MXPA00010740A - Coordinated multi-axis hinge and closure using the same - Google Patents

Abstract

A coordinated multi axis hinge arrangement provides a snap action between stable open and closed states. When the hinges operate between the stable open and closed states across a dead center position, resilient forces imparted by torsionally rigid connecting elements (33.1, 33.2) of the hinge to adjacent hinge parts such as body and lid elements are transferred by coupling or transmitting areas (45.1, 45.2) adjacent the bending regions (34.1 - 34.4) or film hinges to remote resilient deformation energy storage areas (40.1 - 40.3). As the inge passes a dead center position, this energy isin turn supplied and returned to the rigid connecting elements to impart snap action to the closure. The closure may be cast as a single piece of plastic material and may be cast in the open position.

Description

COORDINATED MULTIPLE HINGE AND CLOSURE MECHANISM USES THE HINGE Field of the Present Invention In general, the present application relates to a spring hinge; in particular, to a hinge that can be used in a one-piece injection molded plastic closure system. Background of the Present Invention The elimination of consumable materials, such as cosmetics and foods, creates the need for closure systems for elimination that can be manufactured economically and that the container is closed completely hermetically when they are in the closed position. Because such closure systems are often used in disposable containers for consumer goods, the cost of such closure systems is of paramount importance, as is the desire to have closure systems that are of excellent convenience to the consumer. and give good feeling to the touch. In the many closure systems of the past, a first class of locking systems was often employed that used a single main hinge connection or a number of main hinges aligned along a single axis. Some of these hinges employ an intermediate element, such as a spring element or a taut band, in order to produce a neutral position, in which the tension within the closure system prevents the system from rest stably in its position, making the closure system either fully open or completely closed. In general, such a position of unstable equilibrium is considered advisable in closure systems of this type, since the consumer provides a closure system that gives a good overall feeling to the touch. However, those closure systems of the single main hinge type, even provided with such an intermediate element, demand a significant de-centering of the main hinge with respect to the contour of the closure system, due to the simple movement of the cap, as illustrated in figure 3 of the present application. These hinges are also difficult to mold, due to the asymmetric trajectories of the flow during molding. This, consequently, places the hinge well outside the body of the closure system, which is not considered advisable in such closure systems. Also, those closure systems of the single main hinge type are also often difficult to mold. Examples of such devices employing a single main hinge are those disclosing U.S. Patent Nos. 4,403,712, issued to Isinger, and 4,638,916, issued to Beck: et al. A second class of hinges employs a hinged arrangement with multiple articulated axes. However, in this class of hinges the opening and closing of the multiple joints are not coordinated in this kind of hinge. An example of an uncoordinated hinge is U.S. Patent No. 5,148,912, issued to Nozawa, in which two hinge parts are connected together by means of two non-hysteresis tapes that are flexible or elastic throughout their length. In such a closure system, the hysteresis-free tape plates connecting the hinged cover to the body are folded or bent over their entire length, in order to produce a force that brings the hinge to a single stable position; beyond that, the hinge is continually subjected to effort. The lack of coordination between the multiple axis of the hinge allows the cover to move along multiple trajectories with respect to the closure system, there being no coordination between the parts of the closure system. A third class of hinge are coordinated multi-axis hinge arrangements that, in general terms, rotate around two hinge axes and are designed with two stability positions that typically lack tension, both providing a dead center, or unstable equilibrium position. In such a hinge, a centering force tends to bring the hinge to a stability position, of two, from the neutral position. It is believed that these hinges are the invention of an inventor of the present application, and are better described in U.S. Patent No. 5,794,308 entitled Hinge (Hinge). Although at that time invention 308 was created, the model shown in Figure 1 of the present application was not known, the invention corresponding to the patent 308 can be described, in general, with reference to this model. Such hinges employ a pair of hinge elements comprising an intermediate hinge piece 4, which is rigid in the flexural aspect and is engaged in the first and second hinge parts, typically in the body and lid of an enclosure, by means of coupling elements 6, 7, which provide an elastic displacement of relief in the region of a neutral position. In other words, in the patent 308, coupling elements that are connected directly with the intermediate hinge part that is considerably rigid in the flexion, absorb the elastic deformation to produce the spring action forces in the region of the position of deadlock. Although the teachings of the patent 308 provide an excellent closure system, from the time of the invention of this patent the inventors of the present application discovered various ways to vary and improve the performance of the hinges of the type on which it runs in Patent 308. The Invention Accordingly, an object of the present invention is to introduce improvements in the design of the aforementioned hinges to, at least in part, transfer the deformation forces created by the rigid intermediate portions in the inflectional aspect or in the the torsional, or connecting arms, towards an elastic zone, or more than one, which facilitates the storage of this energy away from the coupling elements or areas with which the connecting arms that are rigid in the inflectional direction are connected. It is another object of the present application to increase the capacity of the closure system to absorb the elastic energy coming from rigid connecting arms in the torsional direction, by transferring part of that energy, or all of it, to areas that are not directly adjacent to it. the bending areas with which the connecting arms are connected, thereby improving the elastic force by spring action that comes from a particular receptacle geometry, especially in those relatively small closing systems.

According to the concepts of the present patent application, the first and second hinge parts are connected with at least two connection arms that are separated from one another and are connected to the hinge part by means of regions of bending. The connecting arms are substantially rigid in the torsional and the connecting arms, when the closure system passes from one state of stability to the other, imparts elastic forces to one of the first and second hinge parts, or both. Then, these forces are transferred, by means of coupling or transmission zones, to an elastic storage zone, or to more than one, which preserve the deformation forces in the form of elastic energy due to bending. Although these coupling or transmission zones can themselves be elastic and conserve energy, as contemplated in the '308 patent, the practical embodiments of the present application transfer some or all of this energy to elastic areas that are at a distance from the bending areas. According to further teachings of the present patent application, the offset of the hinge with respect to the line of separation between the body and the lid of the closure system can be varied, in order to achieve desirable effects, such as, in a of the practical embodiments, providing a closing mechanism and, in another practical embodiment, avoiding interference between the lid and the body during closure, even in the presence of protrusions protruding from the body of the closure system or by unusual shapes designed in the inside of the lid of the closing system.

According to still further teachings of the present application, the molds that are used to produce a coordinated arrangement of multi-axis hinge as described, can be designed to compensate for the contraction of the mold in the body, the cap and the arms. of connection and, even so, continue producing the geometry that is desired. Optimal thin-film hinges operate as efficient flex zones for the hinge. The achievement of the objectives of the present application will become more evident from the detailed description given below, in virtue of which the spirit and the general scope of the present invention will be obvious to those skilled in this technology. It should be understood, however, that the specific examples and descriptions given hereinbelow are merely to serve as an example of the present invention, which is described solely by the appended claims. BRIEF DESCRIPTION OF THE DRAWINGS The present invention will be understood more fully from the detailed description given below and the accompanying drawings, which should not be considered limiting of the invention described in the appended claims. Figure 1 illustrates a mechanical model of a multi-axis hinge coordinated arrangement, which is of the kind that is employed in the practical embodiments of the present patent application; Figure 2 illustrates the specific coordinated displacement of the multi-axis hinge arrangement shown in Figure 1; Figure 3 is a family of kinematics curves showing typical trajectories of a plurality of points in space, rotating around a main hinge connection of the type known in the prior art; Figures 4a) to 4c) each show a family of kinematics curves of various coordinated multi-axis hinge arrangements, of the type illustrated in Figures 1 and 2; Fig. 5 illustrates, schematically, a practical embodiment of a multi-axis hinge arrangement in a closure, according to one of the practical embodiments of the present application; Figure 6 is an approximate view of part of the schematic "" practical embodiment of Figure 5; Figure 7 is the illustration of the practical embodiment of Figures 5 and 6 of the present application, where an arrangement of energy storage dampers, as used in accordance with the teachings herein, is shown in greater detail. request; Figure 8 illustrates a practical embodiment of the present application, wherein an alternative arrangement of buffers for energy storage is employed, in accordance with the teachings of the present application; Figure 9 illustrates a practical embodiment of the present application, which has curved areas of flexure; Figure 10a), 10b) shows trajectories of specific points of a hinge in space, which restricts the first and second hinge parts to interfering trajectories (Figure 10a) and which avoid interference (figure 10b); Figure 11 and Figure 12 are perspective views illustrating additional practical embodiments of the hinge object of the present application, where the principles explained with reference to the figures are employed 10a), 10b); Figure 13 is a side view of yet another practical embodiment of a hinge made in accordance with the teachings of the present application; Fig. 14 is the side view of another practical embodiment of a multi-axis hinge arrangement according to the present application, wherein the manufacturing principles for contraction compensation are illustrated; and Figures (15a) and (15b) show the cross section made through an improved film hinge, which was made according to one of the aspects of the present application, in the open (Figure 15a) and closed positions. (figure 15b). Detailed Description of the Preferred Practice Embodiments A better understanding of the present invention can be obtained through examination of the present detailed description which, when examined in connection with the accompanying drawings, expresses preferred embodiments of the inventions described at the moment. It should be understood that, in the various figures, like elements are identified, generally, with the same reference numbers. In the course of developing various coordinated multi-access hinge arrangements, the inventors discovered that such a hinge can be described in reference to the mechanical model 1 of the multi-axis hinge coordinated arrangement illustrated in Figure 1 of the present application. . The mechanical model 1 of the multi-axis hinge arrangement was discovered by the inventors as a way to describe the operation of the multi-axis hinge coordinated arrangement in its most general or basic form. The mechanical model 1 of a coordinated multi-axis hinge arrangement comprises a lower, or first, hinge part; an upper part, or second part, of hinge; and, at least one, connecting arm 4, connecting the lower part, or first, hinge 2 with the upper part, or second, hinge 3, by means of a first and a second axis of 5 and 6 rotation. Note that, while in the practical embodiment of Figure 1 these axes are illustrated as being in a parallel position, it is possible to place them obliquely to each other, in either of the two dimensions. A coordination device 7 provides coordination for the multi-axis hinge arrangement. In the mechanical model of figure 1, the coordination device is represented by means of two pairs of conical wheels 8,9 which mesh with each other, and a transmission or gearbox, 10, which can have any suitable coupling ratio. , which allows the speed of rotation of the hinge around the first and second axes of rotation 5 and 6 to differ according to the transmission ratio chosen for the gearbox 10.

Alternatively, as may be desired to achieve special effects, the transmission ratio of the gearbox 10 can be made non-linear. However, it falls within what the present invention contemplates that some defined coordination exists between the rotation of the lower and upper parts 2,3 of the hinge, with respect to the connecting arm 4. Figure 2 illustrates how the displacement is coordinated between the lower part 2 of the hinge, the connecting arm 4 and the upper part 3 of the hinge, according to a coordinated multi-axis hinge arrangement of the type disclosed in the present application. In the example of Figure 2, the gearbox 10 of the coordination device 7 exhibits a ratio of 1 to 1. Figure 2a) shows the multi-axis hinge arrangement 1 in the closed position: Figure 2d) shows the arrangement 1 of hinge multieje open completely, with the upper and lower parts of the hinge open at 180 ° with respect to each other. Figures 2b) and 2c) shows the arrangement 1 of the multi-axis hinge in intermediate positions. Collectively, these figures illustrate how the coordination device 7 ensures that the relative displacement between the lower part 2 of the hinge and the connecting arm 4, on the one hand, and the upper part 3 of the hinge and the connecting arm 4, on the one hand, the other, always be coordinated with each other. Although the gearbox 10 is represented with a transmission ratio of 1 to 1 in this illustration, which results in the symmetrical rotation of the upper part 3 of the hinge about the axis of rotation 6, compared to the lower part 2 of the hinge about the axis of rotation 5, a different gear ratio can be chosen for the gearbox, in order to vary the speed of angular change that occurs in the pivots 5, 6. In contrast with the coordinated displacement of a multi-axis hinge coordinated arrangement as illustrated in Figures 1 and 2, the multi-axis hinge-free arrangements are unstable because, at least one, degree of freedom remains undefined. If the coordination device 7 is removed from a multi-axis hinge, the relative displacement of the two parts 2,3 of the hinge with respect to the connection arm 4 can not be established. The upper part 3 of the hinge can be completely opened with respect to the connection arm 4, before the lower part 2 of the hinge begins to open with respect to the connection part 4. In this way, in a device with no coordination, a particular position in the space can be reached by means of multiple displacement trajectories.

Figure 3 illustrates the trajectory of a rectangle that moves through the space under the compulsion of a single hinge connection 21. This so-called kinematic representation illustrates the displacement of various points of the rectangle 20 when it rotates through the space around the main connection 21 of the hinge, following the path Pl. This is representative of a first class of hinges, in which a single pivot hinge is used. The main hinge connection 21 is, in the example of figure 3, perpendicular to the plane of the figure. Thus the rectangle 20 moves from a first position 20.1 to a second position 20.2. the trajectories Pl of all the points of the rectangle 20 are circular in this example, in which the two rectangles 20.1 and 20.2 are connected directly by means of the main connection 21 of the hinge. In the case of closures, it is desirable to remove a lid, such as the one represented by the rectangle 20, to an opening position that is well away from the body of the closure. In such an arrangement of only one hinge, the main connection 21 of the hinge has to be well separated from the container so that this objective can be achieved. This produces a sensitive protrusion from the closure body, appearance of those closures with a single hinge that is considered undesirable. A completely different concept of the coordinated multi-axis hinge arrangement is evident from the examination of Figures 4a) to 4c). The review of the kinematic representation of these figures, in comparison with the kinematic representation of a single hinge, as illustrated in Figure 3, clearly shows the functional advantages of a multi-axis coordinated hinge. Figure 4a) shows a first typical trajectory pattern P2 of points within the rectangle 22, when it rotates 180 'around a multi-axis hinge arrangement 1 such as that illustrated in Figure 1, for example. It is obvious that, because there is no main hinge, the rectangle 22, in the closed position 22.1, is displaced by the multi-axis hinge coordinated arrangement 1, leading it to the open position 22.2. it is clear that the trajectory P2 pattern is not circular. Thus, in this example it is evident that a coordinated multi-axis hinge arrangement can be designed to prevent one of the elements from interfering with other specific elements. By modifying the distance of the rotation axes 5,6 in the space and the transmission ratio of the coordination device 7, a sensible effect on the trajectory pattern can be obtained, and practically any desired trajectory can be realized. Examples of two possible further trajectory patterns are illustrated in the kinematic diagrams of Figures 4b) and 4c). It is very important to understand that the considerable contact between the upper and lower parts of the hinge or, in a practical example, a closure employing a hinge such as that illustrated in Figure 1, should be avoided in general, to achieve movement that is sought. (However, compare figures 10a and 11, which make use of a Intentional interference to produce a bolt action.) From Figures 4b and 4c it is clear that, compared to a single main hinge connection, such as the one illustrated by the kinematics of Figure 3, many different requirements can be met. by adjusting the parameters of a coordinated multi-axis hinge arrangement, as taught herein. Figure 5 shows, in schematic form, a practical embodiment of a multi-axis hinge coordinated arrangement 1 in a closure 30. As with the other practical embodiments described in the present application, the displacement and coordination of the arrangement of The multi-axis hinge is similar to the one described above, in the mechanical model of Figure 1. The closure 30 is drawn in the semi-open position, and is useful for defining several of the expressions used in the present application. The closure comprises a body 31, corresponding to the lower part 2 of the hinge of figure 1; a cover 32, corresponding to the upper part 3 of the hinge of figure 1, and two connecting arms 33.1, 33.2, spaced at a distance apart and separated by a slit, the connecting arms 33.1, 33.2 corresponding to the parts 4 intermediate rigidities in the inflectional aspect, of the practical embodiments of the US patent number . 794,308, which was mentioned above, and connective elements 5 of our International Application number PCT / EP96 / 02780, which is co-pending. Each of the connecting arms 33.1, 33.2, of Figure 5, is connected to a coupling part of the body 31 and of the cover 32 of the closure 30, by bending regions 34.1 -34.4 which, in a practical embodiment preferably, They can be movie hinges. The bending regions 34.1 - 34.4 Be have in this practical embodiment such that each connecting arm 33.1, 33. 2 has trapezoidal shape. Although the regions of flexion are shown arranged symmetrically in Figure 5, within the scope of the present invention an asymmetric arrangement of the flexion regions 34.1-34.4 is also possible, and result in the same effect as the change of transmission ratio of the coordination device 7 of the mechanical model of figure 1. The coordination between the parts 2,3 of the hinge is achieved by the physical arrangement of the flexion regions 34.1-34.4 in the space and the design of the the connection elements 33.1, 33.2. In this style of hinge you get two types of coordination. The first type of coordination is the coordination between the multiple hinge axes, as already described. A second type of "coordination" is the lateral and torsional stability of the hinge, which increases as the hinge moves along the trajectory that is intended to follow from open to closed. This is of special importance, since this second form of stability allows the mechanical seal of the closure.

Absent this lateral and torsional stability, the hinge would not self-center in the closed position, and the closure could not be used in automated filling and packaging machines. More details on this relationship will be explained later, in the present. The arrangement illustrated in Figure 5 requires a predetermined amount of bending or elasticity in one or more of the components of the closure 30 of Figure 5. That resilience can be achieved in accordance with the teachings of the patent. No. 5,794,308, as will be further described in the body of the present text, can be achieved in accordance with the teachings of our pending application PCT / EP98 / 02780, or can be achieved in accordance with further teachings that are expressed in the present application. To make use of this elasticity, and achieve energy storage through this structural deformation, the bending regions 34.1-34.4 are arranged in the space according to the shape that is desired. Since those aspects of the design are described in more detail in the previous patent and the pending application mentioned above, and which are incorporated herein by reference, no further explanation is given here on these aspects of the present invention. When the closure 30 is opened or closed, the geometry of the connecting elements 33.1-33.2 produces a specific deformation of the structure of the hinge area. The degree and extent of the deformation of the various aspects of the geometry of the closure depend on the angles and f of an opening angle a of the closure. In one of the preferred embodiments of the present application, the structural deformation is designed to be zero at times when the closure 30 is in a stable position; in the exemplary practical embodiment, the complete opening position and the complete closing position, being zero in the full closing position and the maximum designated in the full opening position. However, the structural deformation and its corresponding accumulation of force can be designed in any position in a closure: for example, the position of complete closure. If the closure was designed in such a way that an opening force is retained, when the closure is in the full closing position, a greater spring-action effect can be obtained at the time of opening, which may be desirable. As an alternative, a residual closing force may be desirable when the closure is in the full closing position, so as to better maintain the closing state. Figure 6 is a pardal view, in approximation, of the practical embodiment of Figure 5. In addition to the detail of Figure 5, as will be further explained in the PCT / EP96 / 02180 application mentioned above, Figure 6 illustrates better the forces that, at the moment of putting into action the closing of figure 6, produce a structural deformation in some section of the closure. Preferably, the connecting elements 33.1, 33.2 have a trapezoidal shape, like the truncated base of a triangle. The shorter edges of 36.1, 36.2, which serve to truncate the triangles producing the trapezoidal connection elements 33.1, 33.2, are subjected to compression forces, which resist to produce deformation forces to be applied to another section of the closing structure, as illustrated in 35.3, 35.4, 35.5 and 35.8. In an analogous manner, the longer edges 37.1, 37.2 of each connector element are subjected to tension during the closing process of the hinge, and produce deformation forces 35.1, 35.2, 35.8 and 35.7. in this way, each of the connecting arms 33.1, 33.2, provides strength to the rest of the closing structure to which, in some way, the elastic deformation must absorb. The importance of this elastic deformation and the elasticity of the body 31 and of the lid 32 of the closure will be described in more detail with reference to Figures 7 and 8. Desirable, in accordance with the teachings of this aspect of the present application, is that the connecting elements 33.1, 33.2 are relatively rigid, and must be sufficiently rigid so that the compressive forces along the shorter edges 36.1, 36.2 do not overlap the shorter, or compression, edges 36.1, 36.2 as a consequence of the deformation forces 35.3, 35.4, 35.5 and 35.6. Also, it is highly desirable that the connecting elements 33.1.33.2 be relatively rigid in the torsional aspect. Preferably, the cross section of each of the connecting elements 33.1, 33.2, made along the arrow in the figure, is sufficiently rigid against the torsional stress. The torsional rigidity of the entire closure 30 can be modified by increasing the distance B between vertices, to increase the total rigidity in the torsional aspect of the closure 30. To increase the torsional stiffness of the entire closure is achieved when the dimension B increases there are between vertices, defined by the bending regions 34.1, 34.2, 34.3 and 34.4. it is desirable that, in order to produce an acceptable level of torsional stiffness of the entire container 30, the vertices 38.1, 38.2 should store between them a chosen distance B, preferably at least half, of the distance of the length of each shortest edge 36. 1, 36.2. By increasing B you can obtain a stable structure and own centering, the provision of the hinge. However, B can not increase without limit, since this increases the distance between the vertices and must necessarily increase the angle? or the angle f, or both at the same time. In contrast, structures with a small distance B, or in which the vertices 38.1, 38.2 of the triangles defined by the bending regions 34.1, 34.2, 34.3 and 34.4, when they are coincident, produce a hinge structure that is unstable, from the torsional point of view, and weak, with an unsatisfactory and insufficient coordination between the parts of the hinge, especially in the position of total opening. Figure 7 is a further explanation of the practical embodiment of Figure 6, and shows significant features of the Invention that appear in the present application. The importance of these features can be better understood after the operation of the patent 308 on which already discussed above is understood. In the patent 308, as illustrated in, for example, Figure 6 of that patent, an intermediate part 4.1, 4.2, which is substantially rigid in the flexion, of each hinge element is connected to the body and the lid by means of upper and lower coupling elements 6.1, 6.2, 7.1 and 7.2, corresponding generally to coupling or transmission areas 45.1, 45.2 of the body 31 of the container 30, as illustrated in figure 7. Of course , in the cap 32 of the container 30 equivalent coupling elements are also provided with the coupling elements 45.1, 45.2 with the body, in accordance with the teachings of the present application. As explained in the patent 308, the coupling elements are elongation-relieving elements, which are elastic in nature. While the equivalent parts of the present application, the coupling or transmission areas 45.1, 45.2 may be elastic, the present application transmits some or all of this force to adjacent elastic areas, including elastic zone 40.2, which is provided. between the coupling or transmission zones 45.1, 45.2, and the elastic zones 40.1, 40.3, which are provided on opposite sides of the coupling or transmission areas 45.1, 45.2 in this manner, in accordance with the teachings of the present application, such as illustrated in Figure 7, at least some of the induced structural deformation is supplied from the coupling or transmission areas 45.1, 45.2 in the practical embodiment of the present invention, to at least one of the zones elastic 40.1 - 40.3. this has a secondary benefit. In the patent 308, the coupling elements 6, 7 had to be made elastic, to absorb these deformation forces. On the other hand, in the present application, it is not necessary for these coupling or transmission areas 45.1, 45.2 to be made elastic, although they can be manufactured in this way. Instead, in accordance with the teachings of the present application, the coupling or transmission areas 45.1, 45.2 transmit some or all of the deformation forces to the adjacent elastic areas 40.1-40.3. This allows for an increase in flexibility in the design of the hinge and the hinge designer gives you the option of that. there where the deformation energy is absorbed for retransmission, produce the spring action that is desired to bring the hinge to one of its stable states. Figure 7 illustrates this transfer of deformation forces into one of the elastic zones 40.1-40.3. with reference, again, to Figure 6, the structural deformation forces are illustrated with arrows 35.1-35.8. These forces are transmitted from the coupling or transmission areas 45.1, 45.2, as shown in Figure 7 with the arrows 50.1-50.4. in accordance with the teachings of the present application, these elastic zones 40.1 - 40.3 alone, or together with the areas of coupling or transmission 45.1, 45.2, function as energy storage stops, to temporarily preserve the structural deformation energy, which can later be returned to the hinge for provide a closing or opening, by spring action, towards one of the stable states of the hinge. When energy is released from the elastic zones 40.1 - 40.3, it is transmitted from the vueita to the hinge, through the same trajectories indicated by the arrows' 50.1 - 50.4 but, of course, in the opposite direction to that in which the Shipping. According to the teachings of the present application, the energy that is supplied to the hinge to pass it from one stable state to the other is absorbed by induced structural deformation, whereas in the 308 patent, energy was completely absorbed within the areas of coupling or transmission 45.1. 45.2. According to the teachings of figure 7, all or all of the energy is transmitted to the attached elastic zones 40.1 - 40.3. In this way, if the designer designs the coupling or transmission areas 45.1, 45.2 so that they are essentially rigid, essentially all the deformation energy is transmitted to the adjacent elastic areas 40.1-40.3. alternatively, within the scope of the present application, the designer can design the container in such a way that the same energy is damped in the areas of coupling or transmission 45.1, 45.2, while part of the energy is transferred to the adjacent elastic zones. This solution achieves the beneficial result of transmitting the accumulated energy over a larger area, which allows sufficient force for spring action, even in situations in which the coupling or transmission zones 45. 1, 45.2 are relatively small. Thus, the techniques of the present application allow applicants' invention techniques, such as the one disclosed in the prior patent 308, to be instrumented more flexibly and instrumented in smaller containers.

Although the coupling and transmission areas 45.1, 45.2 and the elastic zones 40.1-40.3 can be visibly identified in the finished container, this need not be the case. For design reasons it may be desirable to completely integrate these parts of the container. In particular, in situations in which the deformation energy is intended to be transmitted from the coupling or transmission areas 45.1, 45.2 to the elastic zones 40.1-40.3, all the zones may have the same wall thickness. Preferably, the deformation energy stored in the energy storage stops comprises the elastic zones 40.1-40.3 and is provided with a "flat" force-deformation characteristic. This is best achieved by relatively long spring elements, compared to the degree of deformation that was imparted. Such a flat characteristic is best obtained through the storage of energy that is achieved by bending deformation. In this way, the elastic zones 40.1 - 40.3 are preferably constructed as elastic elements intended to be deformed by bending. It is important to understand that the bending required would not be obtained with hinge arrangements that had a major axis for hinge rotation, as that would cause a complex stress characteristic that would typically cause the problem described above. From the foregoing, it is evident, that the elastic zones 40.1-40.3 can appreciably increase the amount of spring energy that is absorbed from the connecting arms 33.1, 33.2, when passing through the coupling or transmission areas 45.1. , 45.2. in this way, by means of the use of such zones a substantially improved result is achieved. Figure 8 shows an alternative schematic practical embodiment of the present invention. Mainly, Figure 8 differs from Figure 7 in that the longer, outer edges 51.1, 51.2, of the connecting elements 33.1, 33.2 are curved in space. This may be, in principle, for the purpose of improving the integration of the design into a specific container design, such as that illustrated in Figure 13. However, in this example, the curved areas along the edges 51.1, 51.2 of the connecting elements 33.1 33.2 can be used as energy accumulator stops that provide additional bending deformation. In these circumstances, the zones along the inner edges 52.1, 52.2 have to be manufactured, however, with sufficient stiffness to prevent warping or bending, as was previously said, with what the torsional stiffness required to make each complete connection element 33.1, 33.2 rigid before torsion. In this practical embodiment, some deformation force is also transmitted to the coupling or transmission elements 45.1, 45.2 and, in addition, to the elastic zones 40.1 -40.3. in this practical embodiment, the coupling or transmission elements and the elastic areas are defined less clearly, with respect to the ones in relation to the others; of the entire located area of the body 31, which functions as an energy accumulator stopper. Analogously, it should be understood that the entire description of the transmission of forces, with respect to figures 6 and 7, although it is described in a specific manner in relation to the body 31 of the container 30, is also valid for the cover 32 of the container 31. It has to be understood that according to the principles of the present invention, it is not necessary to accumulate energy in the body and in the lid at the same time. Nevertheless, at least one elastic zone must be provided in the body, the lid or the connecting zone, in accordance with the teachings of the present patent application. The identification of the elastic zones and those of coupling and transmission is not easy to determine, when an individual container is observed without technical help. However, the identification of these zones can be done according to any known technique. Perhaps the simplest way to identify these areas is through the use of Finite Element Analysis (FE) techniques, available through several programs, which are available on-site, from computer-aided design and analysis. Figure 9 illustrates an alternative practical embodiment of the container object of the present invention, wherein the bending regions 34.1 34.2 are curved or arcuate. Again, the connecting elements -in this case, 33.1- connect the container body 31 from the lid 32 of the container, and the elements intersect along a separation plane 60 which, in this practical embodiment, is somewhat stepped. Otherwise, the practical embodiment of Figure 9 is, in general, similar to the other practical embodiments of the present application. Figure 10a shows trajectories 56.1, 56.2 of two points P 'and P ", located on the back of a lid 32 of a container 30, according to the practical embodiment of figure 11. In the figure 11 shows, in schematic form, a rectangle 54 on the body 31 of the container 30 (see Figure 11). This rectangle is also shown schematically in Figure 10a. The direction of observation is indicated by an arrow A in figure 11.

The location of a separation plane of the container 30 is illustrated as line 80 in Figure 10a, where it is illustrated as line 60.1 of the median plane of separation in Figure 11. The rectangle 55 shows, schematically, the back section 55 of the lid 32 (extending down from the lid 32 in the closed position), in the area of the points P 'and P "in the closed position (55.1) and in the open position (55.2). ). The two dotted curves 56.1 and 58.2 show the displacement of the two points P 'and P' 'in space, when the closing mechanism moves between the open and closed positions. It is evident that the two points P 'and P "of the rectangle 55 collide with the rectangle 54. This means that, in this case, the lid 32 of the closing mechanism 30 would collide with the body 31. This collision can be avoided if it is followed The teachings of the present application can be done by making the points P 'and P "move along trajectories having a suitable and specific pattern, as shown in the kinematic curves of Figures 4a) to 4c). Figure 10b) shows an example of what is preferred as a solution to the problem explained above in relation to Figure 10a), which avoids the collision between the body 31 and the lid 32 by moving the points P 'and vertically P ", at a distance E above the separation plane 60 and inclining them at an angle d (see also figure 14), the two points P 'and P" move in completely different paths 57.1, 57.2 and do not collide with the lower rectangle 54, which represents the Here, the points P 'and P "are placed in such a position that they immediately move outward and away from the contour of the rectangle 54, which represents the lower body 31. A practical embodiment of Preference for a solution as shown in Figure 12. Figure 11 shows a practical embodiment of preference for a locking mechanism 30 with a coordinated multi-axis hinge arrangement 1. The closing mechanism 30 consists of a body 31, a cover 32 and two connecting arms 33.1 and 33.2, which are connected to the body 31 and the cover 32 by over bending areas 34.1 to 34.4. there is a plane 80 for separating mechanism 30, which is indicated by numbers 60.1, 60.2 and 60.3. in this practical embodiment, the points P 'and P "are located in the separation plane 60. Here, the connecting arms 33.1, 33.2 are constructed with a thick compression zone and a thin tension zone. The thick zone of compression is thick enough to avoid warping or bending when subjected to a pressure load. In this practical embodiment, these zones have no functional importance for the spring effect of the closing mechanism 30. The cross section of the connecting elements is constructed to be rigid against twisting, in accordance with the teachings of the present application. The coupling elements 45.1, 45.2 that exist in this environment can, depending on the application that is desired, accumulate part of the deformation energy. In addition, the coupling or transmission elements 45.1, 45.2 transmit some, or all, of the deformation energy produced by the multi-axis hinge arrangement 1, towards the adjacent elastic zones 40, which work alone or together with other elements, in the nature of an accumulator of energy. In this way, the elastic zones can, as an option, operate together with the coupling or transmission elements 45.1, 45.2. Here the energy is stored temporarily, preferably by bending deformation. Arrows 50.1 - 50.5 illustrate this process of energy transmission. The closing mechanism of Figure 11 is constructed with a latch mechanism. The points P 'and P' 'collide in a desirable and controlled manner with the body 31, in such a way that the coordinated multi-axis hinge arrangement is locked or latched. To release the latch you can tighten the hinge on the back of the body 51, near point P'l. The latch mechanism is described in detail in Swiss Patent Application No. 0981/98, which will be filed on April 30, 1998, and which is incorporated in the present application as a reference. Figure 12 shows another preferred embodiment of the closing mechanism 30 with a coordinated multi-axis hinge arrangement. As with other practical embodiments described above, the closing mechanism consists of a body 31, a cover 32 and two connecting arms 33.1, 33.2 conacted with the body 31 and the cover 32 by means of bending zones 34.1 34. 2. At this time it should be noted that, preferably, in any of the practical embodiments of the present application the bending zones 34.1, 34.2 can be manufactured in the form of thin film hinges, casting the entire closing mechanism by casting. , including the body and the lid, as a single monolithic plastic structure. Thus, it is evident that a closing mechanism complying with the teachings of the present application can be manufactured efficiently. The separation plane 60 of the closing mechanism 30 is indicated by numbers 60.1, 60.2 and 60.3, of FIG. 12. In this practical embodiment, the points P 'and P "are arranged on a surface 61, which is thus shown in Figure 14, which is located at a vertical distance E from the separation plane 60, as best shown in Figures 10b) and 14. The distance E is chosen such that at any time there is a collision between the cover 32 and the body 31. It is desirable that the plane 61 is inclined, with respect to the separation plane 60, according to the angle d, as illustrated in figures 10 and 14. The plane 61 corresponds, in the closed position of the closing mechanism 30, with a surface 62 of the body 30, so that there is no gap and an optimal design is obtained.

In this practical embodiment, the coupling or transmission areas 45.1-45.6 transmit the structural deformation and the concomitant storage of their energy, produced by the multi-axis hinge arrangement 1 towards adjacent elastic zones 40.1-40.3. Of course, the transmission zones 40.1 - 40.6 can also be elastically deformed, so that they also store energy. The elastic zones 40.1 - 40.3 with the coupling or transmission elastic areas 45.1 - 45.6 act as energy storage stops, in which the deformation energy is temporarily stored, preferably by folding deformation. Then, this energy is returned to the hinges to allow closure by spring action.

The dark arrows 50 of Figure 12 illustrate this transmission process described above, in relation to Figure 11. Figure 12 differs somewhat from the other figures, in which 12 illustrates that the elastic zone 40.3 does not need to be located immediately next to the multi-axis hinge arrangement 1, but can be located anywhere in the parts of the overturning mechanism, as long as the transmission of the structural deformation and the concomitant storage of its energy is guaranteed. As stipulated by the teachings of the present application, by means of the use of known modeling techniques it is possible to control the size of the elastic zones, the amount of energy stored in them, the amount of force that is transferred from the hinges, the location of the stable positions and, virtually, any other aspect of the performance of the hinges. The connecting elements 33.1, 33.2, in the practical embodiment of Figure 2, are relatively thick flattened plates, which are rigid in the torsional aspect. The connecting elements 33.1, 33.2 are relatively flat on both surfaces thereof, and the outer surface of them has a shape that follows the outside of the closing mechanism, so that the connecting elements 33.1, 33.2 can be optimally integrated the outer shape of the closing mechanism. Of course, the design of the cross section of the connecting elements must take into account the requirements of torsional rigidity, tension and compression forces, and the contraction behavior of the chosen geometry. However, the principles described in the present application can be obeyed to achieve a hinge design that has the desired performance characteristics. Figure 13 shows another practical embodiment of the closing mechanism 30, which employs the multi-axis hinge coordinated arrangement 1 of the present invention. The closing mechanism 30 in the practical embodiment of Figure 13 differs from the other closing mechanisms in several important aspects. First, the separation plane 60 of the closing mechanism 30 is stepped, as indicated by the closing lines 60.1, 60.2. although this prevents the lid of the closing mechanism from retracting, with respect to the body of the closing mechanism, to the same degree as the other practical embodiments, this may be necessary in order to achieve specific design configurations, such as the complex shape of Figure 13. In this practical embodiment, the multi-axis hinge arrangement 1 is positioned at an angle t serving to lift the separation plane 60 from the lid, relative to the separation plane 60.2 of the body, when the closure mechanism It is in the open position. The purpose of this angle is self-evident, it has the purpose of allowing the lid of the closing mechanism to be kept away from the protruding and very high peak 65 of the body 31 of the closing mechanism. In this practical embodiment, the points P 'and P "are arranged on a surface 61, which is located at a vertical distance E from the separation plane 60, as illustrated in Figures 10b) and 14. In this practical embodiment , this distance E is chosen so that there is no collision between the lid and the body.The plane 61 is incised at an angle d with respect to the separation plane 60, as already discussed with reference to figures 10b) and 14. The plane 61 corresponds, in the closed position of the closing mechanism 30, to the surface 62 of the body 31, so that in this practical embodiment no spaces remain and an optimum design is achieved. Elastic zones 40.1 40. 3 function as buffers that accumulate energy, in the manner already discussed for other practical realizations. Note that in this practical embodiment, however, the transforming energy can be transmitted to a part of the cap that is > »,. ? ÍY Í. considerable distance from the hinge area, transmission that is contemplated in the practical embodiments of the present application. Furthermore, the practical embodiment of Figure 13 differs from the other practical embodiments in that the connecting elements 33.1, 33.2 come in the shape of a "knee" curved in space, such that the external shape of those elements is configured to be conformant with the exterior design of the body 31 and of its cover 32. A zone that is along the longer free edge 37 of the connecting element that has the shape of a knee, by virtue of the articulation or knee that is in the element of the knee. Connection 31.1 or 31.2 may function, in part, as an accumulation buffer, which is illustrated as an elastic zone 40.3. thus, in this practical embodiment employing a knee in the hinge connecting element, a part of the energy that is used for the spring effect can be stored, by bending deformation, within the hinge itself. Of course, the shortest free edge 36 of the connection element must be manufactured, in the case of this practical embodiment, so that it neither warps nor deforms when it is under the compression pressure to which it is subjected. In addition, in order to provide a good hinge with spring action, connection elements 33.1 and 33.2 must be manufactured with sufficient torsional stiffness. Figure 14 is a partial side view of the closing mechanism, taken in the direction of the arrow A of Figure 11. Figure 14, in addition to illustrating the lid 32 in the open position, it also comprises a partial sectional view of the lid in the closed position, which is illustrated as 32.2. Here, the points P 'and P "are arranged on a surface 81 located at a vertical distance E (as will be explained in relation to the figures 10b) and 14) of the separation plane 60. Once again, the distance E is chosen so as to avoid any collision between the tape 32 and the body 31. Likewise, it is repeated again that the plane 61 is inclined at an angle d with respect to the separation plane 60, that allows to reach an optimal design in the way that was already discussed. Figure 14 exhibits, however, another advantageous attribute. It is particularly difficult to manufacture a precise hinge that acts by spring, due, mainly, to many geometric constraints of the manufacture and to the problem of the contraction of the material. The coordinated muitieje hinge arrangement, object of the present application, provides a technique for compensating shrinkage and other problems that are due to geometry.

In relation to a system of x-y coordinates, as illustrated in the figure, the contraction of the material in the mold is usually greater in the direction of the coordinates than in the direction of the abscissas, as explained with reference to the direction arrows of figure 14. By molding the closing mechanism in the open state and compensating the contraction by adjusting the hinge joints, the shrinkage can be compensated adequately. This can be achieved by adjusting the dimensions Kl and K2 shown in Figure 14. Figure 15 illustrates a preferred design, in cross section, of the film hinge 70, which is used as bending areas 34.1-34.4, in FIG. a r practical embodiment of preference of the present application. Figure 15a) illustrates the film hinge 70, when the closing mechanism is in the open position, while Figure 15b) illustrates the hinge when in the closed position. Adjoining the film hinge 70 is a connecting element 33 and the body 31 or the lid 32. As is immediately apparent from the practical embodiments discussed above in this application, the body 31, the lid 32 and the connecting elements 33 are often curved, in order to achieve the desired characteristics of the design. The film hinge 70 should be designed with this consideration in mind, the film hinge should be designed to fit precisely within the available space, and should be designed by parts of a mold that can be easily separated when opened mold. Consequently, it is important that the design of the film hinge be insensitive to geometric imperfections. The film hinge illustrated in Figures 15a), 15b) comprises an internal part to which two planes 72, 73 which are inclined at an angle define? with respect to the vertical, to obtain the best material flow patterns and to optimize the transmission of loads. The angle ? it must be in an area such that the minimum possible thickness 74 of the film hinge 70 is still defined with ciarity. The planes 72, 73 are connected by means of a surface 78 having a cylindrical shape and defining the inner edge of the film hinge 70. The outer part of the film hinge is formed by a plane 75 extending from a first outer surface 76 which, in this example, is curved, up to a second outer surface which is also curved. Note that the first outer surface 76 is the outer surface of the connecting element 33, while the second outer surface 77 is the outer surface of the body 31 or the lid 32. As can be seen in figure 15a), the width from the plane 75 approaches zero in the relative center of the film hinge 70, due to the arcuate curvature of the surfaces 76, 77. However, this plane has a large width at the edge of the film hinge 70, also due to this curvature. Of course, all film hinges must be polished or very smooth. Figure 15b) illustrates one further advantage of this film hinge. In the closed position, the plane 72 is aligned, in general with the plane 73 and helps to put the connection element in position 33. Moreover, this function is to reinforce in general the film hinge, when this is in closed position. This is especially useful in the area of the short or inner free edge of the connecting element 33. This is indicated by the arrow 79. Of course, additional elements can be used on the body 31 and the cover 32 of the closing mechanism 30 , to help in the positioning of the connection element 33. This is indicated, for example, with the arrows 80. As is even more self-evident, the surfaces 72, 73 do not need to be flattened and other surface forms may be employed, although, preferably, such surfaces must be conformable to the surface. the closed position.

A further advantage of the film hinge 70 of FIG. 15 is that, with a suitable design, the film hinge can also act as an energy storage buffer. For example, the alternative practical embodiment shown in Figure 9 accumulates energy in the hinge, thanks to the curvature of the hinge. Of course, other non-linear hinge designs can serve the same purpose. By virtue of the practical embodiments of the present invention described above it is evident that a person, who has normal experience in this technology, can modify the present invention as he wishes without departing from the general scope of the present invention, to which it should be defined only by the appended claims. The changes and modifications of this system that are contemplated by the practical realizations will be obvious for any expert in this technology. Accordingly, the appropriate general scope of the present invention should only be defined by the appended claims.

Claims (27)

1. A multi-axis hinge arrangement with at least two stable positions comprising, a first hinge part; a second hinge part; at least two connecting arms that are separated from each other at a certain distance; at least four bent regions connecting each of the connecting arms directly to the first hinge part and to the second hinge part; at least two transmission zones joining the bent regions; elastic zones of the hinge parts, elastically deformable when opening or closing on the multi-axis hinge arrangement, connected to the transmission zones; whereby the connecting arms have at least four sides, while two unattached sides of each connecting arm are formed by one of the bending regions; in the closed position the bending regions of a first connecting arm define a first plane and the bending regions of a second connecting arm define a second plane that intersects the first plane at an angle; the bending regions of the first connecting arm and the bending regions of the second connecting arm are arranged at another angle with each other in order to allow at least two relative positions of the hinge parts when the connecting arms and / or the hinge parts are practically without structural deformation; The connecting arms have a section that is practically rigid to torsion.

The hinge arrangement according to claim 1, wherein at least one of the connecting arms and / or the hinge parts are tension-free in at least one of the stable positions of the hinge arrangement.

The hinge arrangement according to claim 1 or 2, wherein the elastic area stores energy by means of the elastic deformation when the multi-axis hinge arrangement is opened or closed and in which the stored energy provides an automatic closing action which forces the arrangement of hinge so that it returns to one of its stable positions. .

The hinge arrangement according to any one of the preceding claims, wherein the vertices defined by the bending regions are spaced apart by a distance that is at least practically half the length of the shortest edge of a connecting arm.

5. Hinge arrangement according to any of the preceding claims, wherein at least one of the edges of the connecting arms is rigid and does not curve under compression forces.

The hinge arrangement according to any one of the preceding claims, characterized in that at least one of the connecting arms has an elastic region that is elastically deformable when opening or closing the hinge arrangement.

The hinge arrangement according to any one of the preceding claims, characterized in that the connecting arms are at least partially spatially curved.

Hinge arrangement according to any one of the preceding claims, characterized in that the bending regions are elastically deformable and there is adequate energy stored to open or close the multi-axis hinge arrangement and because the stored energy supports an automatic closing action which forces the Hinge arrangement to return to one of the stable positions.

9. Hinge arrangement according to any of the preceding claims, characterized in that the bending regions are arranged symmetrically or asymmetrically with respect to the hinge parts.

Hinge arrangement according to any one of the preceding claims, characterized in that the first hinge part is a body and the second hinge part is a cover of a closure.

11. Hinge arrangement according to claim 10, characterized in that the elastic zone is arranged in the region of a free edge of the body.

12. Hinge arrangement according to claim 10 or 11, characterized in that the elastic zone is arranged in the area of a free edge of the lid.

13. Hinge arrangement according to claim 10, 11 or 12, characterized in that the elastic zone is disposed between the two transmission zones.

14. Hinge arrangement according to any of claims 10 to 13, characterized in that the connecting arms are in the closed position of the closure integrated in the outer contour of the closure, such that no part protrudes substantially over the surrounding area.

The hinge arrangement according to any of claims 10 to 14, characterized in that the hinge arrangement is at an angle with respect to a dividing plane.

16. Hinge arrangement according to any of claims 10 to 15, characterized in that the connecting arms have at least partially a substantially constant thickness.

The hinge arrangement according to any of claims 10 to 16, characterized in that the connecting arms at their shortest free end have a greater thickness compared to their thickness at their longer free edges.

Hinge arrangement according to any one of claims 10 to 17, characterized in that at least one surface of the cover is arranged outside a dividing plane and cooperates with a corresponding surface of the body such that space of separation does not occur in the position of closed closing.

19. Hinge arrangement according to any of claims 10 to 18, characterized in that the curving regions are made as a film hinge.

The hinge arrangement according to claim 19, characterized in that the film hinge has a section that is limited by a circular curve on one side and by a straight line or by a circular curve on its opposite side.

The hinge arrangement according to claim 19 or 20, characterized in that a plane is disposed at an angle with respect to a dividing plane on the inner side of the film hinge for coupling with a corresponding plane of the connecting element in the position closed of the closure to place the connection element.

22. Hinge arrangement according to any of claims 10 to 21, characterized in that at least one bent area is curved.

23. Hinge arrangement according to any of claims 10 to 22, characterized in that one of the stable positions of the hinge arrangement is outside the design range, beyond the closed position of the closure such that the hinge arrangement is being pushed with a closing force.

The hinge arrangement according to any of claims 10 to 23, characterized in that one of the stable positions of the hinge arrangement is outside the design range, before the closed position of the closure such that the hinge arrangement is being pushed with an opening force.

25. Hinge arrangement according to any of the preceding claims, characterized in that the transmission zones are integrated with the hinge parts.

26. Hinge arrangement according to any of the previous claims, characterized in that at least the transmission zones arranged in a hinge part are practically rigid.

27. Mold suitable for a hinge arrangement according to any of claims 1 to 25, characterized in that at least one mold dimension for corresponding geometry in a first position of the hinge arrangement is larger in a first direction compared to a second direction for the same corresponding geometry in a second position of the hinge arrangement.