RU2816567C2 - Rotary fittings and piece of furniture - Google Patents

Abstract

FIELD: furniture.

SUBSTANCE: group of inventions relates to rotary fittings for movable parts of furniture and to a piece of furniture. Rotary fittings for movable parts of furniture comprises at least one first lever installed around the drive shaft with the possibility of rotation from the initial position through a given angle relative to it, and a clamping mechanism configured to lock the first lever in different angular positions. Clamping mechanism comprises a toothed annular disc mounted on a drive shaft and having an external gear structure, and a latch pivotally mounted on the first lever and loaded in the direction of the outer gear structure. Latch is engaged with outer gear structure in locking position. Clamping mechanism further comprises a first control disc, which is installed with possibility of rotation around the drive shaft and configured to disengage the retainer from the outer gear structure in the adjustment direction, and at least one friction disc mounted on the drive shaft with rotation and axial fixation. Friction disc is fitted on toothed annular disc. Toothed annular disc is retained by friction closure on at least one friction disc until preset torque appears against rotation around axis of rotation.

EFFECT: providing simple protection of rotary fittings against overload.

19 cl, 28 dwg

Description

The present invention relates to rotary fittings, in particular to movable furniture parts on sitting or sleeping furniture according to the restrictive part of claim 1 of the claims, and to a piece of furniture.

Similar rotary fittings are known, for example, from DE 102017110253 A1. In this hinged fitting, two arms can be fixed relative to each other by means of a clamping mechanism. One of the levers can be attached to the base of the body or seating part of the upholstered furniture, and the second lever is used to fix a rotatably mounted headrest, armrest, footrest or other part of the furniture mounted with the possibility of rotation on the body of the base or seated part of the piece of furniture.

With the help of rotary fittings, the rotating part of the furniture can be rotated from its original position to a specified rotation position and fixed in this rotation position.

Pivot fittings are designed in such a way that the piece of furniture to be adjusted can be moved from any pivot position without having to first rotate the two levers to their original position.

Such rotary fittings have proven themselves well in practice.

The problem with such rotary fittings is that if the rotary fittings are overloaded, damage to the rotary fittings or part of the furniture may occur.

To prevent such damage, a solution is known, for example from DE 102017110248 A1, in which a safety clutch is installed between the two arms of the articulation joint, which is arranged structurally between the first arm and the second arm.

The disadvantage is that such safety couplings are relatively expensive to manufacture. Another disadvantage is that the safety clutch must be closed again at the point where it was opened, or at least can be closed again at an offset pitch.

The present invention is directed to further development of the general type of rotary fittings so as to also provide simple and inexpensive overload protection of the rotary fittings.

Another object of the invention is to provide a piece of furniture that further improves the operation of the piece of furniture with movable components.

The first problem is solved by rotary fittings having the features of paragraph 1 of the claims. The second problem is solved by a piece of furniture that has the features of paragraph 12 of the claims.

The rotary fittings according to the invention contain at least one first lever, which is mounted with the possibility of rotation around the drive shaft, which serves as the axis of rotation, from the initial position to a predetermined angle relative to it.

The rotary fittings include a clamping mechanism for locking the first arm in various angular positions within a specified angle relative to the drive shaft.

This clamping mechanism has a toothed ring disk mounted on a drive shaft with an outer tooth structure formed on an outer edge, and a latch that is pivotally mounted on a first lever, loaded in the direction of the outer tooth structure and engaged with the outer tooth structure of the toothed ring disk in locking position.

The clamping mechanism further includes a first control disk that is rotatably mounted about the drive shaft and by means of which at least one latch can be released from the gear mesh in the adjustment direction after passing a predetermined angle from the normal position, so that when the latch is disengaged from the gear mesh engagement, the first lever can be rotated back to its normal position relative to the drive shaft, passing a predetermined angle in the opposite direction.

At least one friction disk is mounted on the toothed annular disk, mounted on the drive shaft with rotational fixation and axial fastening, while the toothed annular disk is held on at least one friction disk by frictional closure until a given torque (M) appears against rotation around the axis rotation.

The rotary fittings configured in this manner provide an overload protection device that is easy to install and has inexpensive components that allow the drive shaft to be disconnected from the toothed ring disk so that in the event of an overload, the drive shaft is disconnected from the first arm.

This allows the first lever to be rotated relative to the drive shaft without damaging the clamping mechanism.

When the overload is reduced again, the rotary fittings according to the invention will again be fully functional.

Preferred embodiments of the invention are the subject of the dependent claims.

According to a preferred embodiment of the invention, the inner circumferential edge of the toothed annular disk has a conical shape and slides along a cone mounted on the drive shaft.

In this case, at least one friction disk is pressed in contact with the toothed annular disk on the smaller diameter side of the inner circumferential edge of the toothed annular disk.

Thanks to a cone located on the drive shaft and the friction disc, the friction disc located on the rotationally locked drive shaft and the toothed annular disc are pressed against each other so that a predetermined torque, which determines the overload limit, must be exceeded in order for the friction the disk rotated relative to the toothed annular disk.

Friction is created on the cone and on the contact surface of the toothed annular disk by the elastic contact force of the friction disk.

A certain torque can be set depending on the selected contact pressure or amount of friction between the contact surface of the toothed ring suit on the friction disc, as well as a certain cone angle.

According to a preferred further development of the invention, the cone is formed as one piece with the drive shaft, which allows for extremely simple assembly.

According to an alternative embodiment, the cone is mounted on the drive shaft.

This means low production costs for the drive shaft itself and the cone, which is manufactured as a separate component, for example as a sheet metal element.

According to a preferred further development, the cone is designed as a radially slotted clamping ring.

According to a preferred embodiment, the cone angle is between 15° and 35°, particularly preferably between 20° and 30°.

According to an alternative embodiment, the friction disc is mounted on both sides of the toothed annular disc with rotational locking and axial locking.

Accordingly, this option does not require a cone on the drive shaft.

According to an alternative embodiment, a plurality of toothed annular disks are disposed on the drive shaft, and a friction disk is located between the two toothed annular disks and is held non-rotably on the drive shaft.

It is preferable to use three toothed ring discs and two friction discs located between them.

An alternative embodiment uses two toothed annular discs with a friction disc located between them.

As a result of the force exerted by the friction discs mounted and/or pressed against the drive shaft in a rotationally locked manner, friction occurs at six contact points (in the case of three toothed ring discs) or four contact points (in the case of two toothed ring discs), by means of whereby the torque provided for overload protection can be adjusted.

Wear and overload torque can be easily adjusted by the spring and pressure force of the friction discs used, as well as the number of toothed ring discs used.

According to another preferred embodiment, a tongue is provided, which is formed integrally on the first control disk and which extends perpendicular to the plane of the first control disk in an axial direction outward relative to the drive shaft, into a recess provided for this purpose in the cutout of the first lever.

According to another embodiment, a recess is provided on the outer edge of the friction disc, in which the switching element is located so that it can be rotated by a switching angle in the plane of the friction disc.

This switching element also serves as an alternative to the combination of the control pin located on the first lever and the cutout in the first control disk.

The friction disk on which the switching element is mounted has a thickness in the axial direction of the drive shaft that is greater than the thickness of the switching element.

This is a simple way to ensure that the forces applied by the friction discs cannot cause the switching element to become pinched.

According to a preferred embodiment, at least one friction disc is fitted with an interference fit on the drive shaft against the toothed annular disc.

This makes it possible to create sufficient friction between the friction disc and the toothed ring disc by means of only one friction disc.

According to another preferred embodiment, the friction disc is designed as a disc spring.

According to another preferred embodiment, a switching circuit is formed on the outer edge of the friction disc.

According to another preferred development, the predetermined torque up to which the toothed annular disk is kept from rotating about the axis by the frictional engagement of the at least one friction disk is at least 70 N⋅m, preferably at least 80 N⋅m.

This ensures that at lower loads, where there is no risk of damage to the rotary fittings, the clamping mechanism does not respond to lower torques, so that the arms maintain their position and can only be adjusted relative to each other at a given torque, without using the actual function of the clamping mechanism .

A particular advantage of the device according to the invention is that the rotary fittings allow a maximum adjustment angle of approximately 250°. This is made possible by the specified configuration of control fingers and stops, as well as the internal structure with a toothed ring disk, control disk and latch.

According to one embodiment, the second lever is pivotally coupled to the drive shaft.

The piece of furniture according to the invention is characterized by the rotary fittings described above.

According to one embodiment, the second arm is part of an adjustable portion of the furniture.

Preferred embodiments are disclosed in more detail below with reference to the accompanying drawings, in which:

fig. 1 is a top view of an embodiment of a rotary fitting according to the invention,

fig. 2 is an exploded perspective view of the rotary fitting without showing the second lever,

fig. 3 is a separate perspective view of the toothed annular disc, the drive shaft, the friction disc, the cone and the first control disc,

fig. 4 is a partial cross-section of the drive shaft with the overload protection components located on it,

fig. 5 is an exploded view of an embodiment of a toothed annular disk, a cone and a drive shaft,

fig. 6 is a perspective view of the components of FIG. 5 assembled,

fig. 7 is a perspective view of an alternative embodiment of a friction disc mounted on a drive shaft,

fig. 8 shows a top view of the rotary fittings with a stop,

fig. 9 shows a rotary fitting corresponding to FIG. 8, in another rotating position,

fig. 10 represents a cross-section of the rotary fittings,

fig. 11 and 12 show top views of the rotary fittings with alternatively designed stops on the second lever,

fig. 13 is a side view of an alternative overload protection design,

fig. 14-19 are top views of the rotary fittings without showing the lever head to illustrate the functional sequence of the rotary and switching movements,

fig. 20 is an exploded perspective view of an alternative embodiment of an overload-protected clamping mechanism with three toothed ring disks and friction disks located between them.

fig. 21 is a side view of an embodiment of the structure of FIG. 20,

fig. 22 is an exploded perspective view of another alternative embodiment of an overload-protected clamping mechanism with two toothed ring discs and friction discs located between them.

fig. 23 is a side view of an embodiment of the structure of FIG. 22,

fig. 24 is an exploded perspective view of another alternative embodiment of an overload-protected clamping mechanism with three toothed annular discs and friction discs located between them, and an alternative switching element,

fig. 25 is a side view of an embodiment of the structure of FIG. 24,

fig. 26 is a schematic top view of an embodiment of the structure of FIG. 24 to illustrate the arrangement of the switching element, and

fig. 27 and 28 are schematic illustrations of a piece of furniture with a rotating piece of furniture mounted thereon.

In the following description of the figures, terms such as “top”, “bottom”, “left”, “right”, “front”, “rear”, etc. refer solely to the presented examples of the arrangement of the rotary fittings, lever, toothed ring disk, latch, drive shaft, cone, friction disk, etc., selected for the corresponding figures. These terms are not to be understood in a restrictive manner and these instructions may vary for other operating positions, mirror symmetrical designs, etc.

In fig. 1, position 1 indicates an embodiment of a rotary fitting according to the invention.

Such rotating fittings 1 serve, in particular, to enable the rotation of movable furniture parts on pieces of furniture, such as, for example, an armrest 103 or a backrest 102, a headrest or a footrest of a piece of furniture 100 designed as sitting or sleeping furniture as shown in as an example in Fig. 27 and 28.

As shown in FIG. 1, in the embodiment shown here, the rotary fitting 1 has a first lever 2 and a second lever 3. The two levers 2, 3 are rotatable relative to each other about a rotation axis D from a home position to a predetermined angle in an adjustment direction V and a return direction R.

The clamping mechanism of the rotary fittings 1, here located between the two heads 23a and 23b of the first lever 2, is designed in such a way that the two levers 2, 3 can be fixed in different angular positions within a given angle relative to each other against a torque acting in the opposite direction R, and can be rotated in the opposite direction R when the clamping mechanism is deactivated.

This makes it possible, for example, to adjust the armrest 103 of a piece of furniture 100, in which the armrest 103 is connected to the second lever 3 while the first lever 2 is connected to the furniture body 101 to rotate the armrest 103 to a position convenient for the user and fix it in desired position.

As shown in FIG. 2 and 3, the clamping mechanism includes a drive shaft 6 connected to a second lever 3 with rotational locking.

A toothed ring disk 4 having an outer tooth structure 41 formed on an outer edge is placed on this drive shaft 6.

There is also a design for rotary fittings 1 without a second lever 3.

The clamping mechanism operates between the lever 2 and the drive shaft 6, which allows you to adjust the angle between the lever 2 and the drive shaft 6.

If the rotary fitting 1 comprises a second lever 3 mounted on a drive shaft 6, the clamping mechanism thus also allows the angle between the first lever 2 and the second lever 3 to be adjusted.

It should be particularly noted that the second lever 3 can also be part of a piece of furniture placed directly on the drive shaft 6.

Therefore, the shape of the lever 3 may differ significantly from the flat and elongated shape shown in the figures, for example, the use of tubes, in particular rectangular or square tubes, is also envisaged.

Here, the latch 5, loaded by the spring element 10 in the direction of this outer gear structure 41 of the gear ring 4 of the disk 4, is rotatably mounted on the first lever 2. Thus, the latch 5 engages with this outer gear structure 41 in the locked position.

In addition, the clamping mechanism includes a first control disk 7, which is rotatably mounted about a common axis D and by means of which the latch 5 can be disengaged from the outer gear structure 41 of the toothed annular disk 4 after passing a predetermined angle from the initial position in the adjustment direction V.

In this disengagement position, the second lever 3 can be rotated back to its original position relative to the first lever 2, passing a predetermined angle in the opposite direction R.

As shown in FIG. 2-4, at least one friction disk 8, which slides onto the drive shaft 6 with rotational and axial fixation, is put on the toothed annular disk 4.

The toothed annular disk 4 is held by friction on at least one friction disk 8 from rotation around axis D until a given torque M appears.

Frictionally holding the toothed annular disk 4 relative to the drive shaft 6 until a predetermined torque M appears is thus an economical means of overload protection for such rotary fittings 1, which is cheaper compared to overload protection in the form of a separate structural unit.

As shown in FIG. 3-5, according to a preferred embodiment, the inner circumferential edge 42 of the toothed annular disk 4 slides onto a cone 9 located on the drive shaft 6 in a conical shape. In this case, at least one friction disk 8 is pressed into contact with the toothed annular disk on the smaller diameter side of the inner annular edge of the toothed annular disk.

In one embodiment, the cone 9 can be formed as a single unit directly on the drive shaft 6.

According to an alternative embodiment, the cone 9 is mounted on the drive shaft 6.

In particular, the cone 9 is made in the form of a radially slotted clamping ring, as shown in Fig. 5. The shown cone 9 has an inner gear diameter 92 for rotationally locking mounting on a drive shaft 6 provided with an outer gear structure 61.

The outer circumferential edge 91 of the cone 9 has a conical shape.

To facilitate the application of the cone 9 on the drive shaft 6, the cone 9 shown in FIG. 5 is formed with a slot 93. When the friction disc 8 is pressed against the cone 9, the inner gear structure of the cone 9 is pressed against the outer gear structure of the drive shaft 6, so that the cone 9 is axially clamped on the drive shaft 6.

The cone angle of the outer circumferential edge 91 of the cone 9 is preferably from 15° to 35°. It is particularly preferred that the cone angle is between 20° and 30°.

The friction disk 8 is preferably mounted with an interference fit on the drive shaft 6 against the toothed annular disk 4.

Alternatively, other axial fixations of the friction disc 8 are possible, for example by applying a weld, a nut, or the like.

As an alternative to installing the toothed annular disk 4 by means of a cone 9 as shown in FIG. 3-5, it is also possible to provide for such a friction disc 8 to be placed on the drive shaft 6 on both sides of the toothed annular disc 4.

This also makes it possible to obtain sufficiently large friction between the friction discs 8 and the toothed ring disc 4 to provide an overload protection function.

As also shown in FIG. 3, at least one friction disc 8 is preferably made in the form of a disc spring.

The predetermined torque M, up to which the toothed annular disk 4 is held by friction against rotation about the axis D by at least one friction disk 8, is preferably at least 70 N⋅m, particularly preferably at least 80 N⋅m.

As also shown in FIG. 3, the first control disk 7 is placed on the drive shaft 6 on the side of the toothed annular disk 4 facing away from the friction disk 8.

The first control disk 7 can be rotated relative to the transmission shaft 6 and is secured in the axial direction by a spring element 13 in the form of a disc spring.

Thus, the spring element 13 is protected against rotation by teeth 132 on the inner circumference 131 of the spring element 13 on the drive shaft 6.

As shown in FIG. 2, the second control disk 11 is located on the side of the friction disk 8 facing away from the toothed ring disk 4 on the drive shaft 6. The second control disk 11 has a shift lever 111 and an elongated hole 112. A single tooth 113 engages the outer gear structure of the drive shaft 6 .

It is also possible, instead of the second control disk 11, to form on the friction disk 8 a switching circuit 82, which extends radially outward from the circumferential edge of the friction disk 8 at a predetermined angle, as shown in FIG. 7.

The latch 5 has a plurality of teeth 52 at the first end of the latch tab 51 that engage the outer tooth structure 41 of the toothed ring disk 4.

At the opposite end of the gripping jaw 51, rotating pins 53 protrude from both sides, with which the latch is secured in rotation, for rotating the sockets 27 of the heads 23 of the levers of the first cover 2a and the second cover 2b.

On the side of the gripper jaw 51 facing the outer tooth structure 41 of the toothed annular disk 4 in the assembled position, a recess 54 is formed between the teeth 52 and the hinge pin 53 to accommodate the switching circuit 71 of the first control disk 7.

To limit the angle of rotation between the two levers 2, 3, the control fingers 12 are fixed or integrally formed on the covers 2a, 2b of the first lever 2, which in the embodiment shown in FIG. 8 and 9 strike in their respective end positions the thrust edges of the disk-shaped stop 15, while the disk stop 15 is connected in a rotationally locking manner to the second lever 3 or the drive shaft 6.

In an alternative embodiment, these stops are formed by side stops 34 on the second arm 3, as shown in FIG. 11 and 12.

The operation of the rotary fitting 1 in normal operation is described below with reference to FIG. 14-19.

In fig. 14 shows the approximate position of the rotary fitting 1, which is already slightly rotated in the adjustment direction V, in which the latch 5 engages with the outer tooth structure 41 of the toothed ring disk 4.

In fig. 15 shows the position of the rotary fittings 1, turned further in the adjustment direction V.

Here, the retainer 5 is always pressed against the outer tooth structure 41 of the toothed annular disk 4 by a spring element 10, which has the shape of a spring plate. The alignment of the outer tooth structure 41 of the toothed ring disk 4 and the teeth 52 of the latch 5 is such that, in the adjustment direction V, the latch 5 can move tooth by tooth along the outer tooth structure 41 of the toothed ring disk 4.

In the position shown in FIG. 16, the shift lever 111 of the second control disk 11 has reached the outermost tooth of the locking gear 5.

In this case, the outer tooth 52 is made with an input bevel 55. As a result, with further rotation of the drive shaft 6 and, consequently, the second lever 3 in the adjustment direction V, the switching lever 111 can slide onto the outer teeth 52 of the latch 5, so that the teeth 52 of the latch 5 disengage with the outer tooth structure 41 of the toothed annular disk 4, as shown in FIG. 17.

As also shown by the dotted lines in FIG. 17, in this position, the switching circuit 71 of the first control disk 7 engages with the recess 54 of the latch 5.

In this case, the control finger 12 rests against the recess 72 of the first control disk 7 on the right edge of the recess 72.

If the second lever 3 or the drive shaft 6 now moves in the opposite direction, that is, in the opposite direction R, this causes the second control disk 11 to rotate around the shift lever 111 currently attached to the teeth 52 of the gripper 5 by engaging the control tooth 113 on the inner circumference of the second control disk 11 by the force of the drive shaft 6 in the elongated hole 112 in the center of the second control disk 11.

At the same time, during this reverse rotation of the drive shaft 6, the control pin 12 reaches the left edge of the recess 72 of the first control disk 7.

During subsequent further rotation of the drive shaft 6 in the reverse direction R, the switching circuit 71 of the first control disk 7 slides onto the tooth-free plane of the tab 51 of the latch 5, so that the teeth 52 of the latch 5 remain out of engagement with the outer gear structure 41 of the toothed ring disk 4, and the rotary fitting 1 can thus be rotated back to its original position.

In the event of an overload acting on the rotary fittings 1, the overload protection functions in such a way that in any position of rotation of the levers 2, 3 of the rotary fittings 1 relative to each other, the torque M caused by the friction between the friction disk 8 and the toothed annular disk 4, the toothed annular disk 4 begins to slide relative to the friction disk 8 around the axis of rotation D, so that the two levers 2, 3 can rotate relative to each other as long as the force acting on the levers is greater than the specified torque M.

If the force applied to the levers decreases and falls below a predetermined torque M, the frictional engagement between the friction disk 8 and the toothed ring disk 4 is restored, and the normal functioning of the rotary fittings 1 is resumed.

In alternative embodiments of the rotary fittings according to the invention shown in FIGS. 20-26, the clamping mechanism has a plurality of toothed ring disks 202, 302 arranged side by side on the drive shaft, instead of a single toothed ring disk 4.

A friction disc 203, 303, 304, which is rotationally supported on the drive shaft 6, is located between each of two such toothed annular discs 202, 302.

In the embodiment shown in FIG. 20 and 21, three such toothed annular disks 202 are provided.

Each of these toothed annular disks 202, 302 has an annular inner circumferential edge 221, 321 and an outer toothed structure 222, 322 into which the latch 5 engages.

In both embodiments shown in FIGS. 20 and 21, as well as the variants shown in FIGS. 22 and 23 and figs. 24-26, the friction disks 8 abut the outer surfaces of the outer toothed ring disks 202, 302, pressing axially against the toothed ring disks 202, 302.

Similar to the embodiment shown in FIG. 13, the first control disk 201, 301 is put on the drive shaft 6 on the outer side of one of the friction disks 8.

This first control disk 201, 301 also has an annular inner circumferential edge 211.

From the outer circumferential edge, identical to the embodiment shown in FIG. 3, there is a switch circuit 212, which serves the same purpose as the switch circuit 71 of the first control disk 7 according to the embodiment shown in FIG. 3.

Unlike the embodiment shown in FIG. 3, here, on the opposite circumferential edge of the first control disk 201, a tongue 213 is formed, which extends perpendicular to the plane of the control disk 201 in the direction of a spring element 13 like a disc spring on the side of the first control disk 201 facing away from the toothed annular disks 202.

In the installed state, this tongue 213 projects into a recess provided for this purpose on the first lever 2, which in this case has a recess in the form of an oblong hole instead of a control pin 12, in which the tongue 213 can be rotated by a switching angle in the circumferential direction of the first control disk 201 .

Similar to the friction disc 8 shown in FIG. 7, the friction discs 203 located between the toothed annular discs 202 have a switching circuit 232 extending radially outward from the outer circumference of the friction discs 203.

The friction discs 203 further include an inner circumferential edge with an internal tooth structure 231 similar to the friction discs 8.

Unlike the embodiment of FIG. 20 and 21, in which three toothed annular discs 202 are provided with two superimposed friction discs 203, in the embodiment shown in FIG. 22 and 23, the two toothed annular disks 202 are provided with one intermediate friction disk 203. Otherwise, the design of the clamping mechanism of these two embodiments is identical.

An embodiment of yet another alternative clamping mechanism shown in FIG. 24-26 preferably includes three toothed annular disks 302, similar to the embodiment shown in FIG. 20 and 21, having a corresponding friction disk 303, 304 located between two toothed annular disks 302.

Unlike the embodiments described with reference to FIGS. 20-23, in this embodiment, one of the friction discs 304 has a raised portion 343 on its outer circumference 342, which is adjacent to a recess 344 for receiving the switching element 305.

In this way, the switching element 305 is adapted to the inner contour of the recess 344 so that it can be rotated to a predetermined switching angle inside the recess 344 about a rotation axis that is coaxial to the rotation axis of the drive shaft 6, but radially offset outward from the drive shaft 6, which also clearly visible in Fig. 26.

In this regard, the recess 344 has a substantially V-shaped receiving area for receiving a V-shaped section of a portion of the switching element 305.

In this regard, the neck of the switching element 305 has a circumferential width from which it can rotate within the recess 344 to a predetermined switching angle.

The switching angle is preferably between 8° and 12°. The thickness of this switching element 305, when viewed in the longitudinal direction of the drive shaft 6, is thus less than the thickness of the friction disc 304.

In the embodiment shown here, the friction disc 304 is greater than the thickness of the friction disc 303.

The slightly thinner thickness of the switching element 305 compared to the friction disc 304 makes it possible by simple means to prevent the switching element 305 from being pinched by the friction discs 8 pressing against the toothed annular discs 302 from the outside.

LIST OF REFERENCE SYMBOLS

1 swivel fitting

2 first lever

2a first cover

2b second cover

21 lever arms

22 bend section

23a lever head

23b lever head

24 drilled hole

25 socket

26 drilled hole

27 rotary pin socket

3 second lever

31 lever arms

32 lever head

33 drilled hole

34 emphasis

4 tooth ring disc

41 external gear structure

42 inner circumferential edge

5 latch

51 latch levers

52 teeth

53 pivot pin

54 socket

55 input bevel

6 drive shaft

61 external gear structure

62 groove

7 first control disk

71 switching circuits

72 recess

8 friction disc

81 internal gear structure

82 switching circuit

9 cone

91 outer circumferential edges

92 internal tooth structure

93 slot

10 spring element

101 spring steel strip

102 tooth

11 second control disk

111 switch foot

112 extended hole

113 tooth

12 control finger

13 spring element

131 inner circle

132 tooth

14 disc

15 emphasis

151 stop edges

100 piece of furniture

161 furniture units

162 back

163 armrest

201 first control disk

211 inner diameter

212 switching circuit

213 tongue

202 tooth ring disc

221 inner circumferential edges

222 external gear structure

203 friction disc

231 internal gear structure

232 switching circuit

301 first control disk

311 inner diameter

312 switching circuit

313 corner area

314 recess

302 tooth ring disc

321 inner circumferential edge

322 external gear structure

303 friction disc

331 internal gear structure

304 friction disc

341 internal gear structure

342 outer circle

343 height

344 recess

305 switch element D rotation axis

V adjustment direction

R reverse direction

α maximum adjustment angle

M torque

d _R friction disc thickness

d _U thickness of the switching element.

Claims (27)

1. Rotary fittings (1) for moving parts of furniture, containing - at least one first lever (2) installed around the drive shaft (6), which serves as an axis (D) of rotation, with the possibility of rotation from the initial position to a specified angle relative to it, - a clamping mechanism configured to fix the first lever (2) in various angular positions within a given angle relative to the drive shaft (6), the clamping mechanism contains: a. a toothed annular disk (4, 202, 302) mounted on the drive shaft (6) and having an outer tooth structure (41, 222, 322) formed integrally on the outer edge, b. a latch (5) pivotally mounted on the first lever (2) and loaded in the direction of the outer gear structure (41, 222, 322), wherein the latch (5) engages the outer gear structure (41, 222, 322) in locking position c. a first control disk (7, 201, 301) that is rotatably mounted around the drive shaft (6) and configured to disengage the lock (5) from the outer gear structure (41, 222, 322) in direction (V) adjustment after a predetermined angle has been passed from the original position, so that when the latch (5) is disengaged from the outer gear structure (41, 222, 322), the first lever (2) rotates back to its original position relative to the drive shaft (6 ), with the passage of a given angle (α) in the opposite direction (R), characterized in that - at least one friction disk (8, 203, 303, 304), installed on the drive shaft (6) with rotational fixation and axial fastening, is mounted on a toothed annular disk (4, 202, 302), and the toothed annular disk ( 4, 202, 302) is held by frictional closure on at least one friction disk (8, 203, 303, 304) until a predetermined torque (M) appears against rotation around the rotation axis (D). 2. Rotary fittings according to claim 1, characterized in that the inner circumferential edge (42) of the toothed annular disk (4) is mounted conically on a cone (9) located on the drive shaft (6), and at least one friction disk (8 ) is pressed against the toothed annular disk (4) on the side of the smaller diameter of the inner circumferential edge (42) of the toothed annular disk (4). 3. Rotary fittings according to claim 2, characterized in that the cone (9) is made as one piece with the drive shaft (6). 4. Rotary fittings according to claim 2, characterized in that the cone (9) is installed on the drive shaft (6). 5. Rotary fittings according to claim 4, characterized in that the cone (9) is made in the form of a radially slotted clamping ring. 6. Rotary fittings according to one of paragraphs. 2-5, characterized in that the cone angle of the cone (9) ranges from 15° to 35°. 7. Rotary fittings according to claim 1, characterized in that the friction disk (8, 203, 303, 304), installed with rotational fixation and axial fastening, is mounted on both sides of the toothed annular disk (4, 202, 302). 8. Rotary fittings according to claim 1 or 7, characterized in that up to three toothed annular disks (202, 302) are installed on the drive shaft (6), with a friction disk (203) located between the two toothed annular disks (202, 302) , 303, 304), held in rotational locks on the drive shaft (6). 9. Rotary fittings according to one of the previous paragraphs, characterized in that at least one friction disk (8) is fitted with an interference fit on the drive shaft (6) against the toothed annular disk (4). 10. Rotary fittings according to one of the previous paragraphs, characterized in that at least one friction disk (8) is made in the form of a disc spring. 11. Rotary fittings according to one of the previous paragraphs, characterized in that a switching circuit (82) is formed on the outer edge of the friction disk (8, 203). 12. Rotary fittings according to one of paragraphs. 1-10, characterized in that a recess (344) is provided, which is made as one piece on the outer edge of the friction disk (304), and in which the switching element (305) is located with the ability to rotate at a switching angle in the plane of the friction disk (304) . 13. Rotary fittings according to claim 12, characterized in that the thickness d _R of the friction disc (304), measured in the longitudinal direction of the drive shaft (6), is greater than the thickness d _U of the switching element (305). 14. Rotary fittings according to one of the previous paragraphs, characterized in that a given torque (M), before the appearance of which the rotation of the toothed annular disk (4) around the axis (D) is prevented by frictional closure of at least one friction disk (8), is at least 70 N⋅m. 15. Rotary fittings according to one of paragraphs. 1-13, characterized in that the predetermined torque (M), until the appearance of which the rotation of the toothed annular disk (4) around the axis (D) is prevented by frictional closure of at least one friction disk (8), is at least 80 N ⋅m. 16. Rotary fittings according to one of the previous paragraphs, characterized in that the second lever (3) is connected with rotational locking to the drive shaft (6). 17. A piece of furniture (100) containing rotary fittings (1) according to one of the preceding paragraphs. 18. A piece of furniture (100) according to claim 17, characterized in that the rotary fittings (1) adjustably fix the armrest (163) or other adjustable parts of the furniture on the body (161) of the piece of furniture (100), designed as sitting or sleeping furniture . 19. A piece of furniture (100) according to claim 17 or 18, characterized in that the second lever (3) is part of an adjustable part of the furniture.