Weighing system with unstabilized links

Abstract

The invention relates to a weighing system (10) comprising: a base (12); a load receiving portion (14) hinged to the base portion (12) by means of a parallel guide assembly; a transmission link (24) pivotably hinged to the base (12) by means of a transmission link hinge (25), a first transmission link arm (241) of the transmission link being connected to the load receiving part (14) via a load coupling belt (28) and a second transmission link arm (242) carrying at least one element of an electromagnetically compensated sensor assembly (26); and a non-stabilization force generating element fixed on one side to the base (12), by means of which a non-stabilization force that can be introduced into an introduction point (32) of the transmission link (24) can be generated. The invention is characterized by an unstabilizing link (36) which is pivotably hinged to the base (12) by means of an unstabilizing link hinge (40), a first unstabilizing link arm (361) of the unstabilizing link being connected to the introduction point (32) via an unstabilizing coupling strip (34) and a second unstabilizing link arm (362) of the unstabilizing link being operatively connected to the unstabilizing force-generating element.

Description

Technical Field

[0001] This invention relates to a weighing system, comprising: - Base; - Load-bearing portion hinged to the base by means of parallel guide assembly; - A transmission link hinged to a base in a swingable manner via a transmission link hinge joint; the first transmission link arm of the transmission link is connected to a load receiving portion via a load coupling belt; and the second transmission link arm of the transmission link carries at least one element of an electromagnetically compensated sensor assembly; and - An unstable force generating element fixed to the base on one side can generate an unstable force that can be introduced into the lead-in point of the transmission link. Background Technology

[0002] Gravity measuring devices (i.e. weighing devices) that operate based on the principle of electromagnetic compensation have long been known to those skilled in the art. For example, EP 2 690 415 A1 discloses a weighing device.

[0003] The basic principle is that the deflection of the load-bearing part relative to the base caused by the weight of the load is transmitted to the sensor via a transmission link after force ratio and displacement ratio conversion. The sensor itself is capable of applying an electromagnetic force to the link arm in the opposite direction of the deflection. This compensating force depends on the current supplied to the coil of the moving coil assembly that generates the compensating force. If the current is selected such that the deflection of the transmission link caused by the load is accurately compensated—that is, the link arm remains in its equilibrium position even when the load is applied—then the compensating current represents a precise quantification of the required compensating force and, consequently, the weight of the applied load.

[0004] Technically, such a system is generally implemented as follows: A parallel guide assembly is used to hinge the load-bearing portion, to which the weighing container is coupled or can be coupled, to a stationary base. Thus, when the weighing equipment is correctly positioned, its degrees of freedom of motion (at least in the case of minor deflections) are restricted to a generally vertical, non-tilting motion. The load-bearing portion is hinged to the drive link via a so-called coupling band, particularly to the link arm on the load-bearing side of the drive link. Here, the coupling band should be understood as a generally elongated coupling portion that is generally flexible only in the bending direction. For this purpose, thin strips are typically used, often with a thinning section near their fixed end, so that the band, already generally flexible only in one dimension due to its shape, is actually hinged at its fixed point. The drive link is supported in a swinging motion on a link hinge (here referred to as the drive link hinge) fixed relative to the base. This support section marks the boundary between the linkage arm on the load-bearing side (referred to herein as the first drive linkage arm) and the linkage arm on the sensor side (referred to herein as the second drive linkage arm). At the end of the linkage arm on the sensor side, the coil of the moving coil assembly is typically fixed, submerged in the magnetic field of a cup-shaped magnet (usually a permanent magnet) fixed relative to its base. An opposite arrangement of the coil fixed relative to its base and the magnet (permanent magnet) fixed relative to the linkage is also conceivable, but uncommon. The position of the drive linkage under a pre-defined reference load (generally unloaded in conventional scales and loaded in comparators) represents its equilibrium position. This equilibrium position can be detected by a separate position sensor (usually operating on optical principles), or the linkage can be adjusted so that it is in the position interpreted as equilibrium by the position sensor under the reference load condition. When the coil is energized, a magnetic field corresponding to the coil current is generated. This magnetic field interacts with the magnetic field of the permanent magnet, thereby creating a force on the linkage arm on the sensor side. Conversely, placing a load on the load-bearing section will cause the connecting arm on the load-bearing side to be subjected to mechanical force. With proper control, such a device can operate such that any (infinitely small) deflection of the transmission link caused by the load will be detected by the position sensor and converted into a compensating current change in the coil. In this way, the transmission link (except for the infinitesimal deflection) is kept in its equilibrium position, where the current flowing through the coil at the end of the oscillation decay process will represent the load placed on the load-bearing section. By measuring the coil current accordingly, the weight of the load can be determined with extremely high accuracy.

[0005] The mechanical components of this complex system are technically referred to as a weighing system. Such weighing systems, often manufactured with extremely high precision and typically as a single unit, may still deviate from an ideal system despite employing state-of-the-art precision technology. This deviation is particularly evident in the so-called stiffness of the hinges within such systems. "Stiffness" refers to the restoring force exerted by a real hinge (compared to an ideal hinge) against its deflection. It is generally impossible to define the position where the linkage hinge is exactly not deflected—that is, the position where there is no torque caused by stiffness—as the equilibrium position of the linkage. Instead, under normal circumstances, a position sensor defines a slightly off-center link position as the equilibrium position. To maintain this equilibrium position against the torque caused by stiffness, a coil current may be required in the moving coil assembly; this coil current is referred to below as the offset current. In this respect, it will be called "zeroing" the scale. However, another deviation from an ideal system lies in the final resolution of the position sensor's ability to detect the position of the linkage (especially its equilibrium position). Therefore, deviations below this resolution limit from the defined equilibrium position will result in a torque due to stiffness, but not compensated for by zeroing, which (in positive or negative form) is added to the torque caused by the weight of the load. Given a deviation in the linkage position, the magnitude of this "error" torque is related to the actual stiffness of the hinge. A technique called astasierung is employed to minimize the slope of this essentially linear dependence, thereby keeping the error torque as low as possible due to the unavoidable actual deviation from the defined equilibrium position caused by the limited resolution of the position sensor.

[0006] Various destabilization methods are known to those skilled in the art. One known destabilization method is that the connecting rod can be designed with its center of gravity above the connecting rod hinge, i.e., above its precise swing axis. This causes instability in the connecting rod's equilibrium position: any deflection of the connecting rod will result in a torque that exacerbates the deflection due to the increased center of gravity. This torque will counteract the reverse stiffness torque at the connecting rod hinge. Conversely, stabilization can be achieved by shifting the connecting rod's center of gravity below its swing axis. The disadvantage of this method is that both the stiffness of the connecting rod hinge and the position of its center of gravity are subject to manufacturing deviations, and therefore can only precisely compensate for each other in very few special cases. Furthermore, it exacerbates the system's susceptibility to tilting. Those skilled in the art will recognize that relative directional terms such as "above" or "over" and "below" or "under" herein should be understood within the context of a fully functional scale and its prescribed orientation.

[0007] A similar but less tilting solution is based on the principle known from EP 0 359 978 B1, which forms the class as described at the beginning. In this solution, the connecting rod carries a coupling portion above its connecting rod hinge for one end of a tension spring, the other end of which is fixed to the base, thus causing the tension spring to be vertically tensioned over the connecting rod hinge. The connecting rod is thus loaded with a downward-acting, vertical force extending through the connecting rod hinge. This force is introduced into the connecting rod via the spring coupling portion, which serves as the point of introduction for the destabilizing force. However, this mechanical implementation disclosed in this document from approximately 35 years ago, while still considered a very advantageous principle, is no longer compatible with modern high-resolution scales. It is particularly desirable to reduce the force acting on the connecting rod hinge in the equilibrium position to prevent material creep in the hinge region, which is typically constructed as an extremely finely thinned section. Furthermore, the direction of the spring force of a tension spring constructed as a helical spring is difficult to reproduce completely so that it extends precisely through the swing axis of the transmission link in all cases, which is necessary for modern high-resolution scales.

[0008] Invention Task

[0009] The objective of this invention is to provide a mechanical implementation of the destabilization principle known from the printed literature that forms the category, compatible with modern weighing systems. Summary of the Invention

[0010] The task is addressed in conjunction with the features described in the preamble of claim 1 by means of an unstable link that is hinged to the base in a swingable manner via an unstable link hinge, wherein the first unstable link arm of the unstable link is connected to the introduction point via an unstable coupling band, and the second unstable link arm of the unstable link is operatively connected to an unstable force generating element.

[0011] The preferred embodiments are the subject of the dependent claims.

[0012] The basic concept of this invention is that the destabilizing force generating element, preferably constructed as a spring, especially as a tension spring, is not directly coupled to the input point, but rather indirectly coupled to the input point via an additional mechanical structure consisting of a destabilizing link and a destabilizing coupling band. By using the destabilizing coupling band, the direction of the destabilizing force acting on the input point can be defined significantly more precisely than when a tension spring, for example, constructed as a helical spring, is coupled there.

[0013] Furthermore, the redirection of the unsteady force by means of the unsteady link can lengthen the entire force flow path, especially the straight end section terminating at the introduction point. Given an unsteady force, the length of this end section of the force flow path is decisive for the strength of the unsteady torque generated when the transmission link deviates from its equilibrium position. The greater the torque obtainable under a given force, the smaller the force required to obtain the desired unsteady torque is chosen. The reduction in the unsteady force introduced at the introduction point also results in a reduction in the load on the transmission link hinge when the transmission link is in its equilibrium position. Accordingly, the risk of material creep in the fine transmission link hinge due to continuous loading caused by the unsteady force applied, for example, as a spring force, is also lower. With the same structural space and the same desired unsteady torque, the indirect introduction of the unsteady force according to the invention enables a more refined design of the weighing system, which is beneficial to its sensitivity and therefore to the resolution of the corresponding scale.

[0014] As previously stated, even in the case of the weighing system according to the invention, the unstabilizing force generating element is preferably constructed as a spring, particularly as a tension spring. A first end of the spring is fixed to the base, and its second end is fixed to the second unstabilized link arm. This fixing method can be hinged. However, the inherent flexibility of the spring is usually sufficient to compensate for the minor deviation from purely linear motion that occurs at the end of the second unstabilized link arm when the expected small deflection of the unstabilized link occurs. Compensation is achieved at the other (i.e., the first) unstabilized link arm by the characteristics of a coupling band, the flexibility of which is precisely defined or limited by its shape.

[0015] As is known from the prior art, the point of introduction for the destabilizing force is preferably located above the hinge of the transmission link or above the swing axis defined by the hinge. When the tension generated on the other side of the rotation axis is used as the destabilizing force, instability occurs. In other words, in this embodiment, the stiffness of the transmission link hinge, determined by its material and shape, is canceled out. If, in certain cases, it is desired that the destabilizing force has a stabilizing effect, then in the corresponding embodiment, the point of introduction can instead be located below the hinge of the transmission link or below the swing axis defined by the hinge.

[0016] Advantageously, the introduction point is axially aligned with the hinge portion of the transmission link, or the swing axis. Here, the direction "axial" refers to the longitudinal extension direction of the transmission link. Within the scope of this specification, the simplified expression "(regarding...link) axial" is also used for this and similar situations. When the transmission link is precisely horizontally oriented in its equilibrium position, the introduction point is preferably precisely vertically positioned above the swing axis. The point where the link-side end of the destabilizing coupling belt is fixed to the destabilizing link should be located as precisely as possible on the extension of the line connecting the introduction point and the swing axis of the transmission link; therefore, in common embodiments, this point is precisely vertically positioned below the swing axis of the transmission link. However, especially when using a long coupling belt, the accuracy of the positioning of this fixing point is not as critical as the accuracy of the positioning of the introduction point relative to the hinge portion of the transmission link. However, as long as the hinge portion of the transmission link (again) can support non-vertical forces, the line of action of the destabilizing force can be tilted or even laterally relative to the vertical distance between the axis of rotation and the longitudinal extension of the link. However, in any case, the line of action of the unstabilizing force should intersect the axis of rotation as precisely as possible.

[0017] Especially when the entry point is located above the hinge of the transmission link, it is advantageous that the transmission link has at least two laterally spaced legs in the region of the hinge, between which the unstable coupling band is guided. The functional transmission link hinge is divided into two spaced-apart (preferably at the thinner material section) structural hinges that together form the swing axis of the transmission link. Sufficient space exists between these two structural hinges, or thinner material sections, that connect one of the parallel legs of the transmission link to the base, so that the unstable coupling band can be guided through the transmission link to the unstable link.

[0018] Despite the advanced manufacturing techniques, particularly in precision milling for integrated weighing systems, minor manufacturing tolerances can still occur, affecting the relative positioning of the aforementioned introduction point and the drive linkage hinge. To compensate for this, an improvement of the invention proposes that the introduction point be configured to be axially adjustable with respect to the longitudinal extension direction of the drive linkage. In other words, in this embodiment, the introduction point is arranged to be movable in the longitudinal extension direction of the drive linkage. This allows manufacturing tolerances to be compensated for in individual cases through appropriate adjustments, ensuring that the direction of introduction of the unsteady force extends precisely through the drive linkage hinge, or the swing axis of the drive linkage.

[0019] Such an adjustment mechanism capable of compensating for micrometer-level or even submicrometer-level deviations is not easy to achieve. One mechanically feasible solution involves placing the entry point on a slider that moves axially along the longitudinal extension of the connecting rod, and this slider is indirectly force-loaded against a stop fixed to the connecting rod via a wedge that can be adjusted transversely to the longitudinal extension of the connecting rod. The transverse movement of the wedge to the axial direction of the connecting rod causes a change in the distance between the edge of the slider abutting the wedge and the stop fixed relative to the connecting rod. Therefore, when the wedge is pulled back, the axial force on the slider pushes it towards the stop. Conversely, when the wedge is pushed forward, this distance increases over the force acting on the slider. For example, the movement of the wedge can be achieved by an adjusting screw with fine threads. For example, a spring can cause a force loading on the slider. However, the inherent elasticity of the material (usually an aluminum alloy) is generally sufficient to accommodate the minimal movement of the slider required for adjustment.

[0020] Alternatively or additionally, the entire unstable link can be movable relative to the base, or at least the fixed point where the unstable coupling band is fixed to the first unstable link arm can be movable relative to the unstable link, more precisely, configured to be axially movable (with respect to the unstable link). This movement can also affect the inclination of the unstable coupling band, and in particular, be adjusted so that the line of action of the unstable coupling band, or the unstable force mediated by it, extends precisely through the axis of rotation of the transmission link. The movement of the entire unstable link can be performed, in particular, by moving its unstable link hinge portion using a suitable displacement mechanism mounted at the base. Individual movement of the fixed point of the unstable coupling band can be performed by means of a suitable displacement mechanism mounted on the unstable link. Compared to the aforementioned variant where the entry point can move relative to the transmission link, this implementation even has the advantage of being less sensitive to adjustment and therefore, in principle, more mechanically feasible. The reason for this is that the distance between the rotation axis of the transmission link and the introduction or fixing point of the unstabilized coupling band at the unstabilized link is usually large. However, in practice, the structural space in the unstabilized link region is limited and / or difficult to access, making the adjustment possibilities arranged here operationally difficult.

[0021] Advantageously, the strength of the destabilizing force can be adjusted (if necessary). In the preferred case where the destabilizing force generating element is designed as a spring (especially a tension spring), this can be achieved by adjusting the fixed position of the spring at its base along the direction of the spring's force. In other words, the spring's preload is changed. This compensates for manufacturing tolerances in the spring and the hinge itself. Attached Figure Description

[0022] For further details and advantages of the present invention, please refer to the detailed embodiments and accompanying drawings below.

[0023] In the attached diagram: Figure 1 A highly schematic illustration of the weighing system according to the present invention is shown; Figure 2 It is shown in the form of a schematic side view. Figure 1 Enlarged view of the hinge joint of the transmission link in the weighing system; and Figure 3 It is shown in the form of a schematic front view. Figure 1 Enlarged view of the hinge joint of the transmission link in the weighing system.

[0024] In the accompanying drawings, the same reference numerals refer to the same or similar elements. Detailed Implementation

[0025] Figure 1 A highly schematic side view of a weighing system 10 according to the invention is shown. Only the base 12 of the weighing system 10, commonly referred to in technical terms as the "fixed portion" or "system carrier," is shown. The weighing system 10 has a Robertwal mechanism by which the load-bearing portion 14 is hinged to the base 12 via two parallel links 16a, 16b. By means of a hinge portion, referred to herein as the Robertwal hinge portion 18, which is preferably constructed as a thinner section of material, one side of the two parallel links 16a, 16b is hinged to the base 12 and the other side to the load-bearing portion 14. The load-bearing portion 14 is connected to the weighing carrier 20, wherein, in the illustrated embodiment, this connection is achieved via a cantilever 22.

[0026] Furthermore, the weighing system 10 also includes a transmission link 24, which is composed of a first transmission link arm 241 and a second transmission link arm 242 on the load-bearing side. The boundary axis between the first transmission link arm and the second transmission link arms 241, 242 is located at the height of the transmission link hinge portion 25, which is preferably constructed as a thinner section of material, and the transmission link 24 is hinged to the base 12 in a swingable manner by means of this transmission link hinge portion. The second transmission link arm 242 carries components of the sensor assembly 26 at its free end. In the illustrated case, this is first the moving coil 261 of an electromagnetically compensated sensor, which also includes a cup-shaped magnet 262 fixed relative to the base. In addition, the second transmission link arm 242 also carries a target 263 of an optical position sensor (the rest of which is not shown).

[0027] The free end of the first transmission link arm 241 is connected to the load receiving part 14 via a load coupling belt 28. In particular, the load coupling belt 28 may be made of a slat, which has coupling belt hinges 30 near its two ends, which are constructed as thinner sections of material.

[0028] In this respect, the weighing system according to the invention is no different from known weighing systems for electromagnetically compensated scales (EMF scales) and is consistent with them in terms of basic function. The weight placed on the weighing carrier 20 exerts a weight force on the load receiving portion 14, which tends to yield to this weight force by a vertically downward deflection. This force, or the resulting tendency to deflect, is transmitted via the load coupling belt 28 to the transmission link 24, whose first transmission link arm 241 tends to be pulled downward and whose second transmission link arm 242 tends to be pushed upward. This deflection is detected by an optical position detector, and a current of appropriate strength is supplied to the coil 261 of the sensor 26 so that the deflection is completely suppressed and the transmission link 24 is held in its equilibrium position after the oscillation decay process ends. The compensation current flowing through the coil 261 required for this represents the weight force exerted by the weighing object.

[0029] The present invention is particularly relevant to a specific manner in which an unstable force is introduced into the transmission link 24. For easier identification, Figure 1 In this context, the corresponding institutions are presented in a highly distorted and unadjusted manner. Conversely, in Figure 2 and Figure 3 The diagram shows the link 24 in its correct, adjusted position. An entry point 32 is located above the hinge 25 of the drive link 24, which is movable in the longitudinal or axial direction of the drive link 24. The diagram schematically shows this entry point on the upper leg of a cantilever. However, in practice, this entry point is typically located directly on the upper side of the drive link 24 itself. Under operating conditions, such as... Figure 2 and Figure 3As shown, the entry point 32 should be precisely located above the swing axis formed by the drive link hinge 25, or at least be able to be positioned in this location through appropriate adjustment. Here, this optimal adjustment is also understood to make the entry point axially co-located with the swing axis. The entry point 32 is connected to the first link arm (here referred to as the first unstable link arm 361) of the unstable link 36 via the unstable coupling band 34. The unstable coupling band 34 is preferably constructed as a slat, similar to the load coupling band 28, which carries the coupling band hinge 38 (constructed as a material thinning section) in its end region. In the illustrated embodiment, the unstable link 36 is arranged below the drive link 24 and is hinged to the base 12 in a swingable manner via the unstable link hinge 40, which is preferably constructed as a material thinning section. The unstable link is specifically positioned such that the coupling point of its first unstable link arm 361 with the unstable coupling band 34 is largely and precisely located below the swing axis of the transmission link 24 formed by the transmission link hinge 25. However, this is not absolutely necessary (at least if the transmission link hinge 25 is also capable of supporting non-vertical forces). The second link arm of the unstable link 36, referred to herein as the second unstable link arm 362, is preloaded relative to the base 12 via a spring 42 configured herein as a tension spring. In the illustrated embodiment, the tension spring 42 applies an upward force to the second unstable link arm 362.

[0030] like Figure 2 and Figure 3 As shown, when correctly positioned after adjustment, the force is redirected by the destabilizing link 36 and introduced into the introduction point 32, so that the force acting on the transmission link 24 when it is in the equilibrium position extends precisely through the swing axis defined by the transmission link hinge 25. Therefore, the force is completely supported by the transmission link hinge 25. No torque is generated acting on the transmission link 24. Conversely, when the transmission link 24 deflects out of its equilibrium position, especially due to the weight of the load placed on the weighing carrier 20, the force flow line will be displaced and extend axially past the pivot axis. Thus, the transmission link hinge 25 no longer fully supports the introduced destabilizing force, and this generates a destabilizing torque that exacerbates the deflection of the transmission link 24 caused by the weight, thereby canceling out the opposing torque caused by stiffness.

[0031] The advantage of introducing the destabilizing force generated by the spring 42 indirectly via the destabilizing link 36 and the destabilizing coupling band 34 is that the direction of action of the introduced destabilizing force in the region of the transmission link hinge 25 can be precisely defined (unlike the case where the spring 42 is directly coupled to the introduction point 32). This allows the destabilizing effect to be reproduced to a high degree, or even precisely adjusted as in the embodiment shown.

[0032] Figure 3 It shows Figure 2 The image shows a front view of a section of the weighing system 10, as shown in the side view. In this preferred embodiment, the transmission link 24 is constructed as two parallel legs 24a, 24b, at least in the region of the transmission link hinge 25. In this embodiment, the transmission link hinge 25 is constructed as two spaced-apart thinned material portions 25a, 25b that together define the swing axis of the transmission link 24. In this embodiment, the destabilizing coupling band 34 may extend between the two legs 24a, 24b of the transmission link 24, or between the two thinned material portions 25a, 25b of the transmission link hinge 25.

[0033] Of course, the embodiments described and illustrated in the specific embodiments are merely illustrative examples of the invention. Given this disclosure, those skilled in the art will find a wide range of possible variations. In particular, variations are conceivable in which the spring 42 is configured as a compression spring rather than a tension spring, and / or acts in the opposite direction to the second destabilizing link arm 362. It is also conceivable that the introduction point 32 is arranged below rather than above the pivot axis of the transmission link 24. Those skilled in the art can thus achieve the desired positive or negative destabilizing effect in individual cases. Regarding the specific mechanical structure for the possible axial adjustability of the introduction point 32, those skilled in the art can also employ all known and possibly yet-to-be-developed precision mechanical implementations.

[0034] List of reference numerals

[0035] 10 Weighing System

[0036] 12 base

[0037] 14 Load-bearing section

[0038] 16a Upper parallel link

[0039] 16b Lower parallel link

[0040] 18. Robeval Hinge

[0041] 20 Weighing Carrier

[0042] 22 Cantilever

[0043] 24. Transmission connecting rod

[0044] 24a 24 outriggers

[0045] 24b 24's support legs

[0046] 241 First transmission link arm

[0047] 242 Second transmission link arm

[0048] 25. Connecting rod hinge section

[0049] 25a 25 Thinning area of ​​material

[0050] 25b 25 Thinning area of ​​material

[0051] 26 Sensor Components

[0052] 261 Dynamic

[0053] 262 Cup-shaped magnet

[0054] 263 targets

[0055] 28 Load coupling band

[0056] 30. Coupling band hinge section

[0057] 32 Introduction Point

[0058] 34 Unstable coupling band

[0059] 36 Unstable connecting rod

[0060] 361 First Unstable Linkage Arm

[0061] 362 Second Unstable Linkage Arm

[0062] 38. Coupling band hinge section

[0063] 40 Unstable connecting rod hinge

[0064] 42 Springs

Claims

1. A weighing system (10), comprising: - Base (12); - The load-bearing portion (14) is hinged to the base (12) by means of a parallel guide assembly. - A transmission link (24) is hinged to the base (12) in a swingable manner by means of a transmission link hinge (25), the first transmission link arm (241) of the transmission link is connected to the load receiving part (14) via a load coupling belt (28), and the second transmission link arm (242) of the transmission link carries at least one element of the electromagnetic compensation sensor assembly (26); as well as - An unstable force generating element fixed to the base (12) on one side, by means of which an unstable force can be generated and introduced into the introduction point (32) of the transmission link (24), Its characteristics include An unstable link (36) is hinged to the base (12) in a swingable manner by means of an unstable link hinge (40). The first unstable link arm (361) of the unstable link is connected to the lead point (32) via an unstable coupling band (34), and the second unstable link arm (362) of the unstable link is operatively connected to the unstable force generating element.

2. The weighing system (10) according to claim 1. Its features are, The destabilizing force generating element is configured as a spring (42), with a first end of the spring fixed to the base (12) and a second end of the spring fixed to the second destabilizing link arm (362).

3. The weighing system (10) according to claim 2. Its features are, The spring (42) is configured as a tension spring.

4. The weighing system (10) according to any one of the preceding claims. Its features are, The inlet point (32) is located above the hinge part (25) of the transmission link.

5. The weighing system (10) according to any one of the preceding claims. Its features are, The inlet point (32) and the swing axis of the transmission link (24) defined by the hinge portion (25) of the transmission link (24) are axially co-located about the transmission link (24).

6. The weighing system (10) according to any one of the preceding claims. Its features are, The transmission link (24) has at least two legs (24a, 24b) that are laterally spaced from each other in the region of the transmission link hinge (25), and the destabilizing coupling band (34) extends between the two legs (24a, 24b).

7. The weighing system (10) according to any one of the preceding claims. Its features are, The inlet point (32) is configured to be axially adjustable with respect to the transmission link (24).

8. The weighing system (10) according to claim 7. Its features are, The inlet point (32) is arranged on a slider that can move axially on the transmission link (24) about the transmission link. The slider is indirectly loaded by force against a stop that is fixedly connected to the transmission link via a wedge that is adjustable in the transverse direction of the axial direction of the transmission link.

9. The weighing system (10) according to any one of the preceding claims. Its features are, The fixed point of the unstable coupling band (34) to the first unstable link arm (361) is configured to be axially movable relative to the unstable link about the unstable link (36).

10. The weighing system (10) according to any one of the preceding claims. Its features are, The unstable link hinge (40), together with the unstable link (36), is configured to be axially adjustable relative to the base (12) about the unstable link (36).

11. The weighing system (10) according to any one of the preceding claims. Its features are, The intensity of the destabilizing force is adjustable.

12. The weighing system (10) according to claim 11 when any one of claims 2 to 3 is invoked. Its features are, The fixed position of the spring (42) at the base can be adjusted along the direction of the force of the spring (42).

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