MXPA96003618A - Bisa - Google Patents

Abstract

The present invention relates to an elastic hinge arrangement, without a main film hinge, having a) a first hinge part, b) a second hinge part, which can assume a plurality of stable pivoting positions with respect to the first hinge part, a dead center that is at least between two stable pivoting positions, and which returns from each pivoting position between two such stable pivoting positions, including a dead center outside the same dead centers of a elastically in the closest stable pivoting position: c) two connecting arms, which are arranged at a distance apart and in each cas include at least one coupling element, which projects movably from a hinge part, cb) at least one substantial and flexural intermediate part, which is delimited by two regions of flexure, which comprises an angle to each other, characterized in that d) the regions d and bending have at the point where a separation distance approaches each other so that each connection arm is substantially free of stresses both in the position and in the closed position, e) in the relative pivoting of the second hinge part with With respect to the first hinge part between two stable pivoting positions including a dead center, each coupling element executes a maximal elastic relaxing motion in the region of the dead center.

Description

HINGE DESCRIPTION OF THE INVENTION The present invention relates to a hinge arrangement in accordance with the preamble of patent claim 1. For the coupled hinge connection, in particular of injection molded plastic closures in one piece, - or 'several designs are known. Generally, in the case of such one-piece plastic closures, two hinge parts that pivot with respect to one another are connected by a main hinge or a plurality of hinge resting on an axis (axial portions). To obtain an effect of snap closure on the actuating hinge, i.e. perceptible and defined opening and closing positions upon expiration of a dead center position, generally provides at least one additional intermediate element, a spring element, a stiff band or elements corresponding. These are disposed laterally of the main hinge, or in the case of a plurality of main hinges between them, and are connected to the two hinge parts. The intermediate elements or stiff bands in this case are arranged so that the hinge The main one rests outside the plane or planes defined by the connecting locations of the intermediate elements with the closing parts. This displacement of the main hinge with respect to the coupling sites of the intermediate elements (displacement of the joint axis) 5 leads during the opening and closing of the hinge to tension and compression forces, which are transferred and absorbed by the intermediate elements and the main hinge and achieve the closing effect under pressure. Such a functional principle based on a displacement * .- ^ a of the joint axis, in which the parts of the hinge pivot about a defined principal axis, rigidly arranged with respect to the hinge parts and the complementary functional elements undergo a geometric deflection with respect to their sites from Coupling in hinge parts is known, for example, from patent specifications DE 1813187, EP 0056469, CH 488085, EP 0447357 or patent applications EP 524275 and DE P 43 35 107.7 of 14.10.1993. In addition to the generally known problem of high or disproportionate material stresses (risk of ripping the material in the hinge region) an additional disadvantage of such a system is that, due to the required main film hinge, the spatial course of the movement of the hinge parts is go extensively restricted and, due to the necessary displacement, the -v main film hinges project beyond the contour of the closure. The mutual position of the parts of the hinge in the two rest positions, ie in the closed condition and in the open condition, and also during the movement does not have a significant influence, since a simple axial rotation takes place. In addition, the corresponding hinge arrangements bring with them various restrictions and limitations with respect to the aesthetic and geometric configuration of the hinge parts. The kinetics of such designs is greatly influenced by the actual configuration of the hinge parts, the material used and in the case of the plastic injection molded parts, by the actual production processes, the mold and by the production tolerances . It is not uncommon for such restrictions to carry designs that are not appropriate for the material, which are susceptible to production damage with respect to the service life in normal use. A design without a main hinge is known from the United States Patent 3,135,456. Two parts of a container that will pivot with respect to each other are connected to each other by an elastomeric projection attached to the outside. This design does not solve the problem of large material elongation, but apparently circumscribes them to the elastomeric, highly elastic material that is used. The hinge is subject to high loads of material and also presents an extremely unstable behavior, with an unpredictable inversion of the larger area. European patent specification EP 0 331 940 discloses a bistable hinge device that takes into account the above disadvantages in regions of importance. This hinge device prevents the main hinge from coming in direct contact with the two parts of the hinge. The parts of the hinge are connected to each other by two identical and symmetrical connecting arms, each of which includes two bracket arms, which connect the connecting arms to the hinge parts. The bracket arms are in turn connected to each other by a substantially triangular plate. The hinge arrangement according to this invention is distinguished by a relatively large opening angle and a press-on-closure effect on average, and despite a relatively rigid design, does not lead to excessive material tension. US-A-5 148 912 describes a hinge arrangement in which two hinge parts are connected to each other by means of connecting arms which are homogeneously flexible or elastic throughout their length. Due to the circular contour of the two hinge parts, the two connecting arms inevitably have a trapezoidal shape. This hinge according to the prior art has no rigid intermediate parts that have a trapezoidal shape nor coupling elements that are formed on the parts of the hinge. The known hinge therefore does not exhibit a good snap effect. That is, the open position and the closed position are not stable positions of the two parts of the hinge in which the latter automatically returns from the intermediate pivoting positions. O-A-92 13 775 describes a hinge arrangement in which the connecting arms are formed by spring elements or the like. These do not have intermediate trapezoidal parts nor coupling elements formed on the hinges. This hinge according to the prior art is also non-bistable in the sense mentioned previously. A similar hinge arrangement is described in O-A-84 04 906. In this case, the band-type connecting arms are flexible along their entire longitudinal dimension and do not include any substantially rigid trapezoidal connecting element. In addition, these connecting arms are located within the external contour of the hinge parts, so they are aesthetically unsatisfactory. The fact that this hinge does not exhibit a good closing effect under pressure is evident due to what was mentioned above.

It is an object of the present invention to provide a hinge arrangement, in particular for one-piece plastic closures, which while retaining the benefits of the aforementioned prior invention (EP 0 331 940) in relation to the stresses of materials, despite of extended opening angles of more than 180 °, presents low material loads and allows the spatial pattern of movement to be controlled specifically and there with [sci] greater degrees of freedom to be provided for the configuration of the hinge parts and its kinetics. This object is achieved by the invention specified in the patent claims. If the opening and closing movements of the plastic closures without a main shaft film hinge, as described in the aforementioned EP, are observed systematically, a complex spatial movement can be recognized. In spite of a good bistable behavior, the angles of opening intended to 180 ° can not be achieved in a tension-free manner, and additionally, a pronounced elongation of the connected arms can be observed in the dead center, in the transition of a position defined to the other. Depending on the material, the closing angle is greater than 0o and the opening angle is less than 180 ° (around 160 °). This means in the long-term behavior that the material '* - is constantly under tension outside the two defined positions with a minimum tension and under manipulation is subject to pronounced elongations, which in the case of plastics can eventually lead to training of 5 rips and, as a result, reduce the service life of such closure. If the process is observed carefully, it is observed that the transition in the two stable positions is accompanied by a process of investment in the material, although H light. Such reversal processes are material deformations that occur simultaneously in all spatial directions (such as a pressure-closing action toy frog), which temporarily leads to an unstable position and therefore rates the two stable positions 5 in both sides of the investment. In addition to this, there are design measures in the form of preformed bending sites, which contribute to controlling the movement process. It is evident that, in spite of an exact injection molding technique by which the "control members" are unforeseen, the intention to control the forces completely as one would wish can not be achieved. The vagabond forces, some even within the practical behavior of the material, present not only unsatisfactory mechanical properties, but additionally, also the phenomenon of erosion of the material, which obviously is undesirable. Probably the reason for this, is that during the design there is generally a tendency to control and monitor as much as possible [sic] and as a result a possible "cooperation" of the material, even driving towards the target, is not recognized and consequently not allowed. Instead of incorporating and using such a cooperative aspect, the entire process -j 'of planned movement is forced to (too) limited constraints. This is where the idea of the invention is presented. If the possibility of incorporating the inherent behavior of the material is given due consideration, a whole series of such "cooperative sequences" can be used, this being in conjunction with an accompanying control of the movement process, assisting in the sequence instead of affecting her too much. In the case of such modalities, the material, in the preferred embodiments the plastic, is allowed to move to where it has a tendency to move, and the control measures are arranged only where a specific movement has been planned. This latitude between rigid directions and a gentle guide has the effect of avoiding unnecessary tensions. Thus, the spatial movement sequence 5 is controlled in a specific manner and does not affect according to the design means, and as a result greater degrees of freedom are created for the configuration of the hinge parts, as required by the specified object . The teaching in accordance with the invention, 5 hereby resolves previous limitations and with the permissible material loads, makes it possible to open angles inter alia of more than 270 ° or even tristable angles. The structural considerations and examples of the embodiments of this invention are now explained with more , * detail in reference to the diagrams and figures listed below. Figure 1 and the diagrams of Figures 2 to 5 present us [sic] basic observations for an understanding of the invention. 15 Figure 1 shows the basic movement sequence and the geometry of a closing cover with a joint axis displacement. Figures 2 to 5 show diagram functions and also the opening and elongation angles in dependence on the design measures. The parameters are, as illustrated in Figure 1, L? 1, L? 2 [sic] and d. Figure 6 shows in a basic representation a first embodiment as an example of a one-piece plastic closure with connecting arms 5, arranged in parallel 25 and in asymmetry with respect to the plane of the closed closure.

Figure 7 shows an enlarged diagrammatic representation of the connecting arms 5 between the two closing parts of the hinge parts. Figure 8 shows the modality of the example in its open condition. The view looks inside the cover and the container. Figure 9 shows the connecting arm 5.1 of the hinge open from the side indicated in Figure 8, and Figure 10 shows the other connecting arm 5.2? ? of the hinge open from the side indicated in Figure 8. Figure 11 shows the two connecting arms 5.1 and 5.2 of the open hinge on the side indicated in Figure 8. Figure 12 shows a modality as an example of Figure 8 in the open condition. The view is viewed from the inside to the hinge, not from the back as in Figure 6. Figure 13 shows the movement of relaxation 20 according to the invention based on an example embodiment diagrammatically represented. Figures 14 to 19 show complementary modalities of the connecting arms 5.1 and 5.2 from the view as seen in Figure 12.

Figure 20 shows in a diagrammatic representation the sequence of movement of an exemplary embodiment with fold regions that run asymmetrically 9, 10. Figures 21a-21d show various embodiments of the coupling elements 6, 7. Figure 22 shows a mode as an example of a connecting arm 5 in a detailed, three-dimensional representation. Figure 23 shows an exemplary embodiment for closing the hinge region for closing coverage. Figure 24 shows a section through the band 15 according to Figure 23 along an intersection line B-B. Figure 25 shows an example mode with a low height of the closure cover. Figures 26-29 show an embodiment of the example of the invention. In the following embodiments as an example, the invention is explained in more detail by means of examples of one-piece plastic closures. The observations made and the clarifications that are presented can obviously be applied immediately to other applications or materials, in particular to materials of the card type.

In the case of the plastic closures, the two parts of the hinge are formed by the body of the closure or by a lower closing part and the closing cover. Figure 1 shows part of a basically conventional closure with a greatly enlarged junction axis displacement, seen from one side. The main film hinge 3, which connects the closure body 1 and the closure cover 2, is perpendicular to the plane of the drawing. An intermediate element 61 (in the case of certain closures, refers to O.Ü 'this as stiff band) is arranged here and this is a novelty, asymmetrically with respect to the plane of the closure V. If the intermediate element 61 is understood as a "set of parallel fibers", each fiber between the binding sites A- ^ and A2 consists of an upper portion h ^ (closing portion) and a lower portion L2 (portion of the closure body). Each fiber is at a certain distance d from the main film hinge 3. These parameters L1 # L2 and d are represented for the outer edge 62 of the intermediate element 61 in Figure 1. 20 The elongation of the material (depending on the actual design, also of compression) required by the principle of displacement of the joint axis, reaches its maximum in the region of the dead center. Since the relation ^ / L2 can vary (compare the slope of the sites of junction A ^ and A2), the elongation and the angle of opening Y "should be calculated individually for each fiber, however, this is not necessary for the basic considerations at this stage For a simplified consideration of the elongation and the angle of opening The parameters of the portion lengths L ^, L2 and the displacement of the axis d are sufficient, in practice, these parameters are generally: L ^ maximum = L2 maximum = approximately 3 mm (in the prior art always symmetric) and d = approximately 1 mm, These are daily dimensions of such a closure cap.A discussion is presented below with reference to Figures 2 to 5 of some diagrams showing details of the load cases, after the variation of the parameters discussed in relation to Figure 1. To simplify the representations, L-, is always normalized to the value 1. The other two parameters L2 and d are therefore specified in relation to L1. In the diagram of Figure 2, the angle of The opening and closing according to Figure 1 is represented as a function of the parameters. L2 varies from 0 L-j_ to 6 L-j_ and d varies from 0 h ^ a ^. The function, represented as an area, shows that, with a displacement of the increasing joint axis d and with the smallest possible portion L2, is theoretically a maximum opening angle, which, when L ^ L1 [sic] tends to 0 (L2 tends to zero) can theoretically be up to about 250 °. Since, up to now, great efforts have been required to achieve angles of opening of much less than 180 °, here 5 there is still the potential that, according to the teachings of the prior art, can in principle continue to be exploited. The principles with dimensionally elastic stiff strips (cf. German Patent Application No. P 43 35 107.7) point in this direction. J O The diagram in Figure 3 shows the elongation of the fiber in the dead center, which at the same time is the maximum elongation of the fiber. L2 in turn varies from 0 to 6 L ^ and d varies from 0 to L-j_. The function shows that, with the large opening angle, desired, that is, with a small portion L2, the elongation of the fibers of 40% and greater occurs even when there is a small displacement d. A comparison of the two diagrams shows that the maximum elongations occur in the same region where the opening angle would be optimal. Whether observes this region of interest more closely, the following is evident: The diagram in Figure 4 then shows the opening angle "*" as a function of the parameters only for the range of the opening angles greater than 180 °, that is, the range from 180 ° C to 250 ° is represented.

"'' • L2 varies from 0 to approximately 2 L-j_ and d varies from 0 to L, the area of the resulting function shows very well here, how narrow the design range becomes the greater the angle of opening and what large elongations are in this case, which is indicated in the following diagram. In the diagram of Figure 5, the elongation of the fiber is shown as a function of L ^ yd, representing the same function of the range as the diagram in Figure 4. It is evident from this, that elongations in the range 0 of interest, that is, f > at 180 °, they fall on 30% and for opening angles of 200 ° and greater they reach up to almost 80%.

This reveals that in fact an extremely narrow range (theoretical) is accessible for conventional solutions.

As can be seen, with an elongation of 30% actually 5 now impermissible, a restricted opening angle of only 180 ° and less results. Therefore, designs leading to such elongation should be avoided, and attempts should be made to find a way in which the design measures but also the cooperation of the material is used to achieve the objective. The European patent specification EP 0 331 940 already shows a form during which it can begin to solve the constraints of the conventional principle with the displacement of the joint axis. However, the solution according to EP 0 331 940 is based < "- strongly in purely geometric inversion processes, which allows little freedom to the closure kinetics.With the previous knowledge, the problems involved are sufficiently apparent to appreciate where the barriers of the prior art are located.

Where and how they are resolved is shown on the basis of a first example of the modality. Figure 6 shows a plastic closure that can be produced in one piece by the injection molding process and is, for example, injection molded of polypropylene (PP). Suitable as plastics for the invention are generally polymers, in particular thermoplastics, without additives and / or fillers of common use, which can be molded into flexible or resistant films or layers with thicknesses of typically 50-2000 μm which They are flexurally resistant in this way. The closure has a closure body 1 and a closure cover 2, which here form the two parts of the hinge. The closure is shown in its closed condition, ie the cover 2 0 rests against the closure body 1 in the region of the closure plane V. The closure body 1 and the cover 2 are simply connected by means of arms connection 5.1 and 5.2, which are preferably arranged in niches. The hinge arrangement according to the invention can consequently be designed without any protruding part outside the closure contour. In contrast to the known hinge arrangements with a main hinge and a joint axis displacement, here there is no additional hinge between the two connecting arms 5.1, 5.2, which would connect the closing parts 1, 2. This allows the body of closure 1 is designed, for example, with a band 15 projecting upwards. The cover 2 has the corresponding recesses, which in the closed state rest just against the band 15. This band 15 has a guide for the cover 2 and can be used specifically for the usual envocation [sic] (granted here) inside the closing. It can easily be seen that the weft 15 allows a wide design field to achieve an exact fit and accurate guiding positioning of the cover 2. Particularly preferred are also the convex up shapes, which make it impossible for the cover 2 to bend to the closure . It can be clearly seen in this figure that the hinge arrangement is configured without a main film hinge. The present invention specifically avoids a connection of the two closing parts by means of a geometric or physical main axis, which would restrict the movement of the cover so as to force a circular pattern movement in the individual points of the parts of the hinge to move.

The two connecting arms 5.1 and 5.2 each include a lower coupling element 6.1, 6.2, which is connected to the closing body 1, and in each case an upper coupling element 7.1, 7.2, which in each case j is connected to the cover 2. The upper and lower coupling elements 6.1, 6.2 and 7.1, 7.2 are connected by means of an intermediate part 4.1, 4.2 substantially and flexurally rigid. According to the invention, the coupling elements 6, 7, like the intermediate parts 1, are configured in such a way that these by a _ > side maintain the torsional stresses of the connecting points between the pivoting element and the coupling element as small as possible and on the other hand have a specific movement, that is, directed 5 (control) of the closing parts in the opening movement and close. In Figure 7, the two connecting arms 5.1, 5.2 are shown greatly enlarged. The two connecting arms are simplified here - without considering their thickness 0 and / or curvature - as two rectangles obliquely standing one with respect to the other and resting on two planes e- ^ and e2 arranged at an angle to one another. In this example embodiment, the connecting arms 5.1, 5.2 are symmetrically configured with respect to a plane of 5 symmetry s ^, perpendicular to the plane of the diagram. On the other hand, here there is no symmetry in relation to the longitudinal direction of the connecting arms. The lower coupling element 6.1, 6.2 and the upper coupling element 7.1, 7.2 of each connecting arm have a different shape. In contrast to the design discussed above according to EP 0 331 940, which operates with triangular shapes and symmetrical arrangements, here both coupling elements 6, 7 and the intermediate parts 4 have a trapezoidal shape. The trapezoidal, preferably asymmetric configuration then has as a result that the movement processes are not confined. According to the invention, it is not intended to restrict the kinetics of the closure to inversions, but rather by means of a trapezoidal configuration, the material properties are deliberately incorporated and, in particular, used to absorb the torsion and flexural forces. Preferably incorporated between the coupling elements 6, 7 and the intermediate parts 4 are straight bending regions 9.1, 9.2 and 10.1, 10.2, respectively. These bending regions 9, 10 are preferably designed as joining sites (regions of area or linear bending), for example, as thin bonding sites, in the case of plastic hinges in particular as film hinges.; however, as explained, they form only a significant part [sic] of the control elements. The closing plane (see Fig. 1), not shown here, is perpendicular to the plane of symmetry s1. An additional plane, parallel to the closing plane, is marked here by e3. According to the invention, the connecting arms are designed in such a way that, while preserving the properties of the material, a deflection movement of the connecting arms around the central region is achieved, in order to reduce or avoid excessive material stresses, particularly impermissible elongations. The dissimilar configuration of the coupling elements 6, 7 results in a virtual pivot axis which is substantially at the level of the line M, which is defined by the points of intersection of the bending regions 9.1, 10.1 and 9.2, 10.2, respectively. Here it is emphasized that this virtual pivot axis must not be confused with a geometric or even physical main axis, since the virtual pivot axis moves continuously during the complex three-dimensional motion process. This principle of deflection and relaxation is explained below based on various embodiments of the invention. The coupling elements 6 and 7, the separated bending regions 9 and 10, and the intermediate parts 4, arranged with each other, offer a wide variety of structural configuration. Depending on the positions, the length and the angle, these parts form "units of movement", which despite a large opening angle and open position and defined closed position have low tension only and consequently little elongation. When mention is made, however, of the elongation, it is assumed that the statement is also obviously related to the corresponding compressions, which occur depending on the structural design of the hinges. The cooperation of the material should be considered as constituted by the fact that the elasticities are used in several directions one after the other, step by step in conjunction with the movement of the two connecting arms. The bending regions 9, 10 support the defined movement of the hinge arrangement and concentrate the investment processes substantially in these regions. The other parts of the connecting arms 5 are inverted or bent only slightly or remain unfolded. The variations of the trapezoidal configuration according to the invention lead to possibilities and a kinetics that opens a new field in comparison with the known solutions. The teaching according to the invention makes possible, inter alia, opening angles of up to 270 ° or even closures having a plurality of stable positions, as explained in more detail below. This in contrast to the known stiff bands or the design according to EP 0 331 940 with triangular elements and two joining lines (fold lines). The invention consequently makes possible a plurality of stable pivoting positions of a first part of the hinge with respect to a second part thereof, there generally being a dead center in each case between two stable pivoting positions. For the purposes of the invention, consequently, it is not only intended to achieve that two (or more) stable pivoting positions are achieved, but that the parts of the hinge always return elastically from each of the pivoting positions [sic] of such dead centers thus providing one of the stable pivoting positions. In other words, not only a greater stability is sought, but a combination of additional stability with a spring or snap-lock effect. Figure 8 shows a modality in a condition fully open at 180 ° and largely free of stress. The view looks inside the cover and the container. The closing body 1 and the closing cover 2 are connected to each other by means of connected arms 5.1 and 5.2. For the closing, the closing cover 2 will be made out of the plane of the paper. The two connecting arms project out of the plane of the paper as two arches of a bridge. Depending on the length of the coupling elements 6, 7, which do not have to be equally long and depending on the angular position of the joining sites or bending regions 9, 10 and depending on the length of the connecting parts 4, the hinge behaves differently during opening and closing. Bending regions 11.1, 11.2, 12.1, 12.2, which make a wide, tension-free opening condition possible here, are also indicated. Figure 9 shows the connecting arm 5.1, which rises in the connecting form of a bridge and whose trapezoidal intermediate part 4.1 is tilted towards the observer so that he sees the same surface as in Figure 8, while the other connecting arm 5.2 the observer is presented in Figure 10 so that he observes the lower end of the intermediate part 4.2, inclined towards it. With the bow ß, the closing and opening movement is indicated. Figure 11 shows the two connecting arms 5, as they are presented to the observer, when he looks through them. It is evident that due to the bending regions 11.1, 11.2 (and 12.1, 12.2, respectively) that run obliquely to one another, they are laterally inclined with respect to each other. A double-headed arrow, designated by A, is intended to indicate a transverse movement with respect to the opening and closing movement designated by ß in Figure 9. This movement designated by A can best be described as a (acting here laterally) movement of lengthening / relaxation of dead center. While the stiff bands according to the prior art are only tensioned and act as a spring in one direction, the connecting arms 5.1 and 5.2 perform a mutually interactive loosening movement, which can be controlled within wide limits by the positional design of the bending regions 9 and 10 and by the linear dimensioning of the coupling sites 6 and y / o by means of additional bending regions 11, 12. The invention consequently provides special elongation-relaxing means for the coupling elements (or in their transitions), which present the required relaxation movement. By proceeding in this way, opening angles greater than 200 ° are obtained with stress-free positions and elongation below 10%, only the contractive force of the flexural film hinges of the connecting sites has to be applied, the tension elastic or with pressure in the connecting arms is of minor importance.

With the asymmetric configuration of the connecting arms 5 (Asymmetry with respect to the plane or s- ^, see Figure 7), the displacements of the pivoting movement are also possible, so that the closing cap rotates obliquely away to one side. A special advantage of the invention is that it is possible to influence the degree of movement of relaxation, and as a result, the effect of closing under pressure. Since the geometry of the closure portions 1, 2 does not have much influence on this, a predictable closure kinetics and a desired spring effect can be achieved selectively. Figure 12 shows the modality of Figure 8 in 5 the closed condition. The view looks from the inside towards the hinge, not from the back as indicated in Figure 6. Despite the complex spatial movements, mentioned in Figures 8 to 11, the two connecting arms 5.1 and 5.2 are, here in the closed condition, x Or simply straight conditions with a distance k, which can consequently be arranged as two common stiff bands. When turning to open, these connecting arms move without great tension, but with a different pressure closing effect, towards the shape of the bridge arch, as indicated in Figures 9 and 10, the compensating movement according to Figure 11 laterally deviated the excessive tension in the dead center during the opening and closing movement. This action is specifically supported by the additional bending regions 11, 12 mentioned. With reference to Figure 13, the lengthening / relaxing movement of the mentioned dead center is explained in more detail. Attached to a lower part 1 indicated diagrammatically, there are two connecting arms 5.1, 5.2, which are represented here only diagrammatically in two-dimensional form. To understand the movement of relaxation the elongation-relaxation elements, here the two coupling elements 6.1, 6.2 are important. If the connecting arms 5.1, 5.2 pivot from the position shown here (closed closing) outwards in the direction of the arrow B, there is in the central region M in the two connecting arms a comprehensive action induced by tension, which opposes the elongation which occurs on the outer edges of the connecting arms. The intermediate parts 4.1, 4.2, which are flexurally rigid in comparison with the coupling elements 6, 7, consequently have in the central region M, the tendency to deviate towards the interior of the closure in the direction of the arrows I -_ e I2. If this movement is avoided, then, as it is in the case in particular with the conventional closures with a displacement of joint axis, the elongations that are in the dimensions explained with reference to Figures 2-5, occur in particular in the outer edges of the intermediate parts 4.1, 4.2, or in the connecting arms 5.1. , 5.2. According to the invention, it is then contemplated that the coupling elements 6.1, 6.2 (or the upper coupling elements 7.1, 7.2, not shown in this figure) execute a loosening movement. As can be seen in Figure 13, not only forces acting towards the closing axis occur in the direction of the arrows I1 # 1-2, but also torsional forces in the direction of the arrows T- ^ and R2. The general tension condition of the arrangement comprises an overlap of tensile, flexural and torsional stresses. The invention has the effect that by means of a movement that absorbs both torsional and radially acting forces in the central region M, the damaging elongation forces, acting in the longitudinal direction of the connecting arms ^ -D 5.1, 5.2, are reduced or compensated. The means required for the movement of relaxation are formed by the additional bending regions 11, 12 and / or the configuration of the coupling elements 6.1, 6.2 (material cooperation, geometry). In this way, it is achieved that, in the relative pivoting of a second hinge part with respect to the first part thereof between two stable pivoting positions, including a dead center, each coupling member executes an elastic relaxing movement in the region of the maximum dead center. 20 If the elongation-relaxing elements are designed so that the stresses of the material are largely eliminated by the loosening movement, the spring forces are reduced and the closing effect under pressure is less. In the central region M, the banks The compressive arms 31.1, 31.2 of the connecting arms 5.1, 5.2 are under pressure, on the other hand, the external traction edges 32.1, 32.2 are subjected to tensile tension, the configuration according to the invention of the arrangement of the The hinge then has as a result that during the opening and closing movements are located in the inner region of the connecting arms 5, a neutral region N (absent or absolutely minimal tensile and compressive forces), which is represented here only for the arm 5.1 connector, as can be seen from - J Figure 13, this region is far in the direction towards the center of the connecting arm 5.1. The coupling elements are preferably configured such that the neutral region N is in the central third of the connecting arms 5. As a result, a tension profile is achieved balanced along the width b of the connecting arms and, as described, damaging material loads are avoided. Preferably, the elongation-relaxing elements, for example, the additional bending regions 11, 12, are consequently designed depending on the material and geometry, so that the elongations of material lie in the optimized regions, and thus the pressure closure effect is discernibly perceptible, but no excessive stresses occur.

The following figures show some preferred structural examples, in each case, represented from the perspective of Figure 12. These originate from a methodical diversity of variations, which have different load results and force flows and therefore, show in each Different properties case, which can be used according to the requirements. Figure 14 shows a modality with connection arms 5.1, 5.2, with an inward angle. The distances k1? k2 apart from the binding sites in the two elements 1 and 2 are equal. The bending regions 9, 10 are arranged on one side of the fold, when swinging from open to closed, the part of the cover 1 pivots substantially at the level M between the two connecting arms and adjusts in a stress-free manner to an angle opening greater than 200 °. Furthermore, it can be seen that the tension compensation movement becomes particularly large, which is advantageous with certain materials. In this embodiment, the additional bending regions 10.1, 10.2, 11.1, 11.2, are not required, since the coupling elements 6.1, 6.2, 7.1, 7.2, arranged obliquely have good torsional and flexural properties and therefore avoid excessive stresses in the material. Figure 15 shows a modality with connecting arms with an outward angle. The distances k- ^, k2 apart from the binding sites in the two elements 1 and 2 are unequal. The flex regions 9, 10 are in turn arranged on one side of the fold. By oscillating from open to closed, the part of the cover 1 pivots with an adequately large tension compensation movement at the M level between the two connecting arms and is adjusted in a substantially tension free manner to an opening angle greater than 200 °. . Figure 16 shows a modality with the connection arms arranged outwards. The distances k- ^, k2 apart from the binding sites in the two elements one and two are unequal, k- ^ > k2. When oscillating from open to closed, the part of the cover 1 pivots to the level M between the two connecting arms and adjusts to an opening angle of approximately 180 °. The tension compensating movement is smaller than in the case of the previous mode, but sufficiently adequate. Otherwise, k- ^ <; When not shown, the part of the cover 1 pivots with an opening angle of approximately 180 ° to a position below the base part 2. Figure 17 illustrates an embodiment with connecting arms arranged in parallel. The distances k- ^ k2 apart from the binding sites in the two elements 1 and 2 are equal. The bending regions 9, 10 are arranged relatively far apart, or the coupling elements 6.1, 6.2, 7.1, 7.2 have only a small (virtually triangular) length. By oscillating from open to closed, the part of the cover 1 pivots with a distinctive pressure closure effect towards the level M and adjusts to an opening angle of approximately 180 °. Furthermore, it can be seen that the tension compensating movement is small, and the bending regions 9, 10 remain slightly under tension. This may be just right for certain applications, to be specific where the part of the roof did not swing, for example, during movement. A large distance a between the bending regions 9, 10 is particularly advantageous also when the hinge parts must be spaced in an open 180 ° position. This obviously also makes it possible to influence the distance required for the injection molding [gap] in the injection position. Figure 18 shows a modality with the connecting arms arranged in parallel (k-j_ = k2) and with an asymmetric configuration of the coupling elements 6, 7, or an asymmetric positional design of the bending regions 9, 10 (different inclination of the connections (see asymmetry with respect to, s-cf. Figure 7), to be precise different angles in a connecting arm and different heights of the trapezoids with respect to the connecting arms, when oscillating from open to closed, the part of the cover 1 pivots with a distinctive pressure closing effect towards a position in a slope with respect to the part of the base.The movement takes place around an axis inclined with respect to the closing plane (cf. With this modality, it is only intended to illustrate the variety and the possibilities offered by the inventive solution All the modalities of Figures 14 to 18, illustrate the variants of the basic form with two connecting sites. utually inclined or flex regions 9, 10 j. ú to obtain the desired pressure closing effect without excessively lengthening the material. However, the opening angle can be further and significantly expanded by the invention if one or more connecting sites or bending regions 11.1, 11.2, 12.1, 12.2 are provided. Depending on the The material and / or design of the parts to be connected (cover / container), the joining sites or coupling elements 6, 7 present a particularly rigid design, so that the "opening cooperation" can no longer be applied virtually. It is then advantageous to provide one or two such complementary bending regions or hinge sites. This may have only one flexure function or an additional pressure closure function. Figure 19 illustrates a special embodiment with an additional inclined bending region, in the vicinity of the part of the hinge, here the closing body 1. The distances k? i, k? 2 [sic] apart from the binding sites in the two elements 1 and 2 are equal. The bending regions 9, 10 are arranged in a manner analogous to the case of other embodiments. The additional bending region 5 is formed by linear bending regions 11.1, 11.2, which connect the coupling elements 6.1, 6.2, with the joints 16.1, 16.2 of the closure body 1. In addition, additional bending regions 12.1 are supplied, 12.2, which connect the upper coupling elements 7.1, 7.2 to ju 'the closing cover 2. The joints 16.1, 16.2 are rigidly connected to the closure body 1. The additional bending regions 11.1, 11.2 are inclined so that they can execute the relaxation movement A that is explained with respect to Figure 11. The disposition of the connections or regions of flexure 9, 10, 11 can be compared to the shape of a z, that is, the lines have an alternate positive or negative inclination with respect to the edges of the connecting arms 5. If it is chosen that the slope of the regions of additional bending 11.1, 11.2 is relatively large (> at 45 °, as shown in the example of Figure 19), the hinge has an additional closing position. When opening from closed to closed, the closing cover 2 first pivots open around the flexing regions 9, 10, with a closing effect on pressure, in a manner similar to the case of the examples explained, and is adjusted to a first opening angle of approximately 180 °. If the cover is further displaced by the application of an additional manual force, a second pressure closing effect 5 occurs substantially around the flex regions 11.1, 11.2 and brings the closure cover to a second opening position of approximately 270 °. . The invention consequently makes possible three stable positions of the closing cover. Accordingly, the invention allows, in a totally novel way, a triestable hinge connection or (in the case of additional bending regions) multi-stable hinge connections, which to date, had not been possible by the known hinge of according to the previous technique. 5 If the connecting arms are connected only by regions of additional bending 11.1, 11.2 in a slightly inclined or horizontal manner by means of the joints 16.1, 16.2 or directly in the transitions to the hinge parts, a bistable opening 0 movement occurs in which the relaxation takes place by tilting the coupling elements 6.1, 6.2, 7.1, 7.2 outwards (cf., for example, Figure 10). As evidence, in the case of the modalities with joints 16.1, 16.2, the tension compensating movement is not adversely affected and the regions 9, 10, 11 are largely free of stress. The inclination of the bending regions 9, 10 or regions of additional bending 11, 12 is specifically used according to the invention to influence the sequence of movement in the sense of a smooth control and as a result, obtain advantageous opening movements. . At the same time, the mutual arrangement of the connecting arms 5 must be taken into consideration. Since the The hinge movement depends both on the inclination of the bending regions and on the mutual arrangement of the connecting arms 5, these parameters are preferably coordinated. The meaning of these parameters will be explained with Referring to Figure 20. This figure illustrates, again in diagrammatic form, two connecting arms 5.2, 5.2, arranged in a round closure body 1. The connecting arms shown here as planes (without thickness) have an overall angle o;. Two lines, perpendicular to the connecting arms, through the axis of the closing body, have an angle ex) = 360 ° -a. The bending regions 9.1, 10.1 and 9.2, 10.2 in each case, comprise an angle F. It can be easily demonstrated that the theoretically achieved opening angle depends on the The mutual relationship of the two angles [lagoon] and F. By means of a trigonomic calculation it can be shown that, with the coupling elements 6, 7, rigidly arranged perpendicular to the closing parts, the following condition has to be satisfied to achieve an angle of 5 theoretical opening of 180 ° (without considering the material influences): tan F / 2 = cos a / 2 = cos (180- a> / 2). Accordingly, for? = 90 °, for example, an angle F = 70.5 ° would be required. As explained in more detail above, an opening angle can be achieved much -i.-J greater if additional bending regions 11, 12 are provided, which allow a tension-free state in the open position. As already explained, flexural and torsional forces occur in an opening movement in the direction of the arrow B. Relevant here are the torsional forces FT1 and FT2 that also the flexural force FB1 in ° s lower coupling elements 6.1, 6.2 and also the torsional forces FT3, FT4, Fßl in the upper coupling elements 7.1, 7.2 . These forces are equal if the coupling elements 6, 7 have a corresponding shape, ie the bending regions 9.1, 10.1 and 9.2 and 10.2 are arranged symmetrically with the same angle ^ - - | _ and "V.2 in the arms of connection 5.1, 5.2 As can be seen from Figure 20, here the regions of lower bending 9.1, 9.2, preferably have a greater angle "X" than the upper bending regions 10.1, 10.2 This results in the corresponding forces FT1, Ft2 and FB1, acting on lower coupling elements 6.1, 6.2. they are smaller than the corresponding forces FT3, FT4 and F2, which occur in the case of the upper coupling elements 7.1, 7.2 As a consequence, in an opening process, a simultaneous bending around the flexion regions 9, 10, it is not achieved, but instead of this around the regions of j_? flexion 9, 10 is not achieved, but instead, the connecting arms 5.1, 5.2 move first around the bending regions 9.1, 9.2 and only after that around the regions 10.1, 10.2.This is used according to the invention specifically to influence the sequence of movement during the opening and closing processes. In the case of the embodiment of the example according to Figure 20, it is achieved, for example, that the upper closure cover (not illustrated here) first executes a pivoting outward movement substantially at the level of the mark M- ^ and, only after a delay, an additional pivoting movement in the region of the mark M2. The inventive idea of controlling the sequence of movement, while at the same time reducing the time of the elongation forces by the cooperative properties of the material, becomes clearer from Figure 20.

The selection of the angles "1 and 2 and also of the distance a apart from the bending regions 9, 10 leaves open a wide range of control for the kinetics of the hinge, Particularly advantageous are the arrangements of the flexion regions. , In which the axes of the regions of diagonally opposite movement are as tilted as possible.In particular, the diagonally opposite flexion regions 9.1 and 10.2 or the flexion regions 9.2 and 10.1 should be as far away as possible. -Ì.0 possible, not parallel and compensated as much as possible in the axial direction. This can achieve the effect that the overall behavior of the hinge is as stable as possible against twisting of the closing portions (in fact desirable torsional forces). With reference to Figures 21a-21d, additional possibilities are described to influence the processes of ,, movement and complementary examples of the dispositions of the functional elements. The cooperation of material according to the invention can be easily supported or influenced by additional structural measures. Figure 21a shows a lower coupling element 6.2, which has a slight convexity 20 transversally with respect to the longitudinal direction R. In a preferred design, this convexity corresponds to the local curvature of the part of the closing. The flexure region 9.2, disposed obliquely with respect to the longitudinal direction, preferably has a straight shape, but for special designs it can bend or exhibit a non-linear course. The intermediate part 4.2 also has a convexity 20 corresponding to the coupling element 5, 6.2. If the connection 9.2 is designed as a film hinge, the movement behavior is [sic] differs in comparison with the modalities described in detail above, essentially only in consideration of the convexity of the coupling element 6.2. The -i-O convexity 20 has the result that the coupling element undergoes a hardening with respect to the flexural forces Fßl. With respect to the torsional forces FT2, however, there is a lower resistance, so that the lengthening relaxation is achieved desired by a pivoting movement substantially in the direction of the arrow FT2. If connection 9.2 is achieved '' By means of a connection of elastic material, the movement process is additionally superimposed by a three-dimensional inversion process of the convex portions 6.2, 4.2. He The effect of snap closure can increase further with this. Figure 21b shows a coupling element 6.2 which is connected by means of a film hinge 9.2 to the intermediate part 4.2. The coupling element here has a straight, flat shape, but is reinforced in the central region by a rib 17 running in the longitudinal direction R. This rib 17 leads to a reinforcement of the material and a corresponding hardening of the coupling element 6.2 in the longitudinal direction . Correspondingly, a hardening can also be achieved in the longitudinal direction by a plurality of thin ribs. In an analogous manner, ribs or reinforcements of material presenting a hardening transversely with respect to the longitudinal direction R can be provided. In this case, the torsional movements of the coupling element 6.2 transversely with respect to the longitudinal direction R are largely eliminated and the coupling element 6.2 will execute in particular flexural movements in the direction of the arrow Fg-j_ • It is not necessary to say that such hardening can be used in combination with regions of additional bending 11, 12 (see for example Figure 19). Figure 21c shows an embodiment in which the coupling element 6.2 is connected by means of a film hinge 9.2 to an intermediate part 4.2. In order to be able to absorb the torsional and flexural forces by means of the coupling element 6.2, a thinning of the material is provided here in the upper region 18 of the coupling element. In order for the coupling element 6.2 to have a suitable general force, the thinning of material is preferably not supplied along the entire width of the coupling element but only where the torsional and flexural forces are greater. As a result, the forces and movements required for the lengthening relaxation are specifically absorbed by certain regions of the coupling element. The bending region 9.2 in this case must be formed so that only one region defined for the actual section around the connecting arm is used. This is achieved by transcending the thinning of the material in region 18 to connection 9.2 which presents a sudden change in material thickness. Figure 21d finally illustrates a mode in which the coupling element 6.2 has a material separation 19, or the coupling element consists of two parts. Such modalities are suitable in particular, in the case of relatively large hinges, to achieve the necessary flexural elasticity. The separations in this case are arranged so that the regions of force transfer are not influenced or only influence is exerted on them to the desired point. The separations in this case, as in this embodiment, can cover only part of the coupling element 6 or reach the flexion regions 9. It is not necessary to say, for example, for aesthetic reasons that for the purpose of saving material or influencing the kinetics of the hinge, the intermediate parts 4.2 can also have a corresponding separation of material. However, it must be ensured that it retains a certain rigidity of the intermediate parts 4, so that the sequence of movement according to the invention is ensured and that non-coordinated inversion effects do not occur. In a special embodiment, it is possible, while retaining the flexural rigidity of the intermediate parts 4, to increase the closing effect under pressure by a torsional spring action of the intermediate parts 4. The intermediate parts are consequently designed so that they are rigid flexurally in the longitudinal direction in relation to the coupling elements 6, 7 and do not allow buckling. In the transverse direction towards the connecting arms 5, the intermediate parts 4 are designed in such a way that they act in this direction as torsional springs, for example, when given a lamellar or rib shape. In this way, when a hinge arrangement is actuated the torsional moment of the intermediate parts 4 assists the spring force presented by the coupling elements. Figure 22 illustrates a detailed view of a connecting arm 5, in which, as in the case of the embodiment according to Figure 20, the coupling elements 6, 7, are arranged rigidly and perpendicularly with respect to the parts of closing. The arc of a bridge that results there in an open position of 180 ° of the parts of the hinge, not illustrated here, then exhibits the present shape. The angle F comprised by the bending regions is selected according to the invention so that in this open arc bridge position of 180 °, the connecting arm, in particular, the coupling elements 6, 7, is in a tension free status. In this embodiment, the coupling elements have a particularly preferred shape. The thickness of the wall of the coupling elements is reduced from the compressive edges 31.1, 31.2, visible from the front, to the traction edges 32.1, 32.2, which rest on the back in this figure. This achieves that the flexural and torsional properties of the coupling elements can be determined uniformly along the entire width b. The thickness of the wall is preferably contemplated so that the flexural and torsional properties produced through a finite region along the width b are as uniform as possible. In an approximation, the thickness of the wall is continuously reduced, the wall thicknesses at the compressive edges 31.1, 31.2 forming the same ratio as for the thickness of the wall at the traction edges 32.1, 32.2 than the heights of the traction edges and the compressive edges between them. If the external surface 27 of the connecting arm 5 adapts to the external contour of a closure, for example, it is in a cylindrical area, the inner end 21 of the coupling elements can be adapted to this outer contour or, as in the embodiment represented, run in a flattened area. Figure 23 illustrates a preferred embodiment for sealing the hinge region. A closing cover 2 with two coupling elements 6.1, 6.2 is shown, arranged rigidly and perpendicularly in the part of the closure 2. For the sake of clarity, the other regions of the connecting arms, that is to say, the intermediate parts and the elements of coupling, which are connected to the other closing part, are not shown. The coupling element has then cut into bending regions 9.1, 9.2. The closure cover has a round cross section, ie the coupling elements 6.1, 6.2 rest on the wall of the corresponding cylinder. Between the coupling elements a band 14 which is designed here in the form of a wall as part of the cylinder wall and rests within the outer contour of the closure can be seen. Connected to the band 14 are two thin walls or membranes 23.1, 23.2, which connect said band in turn to the external regions 24.1, 24.2 of the wall of the closure cylinder. The lower closure part or closure body may be equipped with membranes in a similar manner, so that by means of the band 14 and the membranes a dustproof connection is achieved in the region of the hinge. The magnitude of the membrane of the two closing parts is preferably made so that they touch or overlap each other. Instead of membranes 23.1, 23.2 which are disposed between the band 14 and the regions 24.1, 242. 0 of the closing wall, according to the invention, continuous membranes can be supplied between the regions 24.1, 24.2. It is important that these membranes do not adversely affect the functionality of the coupling elements, that is, they do not prevent the movement of relaxation according to the invention. Figure 24 illustrates a section through the +. band 14 of the mode according to Figure 23 along the line of intersection B-B. The closure body, not illustrated in this Figure 24, has a corresponding band 15 0 projecting upwards. To achieve a connection as tight as possible between the connecting arms, the two bands 14 and 15 overlap each other. As can be seen in the figure, the band 15 has a terminal cross section 26 in cross section, which corresponds to the terminal edge 25 of the band 14. So that the closure kinetics is not affected by the overlapping bands, According to the present invention, it is provided that the terminal edge of the band 15 has a substantially concave cross section, and that of the closure cover, which after all is turned outwards, has a substantially convex shape, to achieve a guide and seal as good as possible. It goes without saying that it is also possible to provide terminal edges of straight cross section for both bands. To achieve a reduced overall height of the closure, it is advantageous not to attach coupling elements in the closure body 1, in the closing plane V, but to move them outwards in the longitudinal direction along the generatrices of the closure. This measurement is illustrated in Figure 25. The coupling element 6.1 of a connecting arm 5.1 is arranged (partially) below the closing plane V. The cross section AA through the connecting arm clearly shows that in this way the elements of Coupling are formed by means of a cut-out 22, so that the coupling elements 6 can be movably projected according to the invention, to execute the loosening movement. In a corresponding manner, it is possible to move the connecting arms 5 further downwards and to integrate them almost completely into the closing body. This makes it possible to make a closing cover or a hinge part with a minimum overall height and design it, for example, as a flat plate. Figure 26 shows the example of a modality with a hinge arrangement integrated in the closure body 1. In the closed condition of the closure, the connecting arms, not visible in this figure, rest within the outer contour of the closure and are received by the recesses 28.1, 28.2. At the connection site between the closing arm and the closing cover 1, the latter has a very small minimum height or wall thickness. As can be seen particularly well in this representation, in this position of the closing cover 2 open at approximately 180 °, the hinge arrangement allows the cover to pivot quite back and down. In the longitudinal direction L of the closure, the closure cover then rests below the upper edge 29 of the closure body and allows easy access to the invoice 33. If a plurality of pivoting positions are provided, the closure in accordance with to the example of this mode, it also shows an opening of up to 270 °. The closure cover then touches its rear edge 34, and the outer surface of the container shown here. It is readily apparent that the bending regions 9, 10, and the additional bending regions 11, 12, should not be understood in a narrow sense of interpretation. Instead, for the hinge movement according to the invention, it is important, that the flexural rigidity in these flexion regions differ from the rigidity of the coupling elements, intermediate parts, etc., and presents a defined region around of the connecting arms 5 in the regions of area or linear bending 9, 10, 11, 12 (concentration of the relative effects of bending). The other parts of the connecting arms 5, on the other hand, should only be stretched lightly in order to achieve the relaxation of the elongation according to the invention. This ensures that the hinge executes a selected pivoting movement and that undefined inversion processes ("bounce movements") do not occur. For example, by using different materials (different modulus of elasticity) for the bending and intermediate regions, the solution according to the invention can be achieved in an equivalent way. In the same way, the required effect can be achieved and the required loosening movement can be achieved for example by the stiffness of the intermediate regions (for example, by ribs or special shapes). Since examples of embodiments with film hinges are mainly shown in the figures, the bending regions 9, 10, 11, 12 are shown only narrowly. If the bending regions are executed in any other way, for example materials with a high flexural elasticity, the bending regions will be correspondingly wider. It is also evident in particular, from Figures 9 and 10, that the bending regions 9, 10 generally experience greater effects of surrounding bending than any additional bending regions 11, 12 that may occur. The various bending regions therefore do not have identical bending properties, but, if required can have optimized features in a way that corresponds to their stresses. For special applications, combined embodiments having a region of flexure 12 without a closing effect under pressure at the cover closing end and an additional bending region 11 on the body of the closure can be devised. It goes without saying that the inventive idea also comprises solutions in which the coupling elements have additional connections (for example, support struts, radial or lateral) with the hinge parts, provided that the elongation relaxation movement is ensured for the intermediate parts 4. With reference to Figures 27 to 29, complementary embodiments of the invention will be explained in greater detail, using in an optimized manner the tension / compression profile that is produced transversely with respect to the connecting arms, which was already explained above. The closing effect under pressure of the closure is achieved according to the invention by the elastic deformations or the spring effect and the interaction of the elements of the connecting arms 5, that is, of the coupling elements 6, 7 and the element intermediate 4. An opening (and closing) of the closure, the decisive stresses for the closing effect under pressure are produced on account of the arrangement and configuration of these elements 4, 6, 7 according to the invention. As described with reference to Figures 13 and 20, the torsional stresses acting on the coupling elements 6, 7 occur around the longitudinal axis of each of the connecting arms 5. Along the shorter side of the elements of coupling, in the traction edge 32.1, a traction region accumulates, and along the longer side of the coupling elements, on the compression edges 31.1, a compression region (longitudinal tension) is accumulated. Because of the function, these tensile and compressive stresses are greater in these outer edges 31.1, 32.1 of the connecting arms 5. The torsional and longitudinal stresses are coupled together and accumulated by a linear load, which is introduced in the intermediate elements 4 in the bending regions 9, 10. This charging process can be easily understood if a vectorial consideration is made and the forces along the load line are interpreted as components of the torsional and tensile forces / compressive In the consideration of the balance of forces, it is quickly evident that here the intermediate elements 4 are essentially loaded only by forces in the direction of the longitudinal axis of the connecting arms and, when actuating the closure, have the traction and compressive regions that were described above, covering the tensile forces mainly on the longer side of the intermediate element 4, on the traction edge 32.1, and compressive forces occur on the shortest side, on the compression edge 31.1. As can be seen from Figures 27-29, these longitudinal forces are introduced from the bending regions 9, 10, eccentrically to the intermediate element 4, that is, in these configurations, the film hinges are joined in the region of the outer surface, not visible here, of the intermediate elements 4. In view of such eccentricities, a second flexion may occur on the compressive edge of the intermediate elements 4, but this is largely avoided according to the invention. The flexurally rigid configuration of the intermediate elements 4, according to the invention, is therefore important.

Represented in Figure 27, there is a particularly advantageous embodiment of the coupling elements, which uses the tensile / compressive ratios very well. The coupling elements 6, 7 are designed in an inverted reflex manner, and consequently, by virtue of their symmetry, they lead to identical tension. The coupling elements 6, 7 acting as spring elements have a relatively solid band-like configuration in the compression region towards the compressive edge 31.1. As a result, disadvantageous buckling of the coupling elements is avoided. On the other hand, the traction regions of the coupling elements on the traction edge 32.1 become much thinner and therefore can act optimally as tension, bending and torsion springs. As in the case of the previous modalities, the intermediate element 4 is given a uniform stiffness. Figure 28 then shows a mode in which the intermediate element 4 has a wall thickness that varies along the width of the connecting arms. In this case, it is important that, according to the invention, the intermediate element nevertheless acts as a substantial and flexurally rigid plate, that is, that this variation of the thickness of the wall does not lead to any bending of the intermediate elements when actuating The hinge. It can be seen very well that, in the compression region on the compressive edge 31.1, the intermediate element is of a solid design, to avoid buckling or bending. In the longer edge of the intermediate element 4, that is to say, in the traction edge 32.1, the thickness of the wall is, however, reduced, for example to 1/3 or 1/4 of the wall thickness in the region compressive, and allows an increase in the effect d general system spring, assuming this region the function of a tension spring. In the case of relatively small PP closures, this traction region, for example, can be designed as a thin film of, for example, 0.25-0.5 mm. It should be noted once again here that the intermediate element retains its function as a flexurally rigid element and the occurrence of undesirable deformations due to bending must be avoided. Accordingly, during the actuation of the hinge, bending of the intermediate element 4 along the traction edge 32.1 does not occur either. The coupling elements 6, 7 have here a substantially rectangular cross section and a wall thickness which is greater than the wall thickness of the intermediate element in the traction region at the traction edge 32.1 (cf. proportions of the wall thickness in Figure 28). Figure 29 then shows an example of a modality that has a favorable spring behavior, in that it includes the characteristics of the modalities according to Figures 27 and 28. Both the coupling elements 6, 7 and the intermediate elements 4 they have in the region of the compressive edge 31.1 a solid wall thickness and therefore prevent buckling. On the other hand, the traction edge region 32.1 is greatly reduced and participates in the spring effect, as described above. The cross sections of the coupling elements 6, 7 and of the intermediate element 4 correspond in this example. It is also important in the case of this embodiment that the intermediate part 4 have a geometry to maintain the intermediate part 4 flexurally rigid during the actuation of the hinge. The transition between the different thicknesses of the wall may be relatively abrupt, take place along a relatively wide region or, at different places in the longitudinal direction, depending on the desired spring behavior. The features to which reference is made can be advantageously combined with other additional features of the invention presented above. Having described the reference as above, property is claimed as contained in the following:

Claims (31)

1. An elastic hinge arrangement, without a main film hinge, having: a) a first hinge part; b) a second hinge part, which can assume a plurality of stable pivoting positions with respect to the first hinge part, a dead center that is at least between two stable pivoting positions, and which returns from each position of pivoting between two such stable pivoting positions, including a dead center outside the same dead centers in an elastic manner in the closest stable pivoting position; c) two connecting arms, which are arranged at a separate distance and in each case comprise ca) at least one coupling element, projecting movably from a hinge part, cb) at least one intermediate part substantially and flexurally rigid, which is delimited by two regions of flexure, comprising an angle to each other; characterized in that d) the bending regions have at the point where a separation distance is closer to each other so that each connection arm is substantially free of stresses both in the position and in the closed position; e) in the relative pivoting of the second hinge part with respect to the first hinge part between two stable pivoting positions including a dead center, each coupling member executes a maximum elastic relaxing motion in the region of the dead center.

2. The hinge arrangement according to claim 1, characterized in that the bending regions, have at the point at which they are closer to each other a separation distance, so that each coupling element, extends in the open position substantially perpendicular to the closing plane of the hinge parts.

3. The hinge arrangement according to claim 1 or 2, characterized in that the angle F that is comprised by the bending regions has a value that satisfies the following formula: where F is the angle formed between the flexion regions,? is the angle that is formed by two lines running penpendicularly in the connecting arms and Y is the effective opening angle.

4. The hinge arrangement according to claim 3, characterized in that the angle F has a value corresponding to the following formula: = 2-ArcTan (Cos a / 2) where the angle o. is the angle comprised by the connecting arms.

5. The hinge arrangement according to any of the preceding claims, characterized in that the bending regions have unequal angles ("V- ^ 2 'with respect to the edges of the connecting arms.

6. The hinge arrangement according to any of the preceding claims, characterized in that the connecting arms are connected to two hinge parts by means of additional bending regions arranged substantially transverse with respect to the connecting arms.

7. The hinge arrangement according to any of the preceding claim, characterized in that the connecting arms are designed asymmetrically with respect to the closing plane of the hinge parts.

8. The hinge arrangement according to any of the preceding claims, characterized in that the connecting arms run in a folded manner, resting in a plane and are arranged over part of their length parallel to each other so that they have opposite ends spaced at different distances (k- ^, k2).

9. The hinge arrangement according to any of the preceding claims, characterized in that the thickness of at least one coupling element varies such that the flexural and torsional stresses are substantially the same over the entire coupling element.

10. The hinge arrangement according to claim 9, characterized in that the thickness of the coupling element decreases continuously from its longest lateral edge to its shortest lateral edge.

11. The hinge arrangement according to any of the preceding claims, characterized in that in the pivoting of the second part of the hinge, each coupling element is under tensile load on its longer lateral edge under compression stress on its lateral edge more short, in such a way that a neutral voltage region (N) is placed between the two lateral edges.

12. The hinge arrangement according to claim 11, characterized in that the neutral region (N) is placed in the third center between the two lateral edges.

13. The hinge arrangement according to any of the preceding claims, characterized in that at least one coupling element has a convexity particularly for its longitudinal direction (R)

14. The hinge arrangement according to any of the preceding claims, characterized in that at least one coupling element has at least one reinforcing flange that changes the bending stiffness.

15. The hinge arrangement according to any of the preceding claims, characterized in that at least one coupling element has a thin material that changes the bending stiffness.

16. The hinge arrangement according to any of the preceding claims, characterized in that at least one coupling element has a spacing that changes the flexural stiffness.

17. The hinge arrangement according to claim 16, characterized in that the coupling element is formed of two parts containing the space.

18. The hinge arrangement according to any of the preceding claims, characterized in that at least one intermediate part is designed in such a way that it is flexurally rigid in the longitudinal direction of the coupling elements, but as a torsion spring in the transverse direction to the.

19. The hinge arrangement according to claim 18, characterized in that the coupling element is designed with sheets or ridges running in the longitudinal direction.

20. The hinge arrangement according to any of the preceding claims, characterized in that the connecting arms are arranged, observed from the outside, in front of the straight formed membranes, along the inner surface of the hinge parts.

21. The hinge arrangement according to claim 20, characterized in that the membranes of the two hinge parts touch or overlap in the closed position.

22. The hinge arrangement according to any of the preceding claims, characterized in that a band is arranged on at least one of the hinge parts between the connecting arms.

23. The hinge arrangement according to claim 22, characterized in that in the closed position, the band projects beyond the closing plane in a recess in the other part of the hinge.

24. The hinge arrangement according to claim 22, characterized in that the bands, which touch or overlap each other, are provided in both parts of the hinge between the connecting arms.

25. The hinge arrangement according to any of the preceding claims, characterized in that the termination edges of the two parts of the hinge are placed between two overlapping connecting arms.

26. The hinge arrangement according to claim 25, characterized in that the termination edges of the two parts of the hinge are placed between the two connecting arms, has regions which are of convex and complementary concave shape.

27. The hinge arrangement according to any of the preceding claims, characterized in that at least one of the connecting arms is attached to the hinge part assigned below the closing plane and is lifted from the hinge part by a guide notch. .

28. The hinge arrangement according to any of the preceding claims, characterized in that in the closed position, the connecting arms are housed in at least a part of the hinge by the recesses.

29. The hinge arrangement according to any of the preceding claims, characterized in that it is bistable and for this purpose, each connecting arm has two interior flex regions and an intermediate portion.

30. The hinge arrangement according to one of claims 1 to 28, characterized in that it is triestable and for this purpose, each connection arm has three interior flexion regions, with positive and negative inclination alternately with respect to the lateral edges of the arms of connection.

31. The hinge arrangement according to any of the preceding claims, characterized in that the intermediate element has in the tension region, close to the tension edge, a wall thickness, which is reduced in comparison with the compression region near the edge of compression and acts as a tension spring. SUMMARIZES A hinge, preferably made of plastic materials, having two connecting arms (5.1, 5.2) which are arranged at a distance (kl, k2) apart which are connected to a part of the lock (1) and to the body of the lock (2). Each connecting arm has at least one rigid intermediate part (4) and a coupling element (7) which executes a relative movement. The coupling element (7) protrudes movably from its corresponding part of the hinge (1, 2). Two regions of flexion (9.1, 10.1, 9.2, 10.2) which form an angle with which they are delimited one from the other by the intermediate part (4). The connecting arms (5.1, 5.2) may or may not be parallel to each other or be indented in a plane. When they are lowered, the connecting arms move to the figure of the arch of a bridge, without extensions of long material, a compensating movement that deflects the excess tension later in the dead center. As a result of an additional bending region (11.1, 11.2, 12.1, 12.2) with or without a movement effect, in each connecting arm, the opening angle is substantially increased and a tri-stable or multistable opening or lock , as desired, it is achieved.