured to two furniture parts 13, 14, for example a side panel and the 
respective door, to be hinged together. The hinge comprises an arm 15 
which ends at one extremity with the first fastening element 11 and at the 
other extremity with a pivot 16 pivoting it to the second fastening 
element to achieve the joint of the hinge. The arm 15 is composed of two 
reciprocally sliding parts 17, 18. The first part 17 comprises the pivot 
16 securing it to the second fastening element 12 and the second part 18 
is L-shaped, one arm of the L forming the first fastening element 11 and 
the other arm of the L forming the sliding surface for the first part 17. 
The sliding is guided by lateral edges 21 which form a guide channel which 
slidingly receives the sliding wing of the first part 17. 
The second fastening element 12 is advantageously made in the form of a cup 
or box recessed so as to contain the pivot, made with a single pin 27 
around which the pivoting end of part 17 is wound. 
A spring 28 reacts between the cup and the pivot to define stable open and 
closed positions. 
As can also be clearly seen in FIG. 9, where the cup has been removed for 
greater clarity, disposed between the first and second part are cam 
adjusting means 30, made according to the invention, comprising a cam 32, 
of the type shown in FIG. 5, pivoted, by means of a pivot 33 received in a 
housing 25, to part 17 so as to react against lateral surfaces of a 
housing 31 in part 18. As can be clearly seen in FIG. 9, the pivot has an 
upper end which faces out from the first part 17 to constitute the 
operating end (for example, by means of a screwdriver) of the cam. Upon 
rotation of the cam, part 17 slides with respect to part 18, thereby 
providing precise and stable lateral adjustment of the position of the 
door.