EP1875027B1 - Hinge device - Google Patents

Description

The invention relates to a hinge arrangement, in particular a refrigerator housing with a hinged thereto via a hinge hinged refrigerator door.

From the DE 203 06 043 U1 is a stop damper for a refrigerator door known. When opening the refrigerator door, however, the door is no longer connected to the damper from a certain opening angle. The door can thus strike in the open state, for example, to an adjacent wall. In the opposite case occurs when closing the door only from a certain closing angle, the door with the damper in combination. Since the weight of refrigerator doors is highly fluctuating, the known damping is unsatisfactory.

Other hinge arrangements are for example from the DE 202 07 036 U1 , of the DE 102 37 148 A1 and from the US 2003/0229965 A1 known.

The invention has for its object to provide a hinge assembly in which the disadvantages of the prior art are overcome.

The object is solved by the features of claim 1. The essence of the invention is to dampen the pivotal movement of two hinged parts made possible by means of a hinge in such a way that a piston-cylinder damping unit is provided which is articulated directly at least at one part. The damping characteristics of piston-cylinder damping unit is much better adjustable such as those of coil springs, which are often used in hinges.

The hinge is designed as a multi-joint hinge comprising two four-point joints, which are each hinged by means of a fitting on one of the two parts. The two four-point joints have a common central hinge arm, on which via a mounting arm, the piston-cylinder damping unit is articulated. As a result, the one part can be guided through a dead center during an opening movement, so that the first part is in stable end positions both in an opening position and in a closed position. The attachment of the piston-cylinder damping unit via the mounting arm to the central hinge arm can be done, for example, subsequently, in which the mounting arm is attachable to an existing hinge. In a special design of the mounting arm this does not protrude beyond the hinge.

Further advantageous embodiments of the invention will become apparent from the dependent claims.

Fig. 1

eine Ansicht einer Scharnier-Anordnung gemäß einer nicht erfindungsgemäßen Ausführungsform mit einer Kolben-Zylinder-Dämpfungs-Einheit,

Fig. 2

einen Mittel-Längs-Schnitt der Kolben-Zylinder-Dämpfungs-Einheit gemäß Fig. 1,

Fig. 3

Kraft-Geschwindigkeits-Kennlinien der Kolben-Zylinder-Dämpfungs-Einheit gemäß Fig. 2 für zwei verschiedene Kolbenpositionen,

Fig. 4

Kraft-Einschub-Kennlinie der Kolben-Zylinder-Dämpfungs-Einheit gemäß Fig. 2 bei konstanter Einschub-Geschwindigkeit,

Fig. 5

eine Scharnier-Anordnung gemäß einer nicht erfindungsgemäßen Ausführungsform in einer Mittelposition,

Fig. 6

einen Schnitt gemäß der Schnittlinie VI-VI in Fig. 5,

Fig. 7

die Scharnier-Anordnung gemäß Fig. 5 in einer Schließ-Position,

Fig. 8

die Scharnier-Anordnung gemäß Fig. 5 in einer Öffnungs-Position,

Fig. 9

eine Scharnier-Anordnung gemäß einem Ausführungsbeispiel gemäß der Erfindung in einer Mittelposition und

Fig. 10

eine Scharnier-Anordnung gemäß einer nicht erfindungsgemäßen Ausführungsform in einer Mittelposition.

Additional features and details of the invention will become apparent from the description of several embodiments with reference to the drawings. Show it:

Fig. 1

1 is a view of a hinge arrangement according to a non-inventive embodiment with a piston-cylinder damping unit,

Fig. 2

a central longitudinal section of the piston-cylinder damping unit according to Fig. 1 .

Fig. 3

Force-velocity characteristics of the piston-cylinder damping unit according to Fig. 2 for two different piston positions,

Fig. 4

Force-insertion characteristic of the piston-cylinder damping unit according to Fig. 2 at constant insertion speed,

Fig. 5

a hinge arrangement according to a non-inventive embodiment in a central position,

Fig. 6

a section along the section line VI-VI in Fig. 5 .

Fig. 7

the hinge arrangement according to Fig. 5 in a closed position,

Fig. 8

the hinge arrangement according to Fig. 5 in an open position,

Fig. 9

a hinge assembly according to an embodiment of the invention in a central position and

Fig. 10

a hinge assembly according to a non-inventive embodiment in a central position.

The following is with reference to the Fig. 1 to 4 a non-inventive embodiment described. In a hinge arrangement 1 is a first part, a refrigerator door 2, articulated via hinges 3 to a second part, only partially shown, a refrigerator housing 4, pivotally. The hinge 3 has a vertical pivot axis 5. In practice, a plurality of hinges 3 are often arranged one above the other, at least at the upper and lower edges of the refrigerator door 2, which have a common pivot axis 5.

For damping the opening and closing movement of the refrigerator door 2, a damper 6, also referred to as a piston-cylinder damping unit, is provided. This has a substantially cylindrical housing 7, which is closed at one end with an integrally formed with the housing 7 bottom 8. At this bottom 8, a fastening element 9 is formed, which is provided with a bore 10, whose axis 11 is perpendicular to the central longitudinal axis 12 of the housing 7 and this intersects. On the inner side 13 of the refrigerator door 2, a hinge element 14 is fixed with a corresponding bore, wherein the fastening element 9 is pivotally connected to the hinge element 14 by inserting a bolt 15.

The housing 7 has a likewise cylindrical interior 16, which is concentric with the axis 12 and is closed at one end by the bottom 8. The interior 16 is bounded in the radial direction by the inner wall 17 of the housing 7. At its other end, the housing 7 has an opening 18 open to the outside. Also concentric with the axis 12, a piston rod 19 is slidably disposed in the interior 16 in the direction of the axis 12, whose one end 20 protrudes from the housing 7 through the opening 18. At this end 20, a further fastening element 21 is attached, which also has a bore 22, whose axis 23 is perpendicular to the central longitudinal axis 12 and this cuts. On the refrigerator housing 4, an associated articulation element 24 is fixed with a corresponding bore, wherein the fastening element 21 is pivotally connected by insertion of a bolt 25 with the articulation element 24. The distance of the articulation element 24 from the pivot axis 5 is denoted by a. The distance of the articulation element 14 from the pivot axis 5 is denoted by b. The fixed articulation of the damper 6 on the door 2 on the one hand and on the housing 4 on the other hand takes place so that the damper 6 protrudes as little as possible from the door 2 in the direction of the enclosed space, b is thus greater than a. The damper 6 can be arranged at the upper edge and at the lower edge of the door 2.

The following is with reference to Fig. 2 the structure of the damper 6 explained in more detail. The damper 6 has an extension direction 26 extending parallel to the central longitudinal axis 12. In the region of the end 26 lying in the direction of the interior 16, a guide / seal bushing 27 is fixed in the housing 7, through which the piston rod 19 is displaceably guided to the outside. The bush 27 is surrounded in the radial direction and in the direction 26 by the housing 7 and fixed by this. It is seated in an annular wall 28 arranged in the inner wall 17, whereby the bushing 27 is also fixed counter to the direction 26. Between the opposite end 26 of the bushing 27 and the bottom 8, a working space 29 is formed. In the working space 29 is a on the inner wall 17 sealingly abutting, along the axis 12 displaceable piston 30 which is fixed to the housing-side end of the piston rod 19. The piston 30 divides the working chamber 29 into a part of the working space 31 facing the bottom 8 and a part of the working chamber 32 facing the bush 27. The working space 29 is largely, but not completely, filled with a damping fluid 33, in particular oil. The level is indicated by the reference numeral 34. Above the oil level 34 is a gas 35, in particular air.

The piston 30 has distributed over its circumference, this along the direction 26 penetrating damping holes 36 which connect the two part-working spaces 31 and 32 with each other. The damping holes 36 are partially closed by valves 37 which are open in a movement in the direction 26 and are closed in a direction opposite to the direction 26. Between the piston 30 and the bushing 27 designed as a spiral spring, the piston rod 19 concentrically surrounding return spring 38 is arranged. This is biased so that it pushes the piston 30 against the direction 26 in retracted piston rod 19 back into the housing 7. In the inner wall 17 a plurality of longitudinal grooves 39 are uniformly distributed over the circumference. In the area of these longitudinal grooves 39, the piston 30 is not tight against the inner wall 17. Rather, a channel 40 is formed between the piston 30 and the base 41 of the longitudinal groove 39. Starting from the bottom 8, there first exists a section 65 along which no longitudinal groove is provided. This is followed by a section 66, along which the cross section of the longitudinal groove 39 along the direction 26 increases constantly from zero. This is followed by a section 67, along which the longitudinal groove 39 has a substantially constant cross section. This is followed by a section 68, along which the cross-section of the longitudinal groove decreases to zero over a short length. This is followed by a section 69, along which no longitudinal groove is present. The effective in the discharge of the piston 30 in the direction 26 flow cross section of the bores 36 is substantially larger than the maximum cross section of all longitudinal grooves 39 in section 67, so that the bores 36 determine the flow resistance. In addition, the effective flow cross-section of the piston 30th counter to the direction 26 is substantially smaller than the flow cross-section of the piston during a movement in the direction 26, so that then the presence of the longitudinal grooves 39 plays a role.

Hereinafter, the characteristics of the damper 6 will be described with reference to FIGS Fig. 3 and 4 described. Fig. 3 shows the force-speed characteristic of the damper 6 for two different cases. The pull-out force F is shown as a function of the speed v. Two cases A and B are contrasted. A concerns the characteristic curve in which the piston 30 is located in the section in which the longitudinal grooves 39 are arranged. If the piston rod 19 is pulled out along the direction 26, the piston 30 shifts along the direction 26. The damping fluid 30 located in the partial working chamber 32 and the gas 35 located there are moved through the damping bores 36 into the partial working chamber 31 pressed. The damping behavior of the damper 6 is weak. The valves 37 are open. The speed dependence of the damping force is low and only slightly increases, which results from the speed dependence of the flow resistance. Characteristic curve B shows the damping force when the piston 30 is opposite to the direction 26 behind the end 42 of the longitudinal grooves 39, ie outside the groove 39. Now, the entire damping fluid 33 must be pressed through the still open damping holes 36. The damping force is thus much higher at the same speed, since the available for the fluid 33 cross section is much lower.

Fig. 4 shows the damping force of the damper 6 at a constant speed during insertion of the piston 30 counter to the direction 26. The x thus corresponds to a depth. The characteristic has a first plateau area C on, in which the damping force is large. This area corresponds to the part where the piston 30 is outside the longitudinal groove 39. The characteristic curve then has a region D which changes in a linear manner. This corresponds to the area where the cross section of the longitudinal grooves 39 changes continuously. The section D is followed by another plateau section E. This corresponds to the area where the longitudinal grooves 39 have their full constant cross-section.

The following describes the damping behavior of the refrigerator door 2 during opening and closing. It is assumed that the refrigerator door is initially closed. The piston rod 19 is in the inserted state. The piston 30 is near the bottom 8. The return spring 38 is in the most relaxed state compared to other states. The gas 35 is under ambient pressure. It is also possible to use pressurized gas 35. If the door is opened, the opening movement is only slightly damped, since the fluid 33 can flow through the comparatively large damping holes 36. The valves 37 are open. Opening the door is thus easy. The opening of the door may be assisted by the relaxing gas 35. In return, the return spring 38 is compressed. Due to the design of the holes 36 and the longitudinal grooves 39, the gas pressure 35 and the spring characteristic of the return spring 38, the damping behavior can be adjusted to different heavy refrigerator doors. In addition, it can be ensured that the damping behavior is substantially the same regardless of whether the refrigerator door is heavily loaded with bottles, for example, or not.

The closing movement of the door is supported by the now strongly compressed return spring 38. The design of the valves 37 can ensure that the damping when closing the door is greater than when opening the door. It should be ensured that the door does not touch the housing 4. This is also realized by the particular arrangement of the damper 6, since the damper 6 in the closed state of the door 2 is almost parallel to the front of the housing 4 and thus the torque generated by it is low. However, the return spring 38 also ensures that the door closes completely. The damping behavior of the piston 30 during insertion of the piston rod 19 is essentially determined by the presence or absence of the longitudinal grooves 39. The flow cross-section of the piston 30 is substantially less when pushed against the direction 26 than in the opposite direction. Because of this, the cross section through the longitudinal groove 39 plays an essential role. In the fully extended state, the piston 30 is located approximately as in FIG Fig. 2 shown, still at the height of section 67. The damping behavior is thus relatively small, but still greater than when pushing out of the piston in the direction 26 at the same height. When the piston 30 reaches the portion 66, the cross section of the longitudinal grooves 39 decreases and the damping force increases linearly. In section 65, the damping is maximal because the longitudinal grooves 39 are no longer present. It is thus prevented that the refrigerator door 2 abuts when closing on the housing 4. The damping by the effective during insertion holes 36 and the longitudinal grooves 39 is speed-dependent and grooved. The more the door is hit, the stronger the damping. A smooth and secure closing in different loading situations of the door 2 is thus always ensured. By the articulation of the damper 6 on the door 2 and the fact that b is much greater than a the damper 6 swung out when opening the door 2 from the operating and viewing area of the refrigerator housing 4. The damping forces of the damper 6 are, as already explained, in the closing and opening direction of the door 2 of different sizes. In the closing direction, the damping forces in terms of speed and closing angle are designed so that a smooth and secure closing of the door 2 are ensured in every loading situation. In the opening direction of the door 2, the damping is designed as low as possible.

The following is with reference to the Fig. 5 to 8 a non-inventive embodiment described. Identical parts are given the same reference numerals as in the embodiment according to FIG Fig. 1 to 4 , whose description is hereby referred to. Constructively different parts, but functionally similar parts receive the same reference numerals with a nachgeschlagen a. The key difference is that the hinge 3a is a multi-joint hinge, in particular a 7-hinge hinge. This has over the first embodiment has the advantage that the door 2 is guided over a dead center when opening and thus represent the opening position and the closed position of the door 2 stable end positions. On the hinge 3a fittings 63, 64 are provided, which are connected to the door 2 and the housing 4, respectively. All elements of the hinge 3a are formed from bent sheet metal having a substantially U-shaped cross-section. The hinge 3a is thus mirror-symmetrical with respect to a horizontally extending plane of symmetry. For simplicity, only one half of the hinge 3a, namely lying above the plane of symmetry, is shown. The hinge 3a consists essentially and in simplified terms of a first hinged to the fitting 64 parallelogram, to which a second parallelogram is articulated, on which in turn the fitting 63 is articulated. Specifically points the fitting 64 a flat body and a protruding with respect to the door 2 nose 43. At this, a middle hinge arm 45 is pivotally mounted via a hinge 44. At the outer end of the nose 43 is - in Fig. 5 to the left of the hinge 44 and further away from the housing 4 than the hinge 44 - a support arm 46 articulated via a hinge 47. The support arm 46 is not straight, but is bent in the direction of the door 2 so that it does not collide with the housing 4 facing, rounded edge 48 of the door 2 when opening. The arms 45 and 46 are both hinged to an intermediate plate 49 at adjacent joints 50 and 51, respectively. The pivot point 50 is located approximately in the middle of the middle hinge arm 45, the arm 45 thus still extends beyond the hinge 50 addition. The intermediate plate 49 is elongated and bulged in the middle. The hinge 50 is located on the housing 4 end facing. The hinge 51 is located approximately halfway between the hinge 50 and the fitting 63 to which the intermediate plate 49 is articulated via a hinge 52. The nose 43, the arms 45 and 46 and the intermediate plate 49 form with the joints 44, 47, 50, 51 a first four-point joint, approximately a parallelogram. At the end remote from the housing 4 of the central hinge arm 45, an intermediate arm 54 is articulated via a hinge 53, which is fastened at its other end to the fitting 63 via a hinge 55. The hinge points 52, 50, 53, 55 form a second four-point joint, which is articulated via the rigid central hinge arm 45 on the one hand and on the other hand via the articulated support arm 46 at the second four-point joint. The joints 52, 50, 53, 55 also approximately form a parallelogram. It should be noted that this is only roughly approximated. The hinge 50 does not rest on a line passing through the hinges 44 and 53, but outwardly therefrom toward the housing 4. The center hinge arm 45 is thus light toward the door 2 formed angled. Centered between the joints 50 and 52 on the one hand and the joints 53 and 55 on the other hand, a compression spring 56 via two joints 57, 58 articulated to the intermediate plate 49 and the intermediate arm 54 each pivotally. In the region of the joint 57, the intermediate plate 49 on the aforementioned bulge.

At the joint 53, the damper 6 with its attached to the piston rod 19 fastening element 21 a, which in Fig. 6 shown in more detail, articulated. For this purpose, a fork 59 with two legs 60 is attached to the outer end of the piston rod 19. The fork 59 has corresponding transversely to the central longitudinal axis 12 open latching openings 61, with which the fork 59 is snapped onto a pivot 53 forming the pin 62. The pin 62 is also guided through corresponding holes in the central hinge arm 45 and intermediate arm 54. It is also possible that the articulation of the free end of the piston rod 19 does not coincide with the joint 53. The articulation can also be done on the arm 45 in the direction of the joint 50 or on an extension then to be provided, which extends beyond the joint 53 to the outside. It is advantageous if the damper 6 is articulated on the center hinge arm 45, since the lever effect achieved thereby is particularly large. By the displacement of the articulation point of the fastening element 21a on the line between the joints 50 and 53, the torque generated can be changed with the same damper 6. For example, the adaptation of the same damper 6 to doors 2 of different sizes and thus different mass can be done. The peculiarity of the center hinge arm 45 opposite the other arms of the 7-hinge hinge is that the arm 45 is simultaneously part of the first four-point joint 44, 50, 51, 47 and the second four-point joint 50, 53, 55, 52. It is possible to attach the free end of the piston rod 19 also on a sheet, the the arm 45 is attached. As in the first embodiment, the damper 6 is hinged at its other end approximately centered on the width of the door 2 on the door 2.

The following is with reference to the Fig. 5 . 7 and 8th described the dynamics of the hinge 3a. In Fig. 5 the door 2 is shown in a central opening position, for example at an opening angle of approximately 45 °. This position represents the initially-mentioned dead center of the door. In this position, the distance between the joints 57 and 58, the articulation points of the compression spring 56, minimal. A pivoting towards the in Fig. 7 shown closed position or a pivoting in the in Fig. 8 shown opening position leads to an increase in the distance between the hinge points 57 and 58, that is, the compression spring 56 pushes the door 2 beyond the dead center either in the open position or in the closed position, which are then stable. In the in Fig. 7 shown closed position, the two arms 45 and 46 are pivoted in the direction of the housing 4. The intermediate plate 49 and the intermediate arm 54 extend obliquely backwards. The hinge 3a is thus compactly folded and the compression spring 56 is compared to the center position according to Fig. 5 relatively relaxed. At the in Fig. 8 illustrated opening position, the two arms 45 and 46 are pivoted maximum of the fitting 64 away. The same applies to the intermediate plate 49 and the intermediate arm 54. The hinge 3a thus has its maximum longitudinal extent. The rear edge 48 of the door 2 is maximally far away from the housing edge 4 facing it so that access to the interior of the refrigerator or to the door is optimally possible. The compression spring 56 is compared to in Fig. 5 shown position in a relatively relaxed state.

In the following, the opening and closing behavior of the door 2 will be described taking into account the damping characteristic of the damper 6. Before opening the door 2, the piston 30 is in a maximum insertion position. When pulling out the piston rod 19, the damping is minimal, since the comparatively large holes 36 are decisive for the damping behavior. The door 2 can thus be easily opened. From a defined opening angle, the door remains in the open position. Here, the opening forces of the door hinge and the closing forces of the damper compensate each other. When closing the door 2, the valves 37 are closed, the damping of the damper 6 is thus higher. The insertion of the piston rod 19 is simplified by the return spring 38. Beyond the dead center, the complete, damped closing of the refrigerator door 2 by the compression spring 56, the return spring 38 and the increasing damping by the longitudinal grooves 39 is ensured.

As already mentioned, it is basically possible to attach the damper 6 to both the upper and the lower hinge 3a of the door 2. This can be z. B. in high refrigerators, where the load can be correspondingly higher, be useful. For devices with double doors, z. As refrigerator and freezer, two doors are arranged one above the other. Depending on requirements, one damper, two dampers or mixed versions can be used for each. As already explained, the hinging of the damper 6 on the center hinge arm 45 reduces the opening force to be applied when the door 2 is opened. This can be explained by the fact that the damper 6 additionally supports the door 2 and thus reduces the frictional forces in the hinge 3a. The wear of the hinge 3a is thus reduced and the life increases. Another decisive advantage of the arrangement of the damper 6 results from the approximately parallel arrangement of the damper to the door. This will avoided that with the door closed 2 too high pressure is exerted on the door seal. This would eventually lead to impairment of the seal and thus to possible leaks over a longer period.

The following is with reference to Fig. 9 an embodiment of the invention described. Identical parts are given the same reference numerals as in the embodiment according to FIG Fig. 5 to 8 , whose description is hereby referred to. Structurally different, but functionally similar parts receive the same reference numerals with a trailing b. The main difference consists in the articulation of the damper 6 on the hinge 3b. For attachment of the fastening element 21b, a separate fastening arm 70 is provided on the center hinge arm 45 in the region of the joint 53. The arm 70 has at its outer end in the form of a fork with two superimposed, spaced-apart webs 71 on. The webs 71 have aligned bores 72 through which a pin 73 is guided and fixed there. At the other end, the fastening arm 70 has a contact surface 74 adapted to the outer contour of the central hinge arm 45. In the present case, the attachment arm 70 is connected by a screw 75 to the center hinge arm 45. It can also find other connection options such as riveting, welding, etc. use. The attachment arm 70 is perpendicular to in Fig. 9 illustrated plane has a smaller thickness than it has the hinge 3b. As a result, the attachment arm 70 does not project beyond the hinge 3b.

The fastening element 21b is formed as a rod-shaped head with a bore through which the pin 73 is guided. The fastening element 21b is thus held between the two webs 71 and around the pin 73 pivotable. An advantage of this design is that an existing hinge can be used, to which the damper 6 can be connected later. Instead of the hole in the fastening element 21 may also be provided an outwardly leading slot in the form of a mouth.

The following is with reference to Fig. 10 a non-inventive embodiment described. Identical parts are given the same reference numerals as in the embodiment according to FIG Fig. 5 to 8 , to the description of which reference is hereby made. Structurally different, but functionally similar parts receive the same reference numerals with a c. The main difference consists in the articulation of the fastening element 21c on the central hinge arm 45c. This is extended beyond the joint 53 to the outside and thus has a relation to the hinge 53 outwardly projecting portion 76. As in the embodiment according to Fig. 9 the section 76 consists of two stacked, fork-shaped projecting webs with aligned holes 77 through which a pin 78 is guided and fixed there. The head-like fastening element 21c has a bore through which the pin 78 is guided. The element 21 c is thus fixed between the webs and pivotable about the pin 78. An advantage of this configuration is that the joint 53 and the joint belonging to the pin 78 are decoupled from each other.

Claims (14)

1. Arrangement,

   a. with a first part (2),

   b. with a second part (4) pivotably articulated to the first part (2) via a hinge (3b),

   wherein

   c. one fitting (63) is fastened to the first part (2) while another fitting (64) is fastened to the second part (4),

   d. the hinge (3b) is a multi-jointed hinge,

   wherein

   e. a piston cylinder damping unit (6) is provided

   i. which is operatively arranged between the first part (2) and the second part (4) for damping a pivoting movement of the two parts (2, 4) relative to each other, and

   ii. which is articulated to at least one part (2, 4),

   f. the hinge (3b) comprises a first four-point joint articulated to the fitting (64) and a second four-point joint articulated to the fitting (63), the two four-point joints being articulated to each other,

   g. the multi-jointed hinge comprises a central hinge arm (45) to which the piston cylinder damping unit (6) is articulated by means of a fastening arm (70),

   h. the fastening arm (70) is configured such as to be separate from the central hinge arm (45), and

   i. the fastening arm (45) is part of the first four-point joint and of the second four-point joint at the same time.
2. Arrangement according to claim 1, characterised in that the piston cylinder damping unit (6) comprises a piston (30) displaceably guided in a housing (7), wherein the piston (30) divides a working space (29) into a first partial working space (31) and a second partial working space (32).
3. Arrangement according to claim 2, characterised in that in the housing (7) a return spring (38) connected to the piston (30) is provided for returning the piston (30) from a withdrawn position into an initial position.
4. Arrangement according to claim 3, characterised in that the working space (29) is partially filled by a damping fluid (33).
5. Arrangement according to claim 4, characterised in that at least along one part of the internal wall (17) of the housing (7) at least one damping groove (39) is provided for altering the damping behaviour.
6. Arrangement according to claim 1, characterised in that the piston cylinder damping unit (6) is articulated to the multi-jointed hinge.
7. Arrangement according to claim 1, characterised in that the central hinge arm (45; 45c) is not directly articulated to at least one part (2, 4).
8. Arrangement according to claim 7, characterised in that the central hinge arm (45; 45c) is directly articulated to the second part (4) via a joint (44).
9. Arrangement according to claim 8, characterised in that the central hinge arm (45; 45c) is articulated to the first part (2) via at least one separate arm (49, 54).
10. Arrangement according to any one of the preceding claims, characterised in that the piston cylinder damping unit (6) comprises a return spring (38) that is pretensioned such that it pushes a piston (30) back into a housing (7) when a piston rod (19) is withdrawn counter to a withdrawal direction (26).
11. Arrangement according to claim 10, characterised in that the return spring (38) is configured as a spiral spring that is arranged between the piston (30) and the bush (27) such as to concentrically surround the piston rod (19).
12. Arrangement according to any one of the preceding claims, characterised in that the hinge (3b) has a dead centre point from which the first part (2), when being pivoted beyond the dead centre point, is displaceable into an opening position or into a closing position as stable end positions.
13. Arrangement according to claim 12, characterised in that a compression spring (56) is pretensioned between articulation points (57, 58), wherein in the dead centre point, a distance between the articulation points (57, 58) is minimal so the compression spring (56) pushes the first part (2) beyond the dead centre position either into the opening position or into the closing position.
14. Arrangement according to any one of the preceding claims, characterised in that from a definable opening angle, the first part (2) remains in an open position, wherein in particular the opening forces of the hinge (3b) and closing forces of the piston cylinder damping unit (6) compensate each other.

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