WO2008125099A2

WO2008125099A2 - Parallelogram connecting rod structure, particularly a monolithic parallelogram connecting rod structure for a weighing sensor

Info

Publication number: WO2008125099A2
Application number: PCT/DE2008/000635
Authority: WO
Inventors: Timo Hauck
Original assignee: Wipotec Wiege- Und Positioniersysteme Gmbh
Priority date: 2007-04-17
Filing date: 2008-04-16
Publication date: 2008-10-23
Also published as: DE102007018422A1; DE102007018422B4; WO2008125099A3

Abstract

The invention relates to a monolithic parallelogram connecting rod structure, particularly for a monolithic weighing sensor, comprising two parallelogram connecting rods (9, 11) located in parallel, wherein each of the two parallelogram connecting rods (9, 11) is connected to a rigid element (3, 7) by at least one solid body joint (13a, 13b; 15a, 15b; 17a, 17b; 19a, 19b) at each of the two ends of each parallelogram connecting rod (9, 11), the four joint axes of the solid body joints (13a, 13b; 15a, 15b; 17a, 17b; 19a, 19b) being parallel and forming the vertices of a parallelogram in cross section. According to the invention, at least one end of a parallelogram connecting rod (9, 11) is connected to the related rigid element (3, 7) by at least two solid body joints (13a, 13b; 15a, 15b; 17a, 17b; 19a, 19b), wherein the longitudinal extension planes of the solid body joints encompass a non-zero angle (α, ß), the joint axes of the at least two solid body joints (13a, 13b; 15a, 15b; 17a, 17b; 19a, 19b) being aligned. The invention further relates to a weighing sensor having such a monolithic parallelogram connecting rod structure.

Description

Parallelogrammlenkerstruktur, in particular monolithic Parallelogrammlenkerstruktur for a weighing sensor

The invention relates to a Parallelogrammlenlcerstruktur, in particular a monolithic Parallelogrammlenkerstruktur for a Wägeaufnehmer, with the features of the preamble of claim 1. Furthermore, the invention relates to a weighing transducer, in particular for an electronic balance according to the principle of force compensation, with such a Parallelogrammlenkerstruktur.

Modern weighing receivers, where high resolution is required, often work on the principle of electromagnetic force compensation. In recent years, such weighing sensors are produced almost exclusively as monolithic weighing receivers, wherein all the essential components, in particular the usual parallelogram link structure and the associated essential components of the power transmission and / or reduction elements are monolithic. Such a weighing sensor is described for example in DE 100 54 847 C2. Such a parallelogram link structure is required in particular in so-called single-point weighing receivers. Without the Parallelogrammlenkerstruktur which causes a forced parallel guidance of the load receiver, with an eccentric load of the load transducer relative to the power transmission and / or reduction elements, such as lever mechanisms, the torques occurring would be transferred to these elements and produce a weighing error by their unwanted deformation.

Such a parallelogram linkage structure is usually produced by an upper and a lower link, which are plane-parallel to each other. In a monolithic embodiment of the weighing transducer, the parallelogram links are connected by means of thin material points, which represent solid-state joints, to the stationary part of the weighing receiver and to load-bearing. The thin joints forming the solid joints provide for a lower rigidity of the parallelogram in the measuring direction, that is, in the translational direction, in which the parallelogram linkage structure allows a shift of the load receiving. The rigidity of the parallelogram linkage in the measuring direction is determined by the thickness of the thin points and the adjoining the thin locations geometry of the solid-state joints and their width. In the direction of the joint axes formed by the solid-state joints, the solid-state joints usually have a constant cross-section. This results in a simple production of solid joints, for example by drilling, milling or erosion.

Particularly in the case of weighing receivers for use in the microgram range, it is necessary to use solid-state joints with the lowest possible rigidity, in which case the thickness of the thin areas must be reduced to values of 100 μm or less. As a result, however, not only the rigidity in the measuring direction is reduced, but also the rigidity of the parallelogram link structure about axes of rotation perpendicular to the joint axes of the solid-state joints. In particular, the stiffness about an axis of rotation, which is perpendicular to the joint axes and lies in the plane which is spanned by the joint axes, is thereby also reduced. Thus, an eccentric load introduction (outside the plane of symmetry of the parallelogram link structure), perpendicular to the joint axes of the solid-state joints, can lead to inaccurate measurement results. The reason for this is that with eccentric loads, the joint axes of the solid-state joints are shifted or tilted with respect to the axis which is defined by the line of the thinnest point.

One way to increase the rigidity of the parallelogram linkage structure over torques about the aforementioned axis is to increase the distances of the joint axes of the solid state links, that is, the height and width of the parallelogram. However, this leads to an undesirable increase in the installation space of such a weighing sensor.

Based on this prior art, the invention is therefore an object of the invention to provide a parallelogram link structure, which in the direction of the measuring direction has a low rigidity and at the same time an improved torsional rigidity, so the parallelogram linkage structure is also suitable for a weighing picker for detecting low load forces. Furthermore, the invention has for its object to provide a corresponding Weighing.

The invention solves this problem with the features of claims 1 and 12, respectively.

The invention is based on the recognition that by using at least two separate solid-body joints at at least one end of a parallelogram link, a higher stiffness with respect to torques about rotational axes that do not coincide with the parallel joint axes can be achieved, if the longitudinal extension planes of the solid-state links include an angle other than zero. The joint axes of the at least two solid-state joints must of course be aligned in order to allow the desired movement of the parallelogram structure in the measuring direction, without the parallelogram structure twisting.

It should be noted at this point that the plane of symmetry is to be understood as the longitudinal plane of a solid in the case of a symmetrical solid-body joint. In the case of asymmetrically designed solid-state hinges, this may mean a plane passing through the thin layer, wherein in the case of a linear thin layer, that is, the side walls of the thin spot each have a straight line (or straight line) at a constant distance, perpendicular to the Distance between the two thin lines defining straight line is.

According to the invention, the stiffness in the desired direction of movement can thus be achieved by the use of very thin thin points of the solid-state joints, i. be made possible by thin sections with a small cross-section in the region of the hinge axis, at the same time high rigidity to other than the hinge axes.

It is of course possible that more than two solid joints are used at the relevant end of the parallelogram, at least two solid joints between the respective longitudinal extension planes must include an angle not equal to zero. If necessary, however, all of the solids can also be Pear joints on the same parallelogram link have longitudinal extensions, which in each case have a different angle relative to a reference plane.

However, for reasons of ease of manufacture, it will be preferable to use a parallelogram structure with two solid joints on at least one end of a parallelogram link. The total width of the solid-state joints (in particular their thin points) can coincide with the entire width of the Parallelogrammlenkerstruktur or the relevant Parallelogrammlenkers. However, the total width of the solid-state joints can of course also be chosen to be less than the total width of the parallelogram link structure or of the relevant parallelogram link. The width and / or the geometry of the solid-state joints - and in particular of their thin points - can be equal or, in order to increase stiffness relative to defined, eccentric loads, unequal.

Each parallelogram link may be formed (on a plane) by individual - not interconnected - (in a plane adjacent) Parallelogrammlenkerelemente, wherein at least one solid-body joint is formed at each end of the Parallelogrammlenkerelements. However, the individual Parallelogrammlenkerelemente can also be interconnected, for example by one or more webs. However, the desired high stiffness will arise in particular in those embodiments in which each of the parallelogram is formed integrally or monolithically, or wherein individual, located in a plane parallelogram link elements are firmly connected to each other.

According to a preferred embodiment of the invention, at least two solid-body links are respectively provided at each of both ends of one or both (or all) parallelogram links, the longitudinal extension planes of at least two of these solid-state links enclosing an angle not equal to zero.

According to one embodiment of the invention, each of the at least two solid-state joints at one end of a parallelogram, seen in the longitudinal extension direction of the parallelogram, opposite one of the at least two solid-state joints on each arranged at the other end of the relevant parallelogram (or the relevant Parallelogrammlenkerelements), ie the center planes of the opposing solid joints (which are perpendicular to the respective longitudinal plane) are substantially aligned. As a result, a symmetrical parallelogram link structure and a symmetrical behavior of the parallelogram link structure relative to introduced forces can be achieved in a simple manner.

According to one embodiment of the parallelogram link structure according to the invention, a first of the provided at one or both ends of the or the parallelogram link at least two solid-state joints on a longitudinal extension plane, which is spanned with the plane which is defined by the two axes of articulation of the respective parallelogram provided solid state joints, a first Angle α includes. In addition, in each case a second of the provided at each end of the parallelogram at least two solid-state joints on a longitudinal extension plane, which encloses a second angle ß with the plane which is stretched by the two axes of articulation of the respective parallelogram link provided solid state joints. The angles .alpha. And .beta. Are defined as those angles which are enclosed by the parallelogram side, which lies between the two opposite joint axes of the relevant parallelogram link, and the part of the respective longitudinal extension plane which extends completely above or completely below the parallelogram.

In this case, the respective first solid-body joints, to which the angle α is assigned, can be seen substantially opposite one another at both ends of a parallelogram link, viewed in the direction of the longitudinal extent of the parallelogram link. A small offset in the transverse direction of the parallelogram is quite permissible.

According to another embodiment, the respective first solid-state joints at one of the two ends of a parallelogram, viewed in the longitudinal direction of the parallelogram, substantially opposite to the respective second solid joints at the other end of the respective parallelogram. This embodiment ensures optimal rigidity against torques about an axis pa. rallel to the longitudinal direction of the respective parallelogram. This embodiment will also be selected, in particular, if the parallelogram link consists of a plurality of mutually separate parallelogram link elements, at the ends of which a single solid-body joint is provided in each case.

According to a further embodiment of the invention, the positions of the first and second solid-state joints provided on the one parallelogram link may be interchanged with respect to the corresponding positions of the first and second solid-state links provided on the other of the parallelogram links.

According to a preferred embodiment, the longitudinal extension planes of the at least two solid-state hinges can be perpendicular to one another at at least one end of a parallelogram link. This results in a maximum stiffness for torques about any axis, except those axes that are parallel to the joint axes of the solid state joints.

According to one embodiment of the invention, in this case the longitudinal extension plane of one of the solid-state hinges at the one or more ends of the parallelogram link or links can be aligned with the plane defined by the joint axes on either side of the relevant parallelogram link.

According to a preferred embodiment of the invention, the parallelogram linkage structure is formed as a monolithic parallelogram linkage structure, that is, the parallelogram links, the solid state links and the rigid elements are monolithic.

Such a Parallelogrammlenkerstruktur is particularly suitable for a weighing receiver, in particular for an electronic balance according to the principle of force compensation, wherein a first of the two rigid elements is held stationary and wherein the second of the two rigid elements is designed to initiate a weight to be measured, that is making load pickup. Such a weighing device may comprise in the usual way at least one force transmission and / or force reduction element, which is connected to the second rigid element, which forms the load receptacle of the weighing Aufhehmers. The force transmission and / or power reduction element serves to transmit the weight to be detected or to reduce the weight on a measuring and / or display device. A power transmission and / or power reduction element may be formed, for example, as a coupling rod or as a lever. It should be understood in the context of the present description under power reduction and a power transmission.

Such a power transmission and / or power reduction element will, as far as possible also monolithic train with the Parallelogrammstruktur and arrange within the parallelogram. If the provision of the measuring and / or display device within the parallelogram is not possible, then a corresponding force transmission and / or force reduction element can also lead out of the parallelogram area, at least partially. In this case, for example, the last lever arm can be guided past the parallelogram structure on the side (divided into two on either side or asymmetrically on one side). In this case, the subject power transmission and / or power reduction element (or part thereof) may be detachably connected to the power transmission and / or power reduction elements monolithically formed with the parallelogram structure, for example by bolting. In another alternative, the last lever arm may also be led out of the parallelogram through one of the rigid elements on the parallelogram sides or through the parallelogram links.

Of course, in a conventional manner, one of the parallelogram or one of the Parallelogrammlenkerelemente at the same time as Kraftübertragungs- and / or force reduction element or part thereof, in particular as a lever or partial lever, serve.

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

The invention will be explained in more detail below with reference to embodiments shown in the drawing. In the drawing show: 1 shows a side view of a first embodiment of a parallelogram structure according to the invention;

FIG. 2 shows a perspective view of the embodiment in FIG. 1; FIG.

Fig. 3 is a perspective view of a Weighing Hinge with a parallelogram structure according to Figures 1 and 2, and

4 shows a perspective embodiment of a weighing jack with a further embodiment of a parallelogram structure according to the invention.

The monolithic parallelogram structure 1 shown in FIG. 1 comprises a first rigid element 3, which is designed for use of the parallelogram structure 1 in a weighing holder for stationary mounting and has an extension 5 for receiving a measuring and / or display device, not shown.

Furthermore, the parallelogram structure 1 has a second rigid element 7, which is connected to the first rigid element 3 via two parallelogram links 9, 11. The second rigid element 7 may be designed to use the monolithic parallelogram structure 1 for a weighing device as a load-receiving device.

The parallelogram links 9, 11 are integrally connected to the first and second rigid elements 3, 7 by means of solid joints arranged at each end of the parallelogram links 9, 11. The solid-state joints (13a, 13b and 15a, 15b) of the upper parallelogram link have longitudinal extension planes, each of which lies in the plane of symmetry of the thin-point regions produced by two holes each. The axes of articulation are in each case in the center of the thin point in question (seen in cross-section), that is to say the axes of articulation are in each case parallel to the lines of the outer walls of the thin-area regions which are at the minimum distance from one another, in the middle of the distance. The joint axes are thus in the relevant longitudinal plane of the solid body joint in question. In the embodiment according to FIGS. 1 and 2, the longitudinal extension planes of the solid-body joints 13b and 15a of the upper parallelogram link 9 each extend horizontally or, in this case, the longitudinal extension planes of the solid-state joints 13b and 15a are identical to the plane defined by the joint axes of these solid-state joints 13b and 15a is spanned.

By contrast, the longitudinal extension planes of the solid-body joints 13a and 15b of the upper parallelogram link 9 extend vertically, that is, these longitudinal extension planes are perpendicular to the longitudinal extension planes of the solid-state joints 13b and 15a. This diagonal arrangement of the solid-body joints (in plan view), each with the same longitudinal plane, results in a very good torsional stiffness in the articulated connection of the second rigid element 7 to the first rigid element 3 with respect to torques about an axis which is not parallel to the joint axes.

The connection of the second rigid element 7 to the first rigid element 3 via the lower parallelogram link 11 has been selected in the embodiments illustrated in FIGS. 1 and 2 such that the solid-state joints 17a, 17b or 19a, 19b are opposite corresponding positions of the solid-state joints 13a, 13b and 15a, 15b each have longitudinal extension planes with the respective other orientation. That is, the solid-state joints 17a, 19b have a horizontally extending longitudinal extension plane, while the longitudinal extension planes of the solid-state joints 17b, 19a extend vertically.

As a result of this arrangement of the solid-body joints, maximum rigidity of the connection of the second rigid element 7 to the first rigid element 3 with respect to torques occurring is achieved about axes which do not run parallel to the joint axes.

Of course, the longitudinal extension planes could also be chosen differently. However, if a certain symmetrical behavior of the parallelogram with respect to defined torques are achieved, it is recommended that the longitudinal extension planes of the two solid joints 13, 15, 17, 19 each one end of a parallelogram 9, 11 each at a defined angle α or ß with respect to a reference plane, ie, a first of the solid-state joints has a longitudinal extension plane including a first angle α with the reference plane, while a second one of the solid state joints has a longitudinal extension plane including a second angle β with the reference plane.

As shown in Fig. 1, for example, that plane E can be selected as the reference plane, which is spanned by the two hinge axes of the solid state joints 13 (13a, 13b) and 15 (15a, 15b). As can be seen from Fig. 1, results for the solid-state joint 13 a, the longitudinal extension plane extends vertically, an angle of α = 90 °, wherein the angle α is that angle, the plane E (or the portion between the joint axes of Solid joints 13, 15) with the part of the longitudinal extension plane of the solid-state joint 13a includes, which extends completely above the parallelogram, which is formed (in cross section) by the four hinge axes.

In the same way, the longitudinal extension plane of the solid-body joint 13b encloses an angle β = 0 ° with the plane E, whereby the angle β is also defined as the angle which, starting from the part of the plane E between the two joint axes of the parallelogram link 9 and the Part of the longitudinal extension plane of the solid-state joint 13b is included, which extends completely above the parallelogram. The longitudinal extension planes of the solid-state joints 13a and 13b thus include an angle δ = α-β = 90 °.

The conditions for the solid-body joints 15a, 15b at the opposite end of the parallelogram 9 are in the embodiment of Figures 1 and 2 exactly the opposite. Here, the solid-body joint 15a has an angle β = 0 ° and the solid-body joint 15b has an angle of α = 90 °, i. A solid-state joint with a first angle of α = 90 ° is opposed in each case by a solid-state joint with a second angle of β = 0 °.

The angles in the case of the solid state joints 17 and 19 can be defined in an analogous manner, wherein the angles α and ß are defined in this case by lying below the parallelogram parts of the longitudinal extension planes (except for the case (not shown) α = 0 ° or ß = 0 °) and that plane which is defined by the joint axes of the fixed body joints 17 to 19 is stretched. In this case as well, α and β always denote that angle which is enclosed by the part of the plane between the two joint axes and the part of the relevant longitudinal extension plane lying completely below the parallel program.

In order to achieve a symmetry and a high rigidity with respect to torques about axes which are not parallel to the joint axes, in the embodiment in FIGS. 1 and 2 the positions of the solid state joints on the lower parallelogram link 11, the longitudinal extension planes with the angles α = 90 ° or ß = 0 °, compared to the corresponding positions of the solid state joints on the upper parallelogram 9 reversed, ie The solid-body joints 17b and 19a each have a longitudinal extension plane at an angle α = 90 °, and the solid-state joints 17a and 19b each have a longitudinal extension plane with an angle β = 0 °.

It should be noted that the widths of the thin joints of the solid-state joints 13, 15, 17, 19 which are respectively chosen to be the same in the embodiment according to FIGS. 1 and 2 do not necessarily have to be always the same width. If, for example, the load receiver is always (or predominantly) subjected to a load asymmetrically in a defined manner (ie the load is not introduced with the center of gravity in the longitudinal center plane of the parallelogram structure), an asymmetrical choice of the widths of the thin joints of the solid-body joints can also be advantageous be.

FIG. 3 shows a weighing transducer 20 which has a monolithic parallelogram structure 1 according to FIGS. 1 and 2. The first rigid element 3 represents the stationary part of the weighing jack 20, and the second rigid element 7 constitutes the (movable) load receptor. Within the parallelogram formed by the joint axes of the solid-state joints 13, 15 and 17 and 19, a monolithically designed with the parallelogram lever 22 is provided, which is connected via a coupling rod 24 to a extending within the parallelogram portion of Lastaufhehmers. The coupling rod 24 is connected via a respective solid-state joint with the load receptor and with the short lever arm of the lever 22. The axis of rotation of the lever 22 is also connected via a fixed body joint 28 defined. At the end of the long lever arm of the lever 22, a holder for receiving a measuring device (not shown) or parts thereof is provided.

The foot region of the stationary part 3 is integrally formed with a base plate 26, with which the weighing device can be mounted, for example, in a balance housing (not shown).

In the embodiment shown in FIG. 3, this foot region of the stationary part 3 is not connected massively to the bottom plate 26, as in the embodiment according to FIG. 4, but via three solid joints 30 which are located between the outer wall of the foot region of the stationary part 3 and the inner wall of a breakthrough in the bottom plate 26 extend. Only one of the two longitudinally provided solid-body joints 30 and the solid-body joint provided in the broad side of the opening is visible in FIG. The joint axes of the solid state joints 30 are perpendicular to the plane of the bottom plate 26, so that when a load is applied to the load receptor or the rigid part 7 of the parallelogram 1 in just this direction no unwanted tilting of the load receptor occurs. Through these three solid-state joints thus a mechanical decoupling of the bottom plate is achieved over the other, relevant to the measurement parts of the weighing Aufhehmers 20, so that, for example, torsions or tensions in the bottom plate 26 by the mechanical attachment to another element, for example in a not Housing shown not to be transferred to the relevant parts for the measurement of the weighing transducer 20 and therefore do not affect the accuracy of measurement.

This feature of connecting the bottom plate to the remaining parts of a weighing sensor via at least three solid joints (preferably exactly three solid joints) may of course be used without the special configuration of the parallelogram structure according to the present invention.

The weighing pickup 20 shown in FIG. 4 differs from the weighing pickup shown in FIG. 3 - except for a conventional solid connection of the foot region of the stationary part 3 to the bottom plate 26 - only by the arrangement of FIGS Parallelogrammstruktur 1. In this embodiment of the parallelogram 1, the opposing solid joints of the parallelogram 9 and 11 each have a horizontal or vertical longitudinal extension plane. The (in plan view) diagonal arrangement of the solid state joints 13 and 15 of FIG. 1 to 3 is thus replaced by the symmetrical arrangement of FIG. 4 (symmetrical with respect to a vertical median plane of the parallelogram 9 and 11, transverse to the longitudinal direction of the parallelogram 1 runs.

In order to achieve symmetrical stiffness properties with respect to torques about an axis that is perpendicular to the joint axes of the solid joints 13, 15, 17, 19, the solid joints of the lower parallelogram 11 are selected with respect to their longitudinal plane so that the longitudinal plane each perpendicular to the longitudinal plane of the concerned solid body joint 13, 15, 17, 19 is at the corresponding position of the upper parallelogram 9.

The embodiments shown in FIGS. 3 and 4 of a weighing receiver 20 or a monolithic parallelogrammic linkage structure 1 each having two solid-state joints at each end of the upper and lower parallelogram links 9, 11 represent embodiments that are important in practice since they are relatively simple to manufacture and have a largely symmetrical characteristic of the parallelogram link structure 1.

As already mentioned, it is also possible to replace each of the parallelogram 9 or 11 by two or more parallelogram parts, which can be generated by a separation of the parallelogram shown in the figures 9, 11 in the longitudinal direction. Here you get largely the same behavior with respect to bending stresses, although the stiffness is slightly reduced. However, such a complete separation of a parallelogram in several Parallelogrammlenkerelemente can offer the advantage that between them a power transmission and / or power reduction element can be brought out, or that can be intervened for the production in this area with appropriate tools in the interior of the parallelogram. Although a fully monolithic design of the parallelogram link structure has advantages in terms of mechanical and thermal stability, however, a partial monolithic design of the parallelogram link structure may also be advantageous or even necessary for production-related reasons. For example, one or more solid joints with adjoining parts of the rigid elements, 3, 7 or the parallelogram 9, 11 may be monolithic. These sub-elements can then be combined with other parts to an entire parallelogram link structure, both by releasably and non-detachably connecting the individual components.

Of course, the parallelogram 7, 9 or Parallelogrammlenkerteile with the provided at one or both ends solid joints and adjoining parts of the rigid elements 3, 7 may be monolithic.

Finally, the parallelogram linkage structure may also be made "sliced", ie, the parallelogram link structure 1 is divided in the longitudinal plane into discrete monolithic parallelogrammic link structure elements, for example, each of these monolithic parallelogram link structure elements comprising the parallelogram link elements, at least one solid-state link at each end, and portions of the rigid element The individual parallelogram link structure elements are much easier to manufacture than an overall monolithically produced parallelogram link structure, wherein the individual parallelogram link structure elements may, for example, only have solid-body articulations, along with the longitudinal extension planes identical angles α or ß possess.

Claims

claims

1. Parallelogrammlenkerstruktur, in particular monolithic Parallelogrammlenkerstruktur for a Weighing,

(a) with at least two parallelogram parallelogram links (9, 11),

(b) each of the two parallelogram links (9, 11) being connected to each one of the two ends of each parallelogram link (9, 11) via at least one solid-state linkage (13a, 13b, 15a, 15b; 17a, 17b; 19a, 19b) rigid element (3, 7) is connected, wherein the four hinge axes of the solid joints (13a, 13b, 15a, 15b, 17a, 17b, 19a, 19b) are parallel and form in cross section the vertices of a parallelogram,

characterized,

(c) that at least one end of a parallelogram link (9, 11) is connected to the relevant rigid element (3, 7) via at least two solid-state joints (13a, 13b; 15a, 15b; 17a, 17b; 19a, 19b),

(D) that the longitudinal extension planes of the solid-state joints include an angle (δ) not equal to zero and

(e) that the joint axes of the at least two solid-state joints (13a, 13b; 15a, 15b; 17a, 17b; 19a, 19b) are aligned.

2. Parallelogrammlenkerstruktur according to claim 1, characterized in that both ends of a parallelogram (9, 11) via at least two solid joints (13a, 13b, 15a, 15b, 17a, 17b, 19a, 19b) with the respective rigid element (7; 3), that the longitudinal extension planes of the respective two solid-body joints (13a, 13b, 15a, 15b, 17a, 17b, 19a, 19b) enclose an angle (δ) not equal to zero and that the joint axes of the respective at least two solid-state joints (13a, 13b 15a, 15b, 17a, 17b, 19a, 19b) are aligned.

3. Parallelogrammlenkerstruktur according to claim 1, characterized in that both ends of both parallelogram (9, 11) via at least two solid joints (13a, 13b, 15a, 15b, 17a, 17b, 19a, 19b) with the respective rigid element (3, 7), that the longitudinal extension planes of each of the two solid-body joints (13a, 13b, 15a, 15b, 17a, 17b, 19a, 19b) enclose an angle (δ) not equal to zero and that the joint axes of the respective at least two solid-state joints (13a, 13b 15a, 15b, 17a, 17b, 19a, 19b) are aligned.

4. Parallelogrammlenkerstruktur according to claim 2 or 3, characterized in that each of the at least two solid joints (13a, 13b, 15a, 15b, 17a, 17b, 19a, 19b) at one end of a parallelogram (9, 11), in the longitudinal direction of the parallelogram (9, 11), opposite one of the at least two solid-state joints (13a, 13b, 15a, 15b, 17a, 17b, 19a, 19b) is arranged at the respective other end of the relevant parallelogram link (9, 11).

5. Parallelogrammlenkerstruktur according to any one of the preceding claims, characterized in that in each case a first of at one or both ends of the or the parallelogram (9, 11) provided at least two solid joints (13a, 13b, 15a, 15b, 17a, 17b, 19a, 19b) has a longitudinal extension plane which is clamped with the plane (E) which is defined by the two joint axes of the solid-state joints (13a, 13b; 15a, 15b; 17a, 17b; 19a, 19b) provided on the relevant parallelogram link (9, 11), includes a first angle (α), and that a respective one of the at least two solid-state hinges (13a, 13b; 15a, 15b; 17a, 17b; 19a, 19b) provided at each end of the parallelogram links has a longitudinal extension. level, which with the plane (E), which is spanned by the two axes of articulation of the relevant parallelogram (9, 11) solid joints (13a, 13b, 15a, 15b, 17a, 17b, 19a, 19b), a second angle (β), wherein the angles (α, β) are defined as those angles which are from the parallelogram side, which lies between the two opposite joint axes of the relevant parallelogram link (9, 11), and completely above or completely below the Parallelogramms extending part of the respective longitudinal extension plane are included.

6. Parallelogrammlenkerstruktur according to claim 5, characterized in that the respective first of the solid state joints (13a, 13b, 15a, 15b, 17a, 17b, 19a, 19b) at both ends of a parallelogram (9, 11), in the longitudinal direction of the parallelogram ( 9, 11), are substantially opposite each other.

7. Parallelogrammlenkerstruktur according to claim 5, characterized in that the respective first of the solid state joints (13a, 13b, 15a, 15b, 17a, 17b, 19a, 19b) at one of the two ends of a parallelogram (9, 11), in the longitudinal direction of the parallelogram (9, 11), substantially opposite to the respective second of the solid-body joints (13a, 13b; 15a, 15b; 17a, 17b; 19a, 19b) at the respective other end of the relevant parallelogram link (9, 11).

A parallelogrammic linkage structure according to claim 6 or 7, characterized in that the positions of the first and second solid-state joints (13a, 13b; 15a, 15b; 17a, 17b; 19a, 19b) provided on the one parallelogrammic link (9), opposite to the positions of the first and second, which are provided on the other of the parallelogram (11) are reversed.

9. Parallelogrammlenkerstruktur according to any one of the preceding claims, characterized in that the longitudinal extension planes of the at least two solid joints (13a, 13b, 15a, 15b, 17a, 17b, 19a, 19b) at least one end of the parallelogram (9, 11) perpendicular to each other stand.

10. Parallelogrammlenkerstruktur according to any one of the preceding claims, characterized in that the longitudinal extension plane of one of the solid state joints (13a, 13b, 15a, 15b, 17a, 17b, 19a, 19b) at the one or more ends of the or the parallelogram (9, 11) the plane which is defined by the joint axes on both sides of the relevant parallelogram (9, 11), is aligned.

11. Parallelogrammlenkerstruktur according to any one of the preceding claims, characterized in that the parallelogram (9, 11), the solid state joints (13a, 13b, 15a, 15b, 17a, 17b, 19a, 19b) and the rigid elements (3, 7) monolithic are formed.

12. Weighing sensor, in particular for an electronic balance according to the principle of force compensation, with a parallelogram structure (1) according to one of the preceding claims, characterized in that a first of the two rigid elements (3) for a stationary support and the second of the two rigid Element (7) is designed to initiate a weight to be measured.

13. Weighing lifter according to claim 12, characterized in that with the second rigid element (7) at least one force transmission and / or force reducing element (22, 24) is connected, with which the weight to be detected or the reduced weight on a measuring and / or display device is transmitted.

14. Weighing lifter according to claim 13, characterized in that the at least one force transmission and / or force reduction element (22, 24) is formed monolithically with the parallelogram structure and is preferably arranged within the parallelogram.