EP1884614A2 - Hinge unit - Google Patents

Abstract

The arrangement (1) has a hinge (3) for pivotably connecting a refrigerator door (4) at a refrigerator housing (2), and a piston-cylinder damping unit (12) arranged between the housing and the door for damping pivoting movement of the housing and the door to each other, where the damping unit is directly hinged at the housing and the door using joint connections (34, 35). A spring unit (36) is arranged between the housing and the door for producing pivoting force and is directly hinged at the housing or the door and the damping unit using spring joint connections (44, 45).

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, this is no longer connected to the stop damper from a certain opening angle. The refrigerator door can thus strike in the open state, for example, to an adjacent wall. When closing the refrigerator door, this only comes into contact with the stop damper at a certain closing angle. Since the weight of refrigerator doors is highly variable, the known damping behavior is unsatisfactory.

The invention has for its object to provide a simple hinge arrangement, which has a comparison with the prior art improved damping behavior.

This object is solved by the features of claim 1. The essence of the invention is that the hinge arrangement comprises a piston-cylinder damping unit, which is articulated directly by means of a first articulation connection on a first part and by means of a second articulation connection directly on a second part at least one spring element is provided, which is arranged to generate a pivoting force between the first part and the second part acting and by means of a first spring-articulation connection directly to one of the parts and by means of a second spring-articulation connection directly to the piston-cylinder damping unit is articulated. Characterized in that the piston-cylinder damping unit is articulated directly to the two parts and the at least one spring element is articulated directly to one of the parts and directly to the piston-cylinder damping unit, the hinge arrangement is simple built up. By means of the piston-cylinder damping unit, the damping behavior of the hinge arrangement can be adjusted within wide ranges. Due to the articulation of the at least one spring element on one of the parts and on the piston-cylinder damping unit, a pivoting force can be generated both when opening and when closing the hinge arrangement.

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

Fig. 1

eine Draufsicht auf eine Scharnier-Anordnung gemäß einem ersten Ausführungsbeispiel mit einer Kolben-Zylinder-Dämpfungs-Einheit,

Fig. 2

eine Seitenansicht der Scharnier-Anordnung gemäß Fig. 1,

Fig. 3

einen Axialschnitt der Kolben-Zylinder-Dämpfungs-Einheit gemäß Fig. 1 für zwei verschiedene Kolben-Positionen,

Fig. 4

Kraft-Einschubweg-Kennlinien der Kolben-Zylinder-Dämpfungs-Einheit gemäß Fig. 1 für zwei Einschub-Geschwindigkeiten,

Fig. 5

eine Ansicht der Scharnier-Anordnung gemäß Fig. 1 in einer Mittel-Position,

Fig. 6

eine Ansicht der Scharnier-Anordnung gemäß Fig. 1 in einer Schließ-Position,

Fig. 7

eine Ansicht der Scharnier-Anordnung gemäß Fig. 1 in einer Öffnungs-Position,

Fig. 8

eine Ansicht einer Scharnier-Anordnung gemäß einem zweiten Ausführungsbeispiel in einer Schließ-Position,

Fig. 9

eine Ansicht der Scharnier-Anordnung gemäß Fig. 8 in einer Öffnungs-Position,

Fig. 10

eine Ansicht einer Scharnier-Anordnung gemäß einem dritten Ausführungsbeispiel in einer Schließ-Position,

Fig. 11

eine Ansicht einer Scharnier-Anordnung gemäß einem vierten Ausführungsbeispiel in einer Öffnungs-Position,

Fig. 12

eine Schnittdarstellung der Scharnier-Anordnung gemäß Fig. 11 entlang der Schnittlinie XII-XII,

Fig. 13

eine Ansicht einer Scharnier-Anordnung gemäß einem fünften Ausführungsbeispiel in einer Öffnungs-Position, und

Fig. 14

eine Schnittdarstellung der Scharnier-Anordnung gemäß Fig. 13 entlang der Schnittlinie XIV-XIV.

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

Fig. 1

a top view of a hinge assembly according to a first embodiment with a piston-cylinder damping unit,

Fig. 2

a side view of the hinge assembly of FIG. 1,

Fig. 3

an axial section of the piston-cylinder damping unit according to FIG. 1 for two different piston positions,

Fig. 4

Force insertion path characteristics of the piston-cylinder damping unit according to FIG. 1 for two insertion speeds,

Fig. 5

1 is a view of the hinge arrangement according to FIG. 1 in a middle position,

Fig. 6

1 is a view of the hinge arrangement according to FIG. 1 in a closed position,

Fig. 7

1 a view of the hinge arrangement according to FIG. 1 in an opening position,

Fig. 8

a view of a hinge assembly according to a second embodiment in a closed position,

Fig. 9

a view of the hinge assembly of FIG. 8 in an open position,

Fig. 10

a view of a hinge assembly according to a third embodiment in a closed position,

Fig. 11

a view of a hinge assembly according to a fourth embodiment in an open position,

Fig. 12

a sectional view of the hinge assembly of FIG. 11 along the section line XII-XII,

Fig. 13

a view of a hinge assembly according to a fifth embodiment in an open position, and

Fig. 14

a sectional view of the hinge assembly of FIG. 13 along the section line XIV-XIV.

Hereinafter, a first embodiment of the invention will be described with reference to Figs. In a hinge arrangement 1, a second part 4, designed as a refrigerator door, is pivotably articulated to hinges 3 on a first part 2, which is only partly shown and designed as a refrigerator housing. Hereinafter, the first part is referred to as a refrigerator housing 2 and the second part as a refrigerator door 4. The hinge 3 each have a cross-sectionally U-shaped first articulation element 5 with a first articulation element wall 6, a parallel thereto extending second articulation element wall 7 and connecting them third articulation element wall 8 , The third link element wall 8 is connected to the refrigerator housing 2. Starting from the refrigerator door 4 facing first hinge element wall 6, a pin 9 extends into a arranged in the refrigerator door 4 pin hole 10, so that the refrigerator door 4 by means of the pin 9 and the pin hole 10 is pivotally connected to the refrigerator housing 2 about a pivot axis 11. 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 4, which have a common pivot axis 11.

For damping the opening and closing movement of the refrigerator door 4 designed as a fluid damper piston-cylinder damping unit 12 is provided. The piston-cylinder damping unit is hereinafter referred to as fluid damper 12. The fluid damper 12 has a substantially cylindrical housing 13 with a central longitudinal axis 14. The housing 13 is closed at one end with a bottom 15 which is formed integrally with the housing 13. On the bottom 15, a first fastening element 16 is integrally formed, which is provided with a first mounting hole 17. The first attachment member 16 has a first pivot axis 18 which is perpendicular to the central longitudinal axis 14 concentric with the first attachment bore 17 and intersects the central longitudinal axis 14. On the refrigerator door 4, a second articulation element 19 is arranged, which has a bore 20. The first attachment member 16 is pivotably connected to the second link member 19 by inserting a bolt 21 into the bore 20 about the first pivot axis 18. In principle, the first attachment element 16 and the second linkage element 19 may be of any desired design, as long as they are pivotally connected to each other about the first pivot axis 18. For example, the first attachment member 16 and the second link member 19 may be formed as a hinged connection with a ball stud and a ball socket.

At an opposite end of the bottom 15 of the housing 13 a integrally formed with this cover 22 is arranged concentrically to the central longitudinal axis 14 has an opening 23. Through the opening 23 a piston rod 24 is led out of the housing 13, to which by means of a screw connection 25, a second fastening element 26 is arranged. The second fastening element 26 is fork-shaped and has a U-shaped cross-section. The second attachment member 26 includes a first attachment member wall 27, a second attachment member wall 28 disposed parallel thereto, and a third attachment member wall 29 connecting the third attachment member wall 29 Fastening element wall 29 is connected to the piston rod 24 by means of the screw connection 25. As an alternative to the screw connection 25, any form-fitting connections are possible. The first and the second fastening element wall 27, 28 are spaced apart from each other so that they can be inserted substantially free of play between the first Anlenk-element wall 6 and the second Anlenk-element wall 7. The first and second fastening element wall 27, 28 each have a second fastening bore 30 in the region of their free ends. Accordingly, the first and second hinge element wall 6, 7 two mutually aligned holes 31. A bolt 32 is guided in each case through a second fastening bore 30 and an associated bore 31, so that the second fastening element 26 is pivotably connected to the first pivoting element 5 about a second pivoting axis 33.

The second mounting bores 30, the bores 31 and the bolts 32 arranged therein form a first articulation connection 34 with the pivoting axis 33, the pivoting axis 33, when viewed in a plane, defining a first articulation point. Accordingly, the mounting hole 17, the bore 20 and the bolt 21 form a second pivot connection 35 with the pivot axis 18, wherein the pivot axis 18 defines a second pivot point. The fluid damper 12 is articulated directly to the refrigerator housing 2 by means of the first articulated connection 34 and directly to the refrigerator door 4 by means of the second articulation connection 35. The fluid damper 12 is arranged damping effect between the refrigerator housing 2 and the refrigerator door 4.

The distance of the first link 34 from the pivot axis 11 is designated by a. The distance of the second hinge connection 35 from the pivot axis 11 is denoted by b. The fixed articulation of the fluid damper 12 on the refrigerator housing 2 on the one hand and on the refrigerator door 4 on the other hand takes place so that the fluid damper 12 as little as possible enclosed by the refrigerator door 4 in the direction of the refrigerator housing 2 Space protrudes. Thus, b is much larger than a.

The hinge arrangement 1 further comprises a spring element designed as a helical spring 36, which is arranged to generate a pivoting force between the refrigerator housing 2 and the refrigerator door 4. At the ends of the spring element 36 integrally a fastening hook 37 is integrally formed. For fixing the spring element 36, a first spring element pin 38 and a second spring element pin 39 is provided. The first spring element pin 38 is disposed in two mutually aligned first spring mounting bores 40 formed near the third mounting element wall 29 in the first and second mounting element walls 27, 28. The spring element 36 is guided with a fastening hook 37 around the first spring element pin 38 and pivotally connected to the second fastening element 26 about a first spring pivot axis 41. The second spring element pin 39 is correspondingly arranged in two mutually aligned second spring mounting holes 42 which are formed near the third hinge element wall 8 in the first and second hinge element wall 6, 7. The further fastening hook 37 is guided around the second spring element bolt 39, so that the spring element 36 is pivotably connected to the first pivot element 5 about a second spring pivot axis 43. The spring element 36 is thus between the first and second fastening element wall 27, 28 and biased between the spring element bolts 38, 39.

The spring element pin 39 and the spring mounting holes 42 form a first spring articulation connection 44 with the spring pivot axis 43, wherein the spring pivot axis 43 in a plane considered a first spring Articulation point defined. Accordingly, the spring element pin 38 and the spring mounting holes 40 form a second spring-hinge connection 45 with the spring-pivot axis 41, wherein the spring-pivot axis 41 a second spring-hinge point Are defined. By means of the first spring-articulated connection 44, the spring element 36 is articulated directly on the refrigerator housing 2 and by means of the second spring-articulated connection 45 directly to the fluid damper 12.

The first articulation connection 34 is stationary relative to the refrigerator housing 2 and the first articulation element 5. Furthermore, the first spring-articulation connection 44 is stationary relative to the refrigerator housing 2 and the first articulation element 5. The second spring-hinge connection 45 is movable relative to the refrigerator housing 2. In a middle position - shown in FIG. 5 - the first linkage 34 is arrangeable along a straight line between the spring-link connections 44, 45. This means that the second pivoting axis 33 lies on a straight line that runs between the spring-pivoting axes 41, 44. When the second pivot axis 33 and the first spring pivot axis 41 intersect the central longitudinal axis 14, as shown in FIG. 5, the straight line is identical to the central longitudinal axis 14. In the middle position, the spring element 36 is maximally tensioned so that a dead center is formed. In the middle position closes the refrigerator door 4 with the refrigerator housing 2 an opening angle α a. The opening angle α and the opening force and the closing force of the spring element 36 can be adjusted constructively in dependence on the position of the spring-articulated connections 44, 45 relative to the position of the first articulated connection 34.

In the following, the structure of the fluid damper 12 will be explained in more detail with reference to FIG. Fig. 3 shows in the upper half of the fluid damper 12 in the closed position shown in FIG. 6 and in the lower half in the open position shown in FIG. 7. The housing 13, the bottom 15 and the cover 22 limit in Essentially a working space 46. In the area of the cover 22, a guide and seal unit 47 is arranged, which is fixed by means of a formed in an inner wall 48 of the housing 13 annular groove 49. The piston rod 24 is guided by the guide and sealing unit 47 and the lid 22 sealed to the outside and slidably guided along the central longitudinal axis 14. In the working space 46 is a on the inner wall 48 sealingly abutting, along the central longitudinal axis 14 displaceable piston 50 which is fixed to the housing-inner end of the piston rod 24. The piston 50 divides the working space 46 into a first working space 51 facing the floor 15 and into a second working space 52 facing the guiding and sealing unit 47. The work space 46 is provided with a damping fluid 53, in particular oil, partially filled, wherein the remaining working space 46 with gas, in particular air, is filled.

Within the housing 13, between the guiding and sealing unit 47 and the piston 50, a first elastic stop element 54 is arranged, which annularly surrounds the piston rod 24 and rests against the inner wall 48 and the guiding and sealing unit 47. The first Stop element 54 is formed as an elastomeric ring. Accordingly, between the bottom 15 and the piston 50, a second resilient abutment member 55 is disposed in the housing 13. The second stop element 55 is designed as a helical spring and bears against the bottom 15 and partially against the inner wall 48. In principle, the stop elements 54, 55 may be formed as desired, for example as a plate spring, coil spring, elastomer or PU foam.

The fluid damper 12 has a parallel to the central longitudinal axis 14 extending Ausschub direction 56. To generate a damping damping bores 57 are arranged in the piston 50 distributed over its circumference, which penetrate the piston 50 and extend parallel to the Ausschub direction 56. The damping bores 57 connect the first part working space 51 with the second part working space 52 and generate a speed-dependent damping force when the piston 50 moves. The damping bores 57 may be partially closed by valves which are open in a movement in the extension direction 56 and are closed in a movement against the Ausschub direction 56. By such valves, upon movement of the piston 50 against the Ausschub direction 56 a greater damping force can be generated, as in a movement in the extension direction 56th

In the inner wall 48 a plurality of longitudinal grooves 58 are uniformly distributed over the circumference. In the region of these longitudinal grooves 58, the piston 50 is not close to the inner wall 48 at. A flow channel 59 is formed between the piston 50 and the groove bottom 60 of the longitudinal grooves 58. Starting from the bottom 15, there first exists a first inner wall section 61, along which no longitudinal grooves 58 are provided are. This is followed by a second inner wall section 62, along which the cross section of the longitudinal grooves 58 along the Ausschub direction 56 increases constantly from zero. This is followed by a third inner wall section 63, along which the longitudinal grooves 58 have a substantially constant cross section. This is followed by a fourth inner wall section 64, along which the cross section of the longitudinal grooves 58 decreases constantly to zero over a shorter length compared to the second inner wall section 62. This is followed by a fifth inner wall section 65, along which in turn no longitudinal grooves 58 are present.

Hereinafter, the characteristics of the fluid damper 12 will be described with reference to FIG. 4. Fig. 4 shows two force-stroke characteristics of the fluid damper 12 for two piston speeds of the piston 50. The force-stroke characteristics are compared at the piston speeds v ₁ and v ₂ , where v _{1 is} greater than v ₂ is. The characteristic curves are in principle the same, with the damping force P being lower at lower piston speed v ₂ than at the larger piston speed v ₁ . In the following, only the characteristic curve for the piston speed v _{1 will be} described. The characteristic initially has a region A in which the damping force P decreases linearly independently of the speed. This is followed by an area B in which the damping force P increases linearly from zero speed. In these areas of the characteristic, the piston 50 is in interaction with the second stop element 55. As the movement of the piston 50 in the extension direction 56 increases, the force of the second stop element 55 on the piston 50 decreases. This is shown as a dashed extension of the area A in FIG. 4. The area B is followed by a plateau-shaped area C, in which the damping force F is constant. In In this area, the piston 50 is no longer in interaction with the second stopper member 55 and the piston speed is constant. However, the piston 50 is still at least partially in the region of the first inner wall portion 61. The region C is followed by a region D in which the damping force P decreases linearly. In this region D, the piston 50 is completely in the region of the second inner wall portion 62, wherein the effective flow cross section due to the longitudinal grooves 58 increases constantly and as a result, the damping force F decreases constantly. The area D is followed by a plateau-shaped area E, in which the damping force P is constant and small. In this area, the piston 50 is completely in the region of the third inner wall portion 63, wherein the effective flow cross section of the longitudinal grooves 58 maximum and consequently the damping force P is minimal. The region E is followed by a region F in which the damping force P increases again linearly. In the region F, the piston 50 is in the region of the fourth inner wall portion 64, wherein due to the linear decreasing effective flow cross-section of the longitudinal grooves 58, the damping force P increases linearly. The area F is followed by a plateau-shaped area G, in which the damping force P is constant. In this area, the piston 50 is located in the region of the fifth inner wall section 65, but not yet in interaction with the first stop element 54. The region G is followed by a region H and a region I. In the region H, the damping force P decreases linearly and in the region I linearly increases again. In these areas, the piston 50 is in interaction with the first stopper member 54, wherein the piston speed decreases to zero and the force of the first stopper member 54 on the piston 50 increases. The superposition of these effects leads to a damping force P corresponding to the areas H and I. Reference is made to the description concerning the areas A and B.

The following describes the damping behavior of the refrigerator door 4 during opening and closing. It is assumed that the refrigerator door 4 is initially closed, as shown in Fig. 6. The piston rod 24 is in the inserted state. The piston 50 is in the position shown in Fig. 3 above. The second pivot axis 33 of the first link 34 is not disposed on the line defined by the spring pivot axes 41, 43, so that the spring element 36 on the fluid damper 12, a closing moment about the second pivot axis 33 and the refrigerator door 4 thus exerts a closing force. When opening the refrigerator door 4, the spring element 36 must first be tensioned. In the middle position shown in Fig. 5, the spring element 36 is maximally tensioned, thereby forming a dead center. The pivot axis 33 of the first link 34 now lies on the line defined by the spring-pivot axes 41, 43, which coincides with the central longitudinal axis 14. When opening the refrigerator door 4, an opening force must be applied up to the middle position shown in Fig. 5, from this middle position, the refrigerator door 4 opens automatically due to the spring force of the spring element 36. When the opening angle α of the center position is exceeded, the pivot axis 33 of the first link 34 no longer lies on the straight line defined by the spring-pivot axes 41, 43, so that the spring element 36 on the fluid damper 12th an opening moment about the pivot axis 33 and thus an opening force on the refrigerator door 4 is generated. The piston 50 is in the middle position in the region of the third inner wall portion 63, wherein the damping force F of the fluid damper 12 according to area E in Fig. 4th results. When the refrigerator door 4 is automatically opened, the piston 50 is increasingly moved in the extension direction 56, wherein a damping force F according to the ranges F, G, H and I of the characteristic acts on the piston 50 during the extension movement. If the piston 50 is in the area of the fifth inner wall section 65, the effective flow cross section is minimal and the damping force P maximum so that the piston 50 is braked. In addition, the piston 50 interacts with the first stopper member 54, which additionally applies a force against the extension direction 56 to the piston 50. The ejection movement of the piston 50 is thus gently braked and the refrigerator door 4 stops automatically in an open position. This is shown in FIG. 7.

When closing the refrigerator door 4, starting from the closing position shown in FIG. 7, a closing force must first be expended in order to tension the spring element 36 until it reaches the middle position. When the center position is exceeded, the spring element 36 generates a closing moment on the fluid damper 12 about the pivot axis 33, so that the refrigerator door 4 closes automatically. Incidentally, the operation of the hinge assembly 1 when closing corresponds to the opening, so reference is made to it.

By the damping behavior of the fluid damper 12 is ensured that the opening and closing of the refrigerator door 4 is substantially equal, regardless of whether the refrigerator door 4 is heavily loaded or not and regardless of what force the refrigerator door 4 is pressed. This is achieved on the one hand by the speed-dependent damping behavior of the fluid damper 12 and on the other hand by the fact that the longitudinal grooves 58 a path-dependent damping behavior generate, wherein the path-dependent damping force in the region of the opening position and the closing position is greatest. In addition, the stopper members 54, 55 generate a damping force in these positions. This ensures that the refrigerator door 4 gently opens or closes automatically when the middle position is exceeded.

Hereinafter, a second embodiment of the invention will be described with reference to Figs. 8 and 9. Identical parts are given the same reference numerals as in the first embodiment, to the description of which reference is hereby made. Constructively different parts, but functionally similar parts receive the same reference numerals with a nachgeschlagen a. The main difference compared to the first embodiment is that the spring-mounting holes 40a, 42a of the spring-hinge connections 44a, 45a are formed as a slot. The elongated holes can run along a straight line or along an arbitrarily curved curve. Further, only the first spring-mounting holes 40a or only the second spring-mounting holes 42a may be formed as a slot. The spring element bolts 38, 39 are slidably guided along the elongated holes in the spring mounting bores 40a, 42a. Although the spring-element pin 39 of the first spring-articulation connection 44a is displaceable, the first spring-articulation connection 44a, in particular the spring-fastening bores 42a, is basically stationary relative to the refrigerator housing 2.

When opening and closing the refrigerator door 4, the spring element bolts 38, 39 can be guided in the elongated holes formed as spring mounting holes 40a, 42a, so that the lever ratios be improved in the automatic opening and closing of the refrigerator door 4. Compared to the first embodiment, due to the spring mounting holes 40a, 42a, a larger opening moment and closing moment is generated on the fluid damper 12a, and thus a larger opening force and closing force on the refrigerator door 4. By the spring mounting holes 40a, 42a is carried out a pivot point displacement and a displacement of the spring-pivot axes 41, 43rd

It is also advantageous if at least one of the spring-element bolts 38, 39 for setting the dead center, that is, the opening angle α in the middle position, relative to the formed as a slot and associated spring mounting hole 40a, 42a is fixable , The fixation can be done for example by a thread and a nut screwed thereon. By a displacement and fixation of the spring-pivoting axes 41, 43, the dead center and the lever ratios, for example during assembly of the hinge arrangement 1a, can be adjusted within wide ranges. In addition, reference is made to the fourth and fifth embodiments described below. With regard to the further operation of the hinge arrangement 1a, reference is made to the first embodiment.

Hereinafter, a third embodiment of the invention will be described with reference to FIG. Identical parts are given the same reference numerals as in the first embodiment, to the description of which reference is hereby made. Structurally different parts, but functionally similar parts get diesleben reference with a trailing b. The essential difference from the first embodiment is that the second elastic stop element 55 b is arranged outside of the housing 13 between the second fastening element 26 and the housing 13. In addition, another elastic abutment element may be provided between the piston 50 and the bottom 15 within the housing 13. The second stop element 55b is formed as an elastomeric ring and surrounds the piston rod 24. Regarding the operation, reference is made to the first embodiment.

Hereinafter, a fourth embodiment of the invention will be described with reference to FIGS. 11 and 12. Identical parts are given the same reference numerals as in the first embodiment, to the description of which reference is hereby made. Structurally different parts, but functionally similar parts receive the same reference numerals with a c. The main difference with respect to the first embodiment is that the second spring-mounting holes 42c are formed as a slot, wherein the associated second spring-element pin 39c is fixed relative to these. For fixing the second spring-element bolt 39c, the hinge arrangement 1c has a cross-sectionally U-shaped retaining clip 66 with a first retaining clip wall 67, a parallel thereto extending second retaining clip wall 68 and a this connecting third retaining clip wall 69. The retaining clip 66 is disposed between the hinge element walls 6c, 7c of the first hinge element 5c. The first and second holding-bracket wall 67, 68 have for performing the second spring-element pin 39c each have a holding-bracket bore 70, wherein the holding-bracket holes 70 are substantially congruent. The second spring-element pin 39c is defined by the second spring-mounting hole 42c of the first link-element wall 6c, the retaining-pin holes 70, and the second Spring mounting hole 42c of the second link element wall 7c out, wherein the second spring element pin 39c by a comparison with the second spring mounting holes 42c larger bolt head 77 and a securing ring 78 against Displacement along the second spring-pivot axis 43 is secured. The second spring element pin 39c is arranged in the retaining clip holes 70 substantially free of play. The fixing hook 37 of the spring member 36 is fixed in a bolt groove of the second spring-element pin 39c.

For positioning the second spring-element pin 39c along the second spring-mounting holes 42c designed as a slot, the hinge arrangement 1c has an adjusting screw 71. The adjusting screw 71 is guided by a setting screw hole 72 on a fourth link element wall 73 of the first link element 5c. The fourth link element wall 73 connects the first and second link element walls 6c, 7c and is disposed substantially perpendicular to the third link element wall 8c. The adjusting screw 71 is secured by means of a securing ring 74 in the adjusting screw hole 72. The adjusting screw 71 has an adjusting screw external thread 75 which is screwed into a retaining clip female thread 76. The retaining clip female thread 76 is formed centrally in the third retaining clip wall 69 and opposite the setting screw bore 72.

By means of the adjusting screw 71 is a pivot point displacement, ie a displacement of the second spring-pivot axis 43, the first spring-link connection 44c possible. If the second spring-pivoting axis 43 is displaced by means of the adjusting screw 71 in the direction of the refrigerator door 4, then the opening and closing behavior of the refrigerator door changes 4 such that the automatic closing of the refrigerator door 4 starts later and the automatic opening of the refrigerator door 4 earlier. If the second spring pivot axis 43 is displaced by means of the adjusting screw 71 in the direction of the fourth link element wall 73, then the opening and closing behavior of the refrigerator door 4 changes such that the automatic closing of the refrigerator door 4 starts earlier, the automatic opening of the refrigerator door 4 later. By means of the adjusting screw 71 can thus be made an individual fine tuning of the opening and closing behavior of the hinge assembly 1c. This can be done for example during assembly of the hinge assembly 1c or by the later user. As an alternative to the adjusting screw 71, an eccentric can also be used. With regard to the further operation of the hinge arrangement 1c, reference is made to the preceding embodiments.

Hereinafter, a fifth embodiment of the invention will be described with reference to Figs. Identical parts are given the same reference numerals as in the first embodiment, to the description of which reference is hereby made. Structurally different parts, but functionally similar parts receive the same reference numerals with a d followed. The main difference with respect to the first embodiment is that the first spring-mounting holes 40d are formed as a slot, wherein the associated first spring-element pin 38d is fixed relative to these. For positioning and fixing the first spring-element pin 38d, according to the fourth embodiment, a retaining clip 66d is provided, which is disposed between the first and second fastening element wall 27d, 28d of the second fastening element 26d. The retaining clip 66d is by means of the adjusting screw 71d along the central longitudinal axis 14 displaced, wherein the adjusting screw hole 72 d is arranged in the third mounting element wall 29 d. By means of the adjusting screw 71d is a pivot point displacement of the second spring-hinge connection 45d possible, that is, the first spring-pivot axis 41 along the central longitudinal axis 14 is displaced. If the first spring-element pin 38d is displaced in the direction of the housing 13 by means of the adjusting screw 71d, the spring force of the spring element 36 is thereby increased, as a result of which a greater closing force during the automatic closing of the refrigerator door 4 acts on it. Is displaced by means of the adjusting screw 71d, the first spring-element pin 38d in the direction of the first hinge element 5, thereby the spring force of the spring element 36 is reduced, whereby a lower closing force in the automatic closing of the refrigerator door 4 on this works. By means of the adjusting screw 71d can thus be made an individual fine tuning of the closing force with respect to the weight of the refrigerator door 4 and the damping behavior of the fluid damper 12d. The fine tuning can be done during assembly or by the later user. As an alternative to the adjusting screw 71d, an eccentric can also be used. With regard to the further operation of the hinge arrangement 1d, reference is made to the preceding embodiments.

Claims (10)

Hinge arrangement, in particular refrigerator housing with a pivotally hinged thereto refrigerator door, with a. a first part (2), b. a second part (4) pivotably connected to the first part (2) via a hinge (3), c. a piston-cylinder damping unit (12; 12a; 12b; 12d), i. which is arranged for damping a pivoting movement of the first part (2) and the second part (4) to each other between these acting, and ii. which is articulated directly to the first part (2) by means of a first articulation connection (34) and directly to the second part (4) by means of a second articulation connection (35), and d. at least one spring element (36), i. which is arranged to generate a pivoting force between the first part (2) and the second part (4), and ii. which is directly connected to one of the parts (2, 4) by means of a first spring-articulation connection (44; 44a; 44c) and directly to the piston-cylinder damping by means of a second spring-articulation connection (45; 45a; 45d) Unit (12; 12a; 12b; 12d) is articulated. Hinge arrangement according to claim 1, characterized in that the at least one spring element (36) is articulated directly to the first part (2) by means of the first spring-articulation connection (44; 44a; 44c). Hinge arrangement according to claim 1 or 2, characterized in that the first articulation connection (34) is stationary relative to the first part (2). Hinge arrangement according to one of claims 1 to 3, characterized in that the first spring-hinge connection (44; 44a; 44c) is stationary relative to one of the parts (2, 4). Hinge arrangement according to one of claims 1 to 4, characterized in that the first articulation connection (34) for forming a dead center along a straight line between the spring-hinge connections (44, 45, 44a, 45a, 44c, 45; 44, 45d) can be arranged. Hinge arrangement according to one of claims 1 to 5, characterized in that at least one spring-articulation connection (44a, 45a; 44c; 45d) for articulation-point displacement at least one formed as a slot spring-mounting hole (40a, 42a, 42c, 40d) and a spring element pin (38, 39, 39c, 38d) guided therein. Hinge arrangement according to claim 6, characterized in that for setting a dead center of the spring-element pin (38, 39, 39c, 38d) relative to the at least one elongated hole formed as a spring-mounting hole (40a, 42a; 40d) can be fixed. Hinge arrangement according to one of claims 1 to 7, characterized in that the piston-cylinder damping unit (12; 12a; 12b; 12d) has a piston (50) displaceably guided in a housing (13), a piston rod arranged thereon (24) and a arranged at this fork-shaped fastening element (26; 26a; 26d). Hinge arrangement according to claim 8, characterized in that within the housing (13) at least one elastic stop element (54, 55) is arranged. Hinge arrangement according to claim 8 or 9, characterized in that outside the housing (13) at least one elastic stop element (55b) between the fastening element (26) and the housing (13) is arranged.

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