EP0349005B1 - Hinge - Google Patents

Description

The invention relates to a hinge according to the preamble of claim 1.

Such a hinge is known from DE-U-74 39 012.

It is a hinge in which the housing connection part (lower hinge part) can be connected to a housing. A cover connection part (upper hinge part) is rotatably mounted around a bearing pin on the housing connection part. The lid connector can be connected to the lid. A stop pin is arranged on the cover connection part at a distance from the bearing pin. The stop bolt can protrude laterally beyond the cover connection part. For this purpose, guide recesses can be provided in the housing connection part, into which the pins of the stop bolt projecting beyond the cover connection part engage.

A spring guide is supported on the one hand on the end of the housing connection part opposite the cover connection part, and on the other hand on the stop bolt of the cover connection part. The spring guidance is enclosed by a compression spring.

Such a hinge is used by the compression spring to support the opening movement of the lid. Furthermore, with such a hinge a braked opening movement can be achieved. Means are therefore provided which slow down the opening movement of the cover.

In order to achieve a braking effect, a rocker is provided in the known hinge. This rocker consists of a plastic part, which is mounted on the spring guide made of metal so that it can be moved longitudinally. The plastic part has an outer cone on which an inner cone of an annular metal part is supported. This ring-shaped metal part is in turn supported on the housing connection part, namely at that end of the housing connection part which lies opposite the cover connection part. When the cover is opened, there is a relative movement between the spring guide and the rocker, consisting of a plastic part and a metal part. In the previously known hinge, the braking force which triggers the braking action is achieved between the plastic part and the spring guide in that the spring force is deflected into a radial force via the cone. It follows that the frictional force depends on the spring force. The spring force in turn depends on the travel. Since the spring travel is increased when the hinge is opened, the friction force and thus the braking effect decrease accordingly. The braking force is greatest when the lid is closed. In the following movement, the braking force decreases continuously. In the closed state, however, no braking force is required at all. In addition, a braking force in the closed state can also be harmful because it places a load on the plastic part (shoe brake). Plastic tends to flow under high loads, i.e. to undesired, permanent changes in shape. The flow process takes a long time. If the known hinge remains closed for a long time, the effect of the shoe brake can change. It then no longer achieves the desired braking effect. The braking performance decreases. But it is also possible that the braking power increases. Endurance tests have also shown that the sliding surface of the plastic part can change. The greater the force, the greater the wear. Since a high force is present in the idle state (closed state), a high force is practically applied to the surface when opening begins, which promotes rapid wear.

In the known hinge, the spring force decreases with increasing opening of the cover. The spring is designed to support the opening of the lid. The brake ensures that the lid movement does not become independent, so that the lid does not "pop up." If the spring force drops as the lid opening angle increases, the braking effect also decreases. With the known hinge, a braking effect that is too small may be achieved with a lid opening angle of a certain size.

The object of the invention is therefore to provide a hinge with a brake with which the required braking effect can be achieved for the respective cover opening angle.

According to the invention this object is achieved by the features specified in the characterizing part of claim 1. Advantageous refinements are specified in the subclaims. The spring guide rod, hereinafter referred to as "spring guide", has a braking area that is elastic in the radial direction and whose outer cross section is larger than the inner cross section of the rocker, so that the sliding movement of the spring guide in the rocker is braked.

If the rocker is in the braking area of the spring guide, the friction is increased and the desired braking effect is achieved. If the cross-section or diameter of the spring guide is smaller, this friction decreases. By an appropriate Cross-sectional gradation or diameter gradation can also be achieved that there is no friction at all. The desired braking effect can therefore be set freely; it can be easily specified by the designer depending on the requirements.

Furthermore, the cone that has been customary to date is dispensed with. The rocker is designed in one piece. It is so rigid that the inner diameter of the sliding guide remains practically the same regardless of how much the spring is compressed. The braking effect is therefore not dependent on the spring force, but solely on the cross section of the spring guide.

The spring guide can be made of plastic and the rocker can be made of metal, in particular sheet metal.

It is possible to manufacture the spring guide from solid material. Then, however, exact fits must be made; this is only possible with a high manufacturing outlay. It is therefore better if the cross section of the spring guide is weakened in a suitable manner, so that this spring guide can be deflected elastically.

• (1) Das Kunststoffteil muß spritztechnisch auf einfache Weise herstellbar sein.
• (2) Es soll eine möglichst große Umfangsfläche vorhanden sein, damit die Flächenpressung möglichst gering ist. Das Kunststoffmaterial hält nämlich nur eine bestimmte Flächenpressung aus. Darüberhinaus ist der Verschleiß um so großer, je größer die Flächenpressung ist.
• (3) Es soll eine möglichst große Federkraft in radialer Richtung erzeugt werden können.

The cross-sectional shape of the lead must meet various requirements:

• (1) The plastic part must be easy to manufacture by injection molding.
• (2) The largest possible circumferential surface should be available so that the surface pressure is as low as possible. The plastic material can only withstand a certain surface pressure. In addition, the greater the surface pressure, the greater the wear.
• (3) It should be possible to generate the greatest possible spring force in the radial direction.

For these reasons, it is advantageous to provide radial slots (recesses). These can, for example, be arranged opposite one another and be slightly offset laterally. It is even better if the radial slots are rounded, since a particularly good spring action in the radial direction can then be achieved. The slots can be reinforced by ribs. The ribs can face each other diagonally. This also makes you independent of manufacturing tolerances. The tolerances must be adhered to the more precisely, the less the spring material springs. With solid material, the tolerances must be adhered to most precisely. With a good spring action, the tolerances are no longer so important.

Another advantage is that the spring can be completely guided over its entire length and with each travel. Strictly speaking, this only applies to the compressed state of the spring. So far, the spring guide was made of metal and the shoe brake was made of plastic. The situation is now reversed: the spring is made of plastic and the rocker is made of metal. It is therefore advisable to increase the diameter of the upper area of the spring guide, since this is possible in a simple manner. The spring can then no longer buckle.

The area of the rocker with the smallest diameter, that is to say the area that comes into engagement with the spring guide, can be designed on both sides in the shape of a nozzle. It is therefore necessary to remove the burr so that the surface of the spring guide is not damaged or scratched.

The spring force can be adjusted so that it is in closed state is zero, then rises and has a constant large amount. Shortly before the maximum open position of the cover is reached, the braking force decreases again. However, it is kept at a certain minimum value since the spring is still effective in this area and therefore a minimum braking effect is still required. However, one is not limited to this braking force curve. The braking force curve can rather be predefined by a simple change in diameter.

The housing connection part can also have a novel design. It basically consists of a C-shaped sheet. As a result, the part is particularly stable since there is approximately a box profile.

Fig. 1

eine Schnittansicht von der Seite,

Fig. 2

das in Fig. 1 gezeigte Ausführungsbeispiel in einer Ansicht von vorne,

Fig. 3

einen Querschnitt durch das in den Fig. 1, 2 und 4 gezeigte Ausführungsbeispiel längs der Linie III-III in Fig. 4,

Fig. 4

eine vergrößerte Einzelheit aus der Fig. 2

Fig. 5

die Federführung in einer vergrößerten Darstellung,

Fig. 6

einen Schnitt längs der Linie E-F der Fig. 5,

Fig. 7

einen Schnitt längs der Linie G-H der Fig. 5,

Fig. 8

die Wippe in einer vergrößerten Darstellung,

Fig. 9

eine vergrößerte Einzelheit der in Fig. 8 gezeigten Wippe,

Fig. 10

die in Fig. 8 gezeigte Wippe in einer Ansicht von oben,

Fig. 11

eine vergrößerte Ansicht des Bremsbereichs 16 in einer der Fig. 5 entsprechenden Darstellung,

Fig. 12

einen Schnitt längs der Linie J-K der Fig. 11 und

Fig. 13

einen weiteren Schnitt längs der Linie J-K der Fig. 11 einer weiteren Ausführungsform.

An embodiment of the invention is explained below with reference to the drawing. In the drawing shows

Fig. 1

a sectional view from the side,

Fig. 2

the embodiment shown in Fig. 1 in a view from the front,

Fig. 3

2 shows a cross section through the exemplary embodiment shown in FIGS. 1, 2 and 4 along the line III-III in FIG. 4,

Fig. 4

an enlarged detail of FIG. 2nd

Fig. 5

the lead in an enlarged view,

Fig. 6

a section along the line EF of Fig. 5,

Fig. 7

5 shows a section along the line GH of FIG. 5,

Fig. 8

the rocker in an enlarged view,

Fig. 9

8 shows an enlarged detail of the rocker shown in FIG. 8,

Fig. 10

the rocker shown in Fig. 8 in a view from above,

Fig. 11

3 shows an enlarged view of the braking area 16 in a representation corresponding to FIG. 5,

Fig. 12

a section along the line JK of Fig. 11 and

Fig. 13

another section along the line JK of FIG. 11 of a further embodiment.

1 and 2, the hinge is shown in the closed position. The hinge is particularly suitable for lids that lie horizontally when closed. The bearing pin 2 is connected to the housing connection part 1. On this bearing pin 2, the cover connection part 3 is rotatably mounted. At a distance from the bearing pin 2, a stop pin 4 is arranged in the cover connection part 3. The stop pin 4 protrudes on both sides beyond the cover connection part 3. These protruding pins are in a quarter-circular recess 5 of the housing connector.

The spring guide 6 is rotatably mounted on the stop pin 4. The spring guide 6 is rotatably supported at its one end, shown at the bottom in FIGS. 1, 2 and 4, that is to say at the end opposite the cover connection part 3 on the housing connection part, specifically via the rocker 7. This rocker 7 is along the spring guide ( 6) slidably mounted. At the outer end, the rocker 7 is supported on the projections 8 of the housing connection part (1). At the other end, the spring guide 6 is rotatably mounted on the stop pin 4 of the cover connection part 3. The spring guide 6 has a semi-circular or semi-cylindrical bearing shell 9 at this end.

The compression spring 11 is located between a shoulder 10 on the spring guide 6 on the one hand and the rocker (7) on the other hand.

1 and 2, the hinge is shown in the closed position. The compression spring 11 is thus compressed. When opening the hinge, the spring 11 supports the movement of the lid. During the opening process, the rocker 7 acts as a brake in that it slides along the spring guide 6. The inside diameter of the rocker 7 and the outside diameter of the spring guide 6 are thus coordinated with one another in such a way that the desired friction effect is achieved.

The rocker 7 is designed in one piece. It is shown enlarged in FIGS. 8, 9 and 10. The rocker 7 has an inner guide 12 with which it is guided in a longitudinally displaceable manner on the spring guide 6. Furthermore, the rocker 7 has a radially extending shoulder 13, on which the compression spring 11 is supported. The cylindrical part 14 adjoins this radially extending shoulder 13 radially on the outside. In this cylindrical part 14 are opposed, offset by 180 ° Notches 15 are provided. The opening angle of these notches 15 is 50 °. The rocker 7 is supported with these notches 15 on the projections 8 in the housing connection part 1 (see FIGS. 2 and 4).

The rocker 7 is designed in the form of a nozzle on both sides in the area of its inner guide 12, that is to say in the area that comes into engagement with the spring guide 6; the ridge is removed. This prevents damage or scratching of the surface of the spring guide 6.

As shown in FIGS. 2 and 4, the spring guide 6 has a braking area 16 which is elastic in the radial direction. The outer cross section or outer diameter of the braking area 16 is larger than the inner cross section or diameter of the inner guide 12 of the rocker 7, so that the sliding movement of the spring guide 6 in the rocker 7 is braked.

5, the spring guide 6 is shown enlarged. The spring guide 6 has a first area 17, in which the outer diameter is slightly smaller than the inner diameter of the inner guide 12 of the rocker 7. In the closed position of the hinge, the rocker 7 is located in this first area 17 of the spring guide 6. When the hinge is opened so no friction or braking effect is initially generated. The second area adjoins the first area 17, that is to say the braking area 16. In this braking area 16, the diameter of the spring guide 6 is slightly larger than the inside diameter of the inner guide 12 of the rocker 7; Furthermore, the spring guide 6 in the braking area 16 is elastic in the radial direction. The third area 18 adjoins the braking area 16 and is therefore located at the end of the spring guide 6 shown on the right in FIG. 5. In this third area 18, the outer diameter of the spring guide 6 is slightly larger than the inner diameter the inner guide 12 of the rocker 7, so that a certain, relatively small braking torque is generated. A braking effect is thus also achieved immediately before the opening operation is ended. When the hinge is fully open, the rocker 7 lies in the third region 18 of the spring guide 6.

In its braking area 16, the spring guide 6 has radially running, oppositely arranged and laterally offset slots 19, as can be seen particularly clearly from FIGS. 6 and 7. The cross section of the spring guide 6 in this braking area 16 thus consists of a central web 20, which is followed by arches 21 which are offset on both sides by 180 ° and at an angle of approximately 130 °. The cross-section is thus designed in such a way that all requirements for the cross-sectional shape of the spring guide (6) are met: The spring guide (6) can be produced in a simple manner by injection molding in this area. There is a relatively large peripheral area. Furthermore, a relatively large spring force can be generated in the radial direction. The arches 21 are reinforced by ribs 22.

In its area 23 adjoining paragraph 10, the spring guide 6 is approximately as large in diameter as the inside diameter of the compression spring 11. The compression spring 11 is thus completely guided; it cannot buckle.

As can be seen from Fig. 3, the housing connection part 1 consists of a C-shaped profiled sheet.

As can be seen particularly clearly from FIG. 7, the diameter of the spring guide 6 in the braking area 16 at the location of the central web 20 corresponds to the inner diameter of the inner guide 12 of the rocker 7. This diameter then becomes in the course of the arches 21 greater. Since the arches 21 are designed to be elastic, they are compressed when the rocker 7 with the inner guide 12 reaches the braking area 16. This creates a normal force acting on the inner guide 12 of the rocker 7, which causes the friction and thus the braking effect.

With the hinge just described, the braking force can be controlled depending on the distance. The braking force is independent of the spring force. The spring guide 6 is in one piece. On the spring guide 6 there are paragraph 10, area 23 and areas 17, 16 and 18; all parts are in one piece with the spring guide 6. The hinge consists of a few components, so it is inexpensive to manufacture and easy to assemble. The two support points of the rocker 7, the projections 8, are close together; this allows the rocker (7) to be made of relatively thin material.

FIG. 11 shows an enlarged view of the braking area 16 in a representation corresponding to FIG. 5. The same parts are provided with the same reference numerals.

FIG. 12 shows a section along the line J-K of FIG. 11. Between the end regions of the arches 21 and the central web 20, resilient elements 31 are provided which are circular in cross section and which are integral with the arches 21 and the central web 20.

13 shows another embodiment. Here too, resilient elements 32 are provided between the end regions of the arches 21 and the central web 20, which are integral with the arches 21 and the central web 20. However, the cross section of the resilient elements 32 is semicircular.

Claims (15)

1. Hinge with a housing connection part (1), a lid connection part (3) mounted to rotate thereon about a bearing pin (2), in which lid connection part (3) a stop pin (4) is located at a distance from the bearing pin (2), with an axially displaceable spring guide bar (6), which at its one end is mounted at the end of the housing connection part (1) located opposite the lid connection part (3) so that it is able to tilt with respect to the latter in a rocker member (7) and at its other end is mounted to rotate on the stop pin (4) of the lid connection part (3), the rocker member (7) comprising an internal guide (12), in which the spring guide bar (6) is guided to be longitudinally displaceable and with a compression spring (11) surrounding the spring guide bar (6), which compression spring is located between the rocker member (7) and a stop (10) for the compression spring (11), an axial braking movement of the spring guide bar (6) taking place at the time of opening or closing of the lid by means of a braking device between the spring guide bar (6) and rocker member (7), characterised in that in its section guided in the internal guide (12), the spring guide bar (6) comprises a cylindrical surface, which is resilient in the radial direction, as the braking region (16), whereof the unloaded outer diameter is greater than the guiding diameter of the internal guide (12) of the rocker member (7), the axial length of the braking region (16) extending over a distance, which is dependent on the angular position of the lid connection part (3).
2. Hinge according to Claim 1, characterised in that the internal guide (12) of the rocker member (7) has a cylindrical construction.
3. Hinge according to Claim 1 or 2, characterised in that the rocker member (7) comprises a radially extending shoulder (13) for supporting the compression spring (11).
4. Hinge according to Claim 3, characterised in that a cylindrical part (14) adjoins the radially extending shoulder (13).
5. Hinge according to Claim 4, characterised in that recesses (indentations 15) are provided in the cylindrical part (14).
6. Hinge according to one of the preceding Claims, characterised in that the spring guide bar (6) comprises a first region (17), whereof the cross-section or diameter is slightly smaller than the internal guide (12) of the rocker member (7), as well as a second braking region (16), which adjoins the first region (17).
7. Hinge according to one of the preceding Claims, characterised in that the spring guide bar (6) comprises a third region (18) as the braking region, which adjoins the braking region (16) and whereof the cross-section or diameter is slightly greater than the internal guide (12) of the rocker member (7).
8. Hinge according to one of the preceding Claims, characterised in that the rocker member (7) is mounted on projections (8) of the housing connection part (1).
9. Hinge according to one of the preceding Claims, characterised in that the spring guide bar (6) comprises radially extending slots (19) in the braking region (16).
10. Hinge according to Claim 9, characterised in that the slots (19) are arranged opposite each other and offset laterally.
11. Hinge according to one of the preceding Claims, characterised in that in the braking region (16), in cross-section, the spring guide bar (6) comprises a central web (20) and curves (21) adjoining it laterally.
12. Hinge according to Claim 11, characterised in that provided between the end regions of the curves (21) and the central web (20) are resilient members (31, 32), which are preferably circular (31) or semicircular (32) in cross-section and are preferably integral with the curves (21) and/or the central web (20).
13. Hinge according to one of Claims 9 to 12, characterised in that radially extending ribs (22) are located in the slots (19).
14. Hinge according to Claim 13, characterised in that the curves (21) and ribs (22) lie diagonally opposite each other.
15. Hinge according to one of the preceding Claims, characterised in that in the region (23) of the compression spring (11), the spring guide bar (6) has a diameter which is slightly smaller than the internal diameter of the spring (11).

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