Decoupling device for vibrating systems

Abstract

A decoupling device (50) of vibrating systems comprises at least one nonlinear stiffness element with negative stiffness k nl (u) comprising at least one first spring element (27) and at least one linear stiffness element with positive stiffness k connected thereto in parallel l,stat , which has at least one second spring element (28). The at least one nonlinear stiffness element with negative stiffness k nl (u) is in series with at least one other stiffness element with a linear stiffness K l , which has at least one third spring element (29), connected, and this series connection is in parallel with the at least one linear stiffness element with positive stiffness k l,stat connected, wherein a quasi-zero-stiffness isolator with increase of the amount of negative stiffness k nl,ser,tot (u) is formed.

Description

[0001] The present invention relates to a decoupling device for vibrating systems according to the preamble of claim 1.

[0002] The dynamic isolation or decoupling of structures using such decoupling devices is employed to reduce vibration transmission and noise emissions. This includes vibrations in both translational and rotational directions (torsional vibrations). Elastic bearings or couplings are typically used for isolation. These elements exhibit a positive and approximately constant stiffness. To achieve a sufficiently low overall stiffness for isolation purposes and simultaneously limit the deformation of each element to an acceptable level, several of these linear elements are, for example, connected in series.

[0003] Besides the use of linear decoupling elements, approaches also exist with nonlinear elements whose stiffness does not have a constant value, but varies depending on the deformation. These include, among others, so-called quasi-zero-stiffness concepts.

[0004] Fig. Figure 1a shows a schematic symbolic representation of a spring arrangement 1' from the prior art.

[0005] The spring arrangement 1' represents a parallel connection of stiffnesses k 1,stat and k n1 (u) for vibration isolation (quasi-zero-stiffness isolator).

[0006] The “parallel connection” of stiffnesses or spring elements means that a first end of the first spring element is connected to a first end of the second spring element, and that a second end of the first spring element is connected to a second end of the second spring element.

[0007] The term "series connection" or "connected / arranged in series" means that a second end of a first spring element is connected to a first end of a second spring element, etc.

[0008] The spring assembly 1' comprises a first spring element 2 and a second spring element 3. The first spring element 2 is a linear spring element with a constant stiffness k. 1,stat and is to the second spring element 3, which is a non-linear spring element 3 with a stiffness k n1 (u) is arranged in parallel.

[0009] The spring elements 2, 3 are each attached at a first end to a frame 4, with their other ends attached to an exemplary plate 5, on which a load L acts in a direction of a path u and deflects the spring elements 2, 3 in the direction of the path u.

[0010] The second, nonlinear spring element 3 exhibits a negative stiffness for certain deformations. A stiffness characteristic curve 100 belonging to the first spring element 2 and a stiffness characteristic curve 101 belonging to the second spring element 3 are shown in a diagram of stiffness characteristics in Fig. 2 shown.

[0011] If the magnitude of the negative stiffness of the second spring element 3 corresponds to the stiffness value of the linear first spring element 2, then the parallel connection of both spring elements 2 and 3 results in a non-linear stiffness characteristic 104 with stiffness k n1,tot (u), which exhibits vanishing stiffness within the working range. This achieves optimal vibration isolation of the system while simultaneously ensuring the transmission of the static load (see load characteristics 200, 201 and 204 in Fig. 3.

[0012] Document DE 10 2022 117 077 A1 describes an "Optimized torsional vibration isolation using a nonlinear characteristic curve of an element with negative torsional stiffness" and relates to a torsional vibration isolated coupling with a rotation axis, comprising a first coupling part as the input side of the coupling, a second coupling part as the output side of the coupling, and a damping unit. The damping unit has at least one spring arrangement designed as a nonlinear spring arrangement with a degressive spring characteristic curve.

[0013] Document DE 10 2022 128 006 A1 concerns a "coupling element for realizing a nonlinear torsional spring characteristic with negative torsional stiffness" and describes a torsionally isolated coupling element with one axis of rotation. It comprises an outer ring as the input side of the coupling element, an inner ring as the output side of the coupling element, and at least one energy storage unit with at least one energy storage element. The torsional vibration isolated coupling element exhibits a nonlinear torsional stiffness.

[0014] A conflict of objectives exists between the transmission of static loads (forces and torques) and the decoupling of vibrations resulting from dynamic load fluctuations. High stiffness is required to transmit the static load with minimal deformation of the connecting element. Conversely, minimal stiffness is necessary for the dynamic decoupling of the system. To meet both requirements, a series connection of linear stiffness elements is typically used. This allows for low overall stiffness (isolation) combined with low static deformation per element. However, the minimum achievable overall stiffness k is l,tot by the finite number N of interconnected stiffness elements k i limited to a lower value, see equation (1). 1kl,tot=∑i=1N1kl=1kl+1k2+⋯+1kN

[0015] Against this background, the use of nonlinear connecting elements with degressive stiffness is advantageous. Here, the transmitted load initially increases with increasing deformation of the element until a nearly constant load level is reached at the operating point (OP). These nonlinear elements with vanishing stiffness at the operating point (quasi-zero stiffness isolators) enable the transmission of static loads and also ensure optimal decoupling of the system from load fluctuations at the operating point.

[0016] To achieve the degressive spring characteristic, a spring element with a sufficiently high positive stiffness k is used. 1,stat (Transfer of the static load) around a parallel-connected nonlinear stiffness element k nl (u) supplemented with a corresponding negative stiffness at the operating point u*, as in Fig. 1 is shown. knl,tot(u)=k1,stat+knl(u) with knl(u*)<0

[0017] The resulting total stiffness k nl,tot (u*) at the operating point is defined by the degree of decoupling ε. knl,tot(u*)=(1−ε)k1,stat

[0018] Optimal insulation (complete compensation of the linear stiffness k) 1,stat) At the operating point, a decoupling degree ε = 1 is achieved. knl,tot(u*)=−k1,stat

[0019] Various concepts exist for realizing nonlinear connecting elements with negative stiffness (hereinafter also referred to as NeSt elements). These are typically based on one or more energy storage elements. When a static load is applied, energy is initially stored in these elements (e.g., by tensioning or compressing mechanical springs). Above a certain degree of deformation, the stored energy reaches its maximum and is released again if the NeSt element deforms beyond this point. The released energy reduces the force or torque required for further deformation of the element, thus resulting in negative stiffness.

[0020] A fundamental problem with NeSt elements is their limitation in providing sufficiently high negative stiffness values. The technical limits to achieving high negative stiffness values ​​are determined, among other things, by the permissible stress values ​​and maximum load-bearing capacities of the components used in the NeSt elements (e.g., springs, levers, bearing elements, etc.).

[0021] The invention is therefore based on the objective of creating an improved decoupling device for oscillating systems.

[0022] This problem is solved by an improved decoupling device for vibrating systems with the features of independent claim 1.

[0023] In order to achieve the negative stiffness values ​​required for sufficient decoupling within the aforementioned limits, a concept for increasing the negative stiffness of a decoupling device is presented according to the invention.

[0024] The present invention presents a device for decoupling vibrating systems based on a nonlinear spring characteristic with zero stiffness at the operating point (quasi-zero stiffness isolator). Application areas include, for example, earthquake protection of buildings, isolation of measuring setups, or torsional vibration isolation of drive trains.

[0025] Accordingly, a decoupling device for vibrating systems comprises at least one nonlinear stiffness element with negative stiffness k. nl(u) comprising at least one first spring element and at least one linear stiffness element with positive stiffness k connected thereto in parallel l,stat , which has at least one second spring element. The at least one nonlinear stiffness element has negative stiffness k. nl (u) is in series with at least one other stiffness element with a linear stiffness K l , which has at least one third spring element (29), connected, and this series connection is in parallel with the at least one linear stiffness element with positive stiffness k l,stat connected, wherein a quasi-zero-stiffness isolator with increase of the amount of negative stiffness k nl,ser,tot (u) is formed.

[0026] The novel and advantageous feature of this decoupling device lies in the fact that, in addition to the parallel connection of the linear spring element and the nonlinear spring element with negative stiffness, the latter is supplemented by an additional linear spring element connected in series. This makes it possible to significantly increase the magnitude of the negative stiffness and to ensure almost linear behavior outside the operating range.

[0027] This additional reinforcement enables the use of NeSt elements with comparatively low negative stiffness values, which, due to the correspondingly low mechanical stresses, can be implemented much more easily within technical limits. Consequently, significantly higher decoupling coefficients ε can be achieved with technically feasible NeSt mechanisms through the targeted tuning of the series-connected nonlinear and linear springs.

[0028] Further advantageous embodiments of the invention can be found in the dependent claims.

[0029] In one embodiment, the decoupling device comprises at least one stiffness unit, which includes an input element, at least one output element, at least one first spring element, at least one second spring element, at least one third spring element, a first slide, a second slide, and linear guides, wherein the second slide is slidably guided in / on the output element. This results in an advantageously simple and compact design.

[0030] In a further embodiment, the first slide is connected to the input element via the at least one third spring element and coupled to the second slide via a coupling unit, wherein the at least one first spring element is arranged between the second slide and the output element, and wherein the at least one output element is connected to the input element via the at least one second spring element.

[0031] Through the targeted coordination of the spring elements connected in series with k l and k nl (u) according to equation (6) it is possible to determine a nonlinear stiffness k nl,ser (u) to generate whose negative stiffness value is significantly larger than the corresponding stiffness value of the nonlinear single spring element (k nl,ser (u*) < k nl (u) < 0).

[0032] In a further embodiment, the coupling unit has at least one lever which is articulated to the first slide with a first lever axis and to the second slide with a second lever axis.

[0033] Instead of the costly optimization of a complex NeSt mechanism, the simple selection of a suitable linear stiffness element k is advantageous. l This concept also allows for the subsequent strengthening of existing NeSt elements and their adaptation to different applications through the appropriate selection or adjustment of the linear stiffness k. l

[0034] The use of a lever or levers results in an advantageously simple construction.

[0035] An alternative design provides for the coupling unit to have a rolling mechanism (with a contour) and a rolling element. This allows for a simple design and easy assembly of the coupling unit.

[0036] In a further embodiment, the contour of the rolling mechanism is arranged on the first slide and the rolling element on the second slide, or the contour of the rolling mechanism is arranged on the second slide and the rolling element on the first slide. This design offers the advantages of simple construction and easy assembly.

[0037] Advantageously, the rolling element of the rolling mechanism can be a rotatably mounted ball, which is available as a cost-effective component of high quality.

[0038] In another alternative design, the coupling unit has at least one beam element. This offers the advantage of a simple, compact design.

[0039] Another embodiment provides that the decoupling device has a first stiffness unit and a second stiffness unit with identical construction, wherein the two stiffness units are arranged rotated by 180° within an interior space of the input element. This is particularly advantageous because it allows for the compensation of undesired force components.

[0040] In a further embodiment, the two stiffness units have a common first slide which is connected to the input element via the at least one first spring element, resulting in an advantageous compact design.

[0041] Furthermore, the following special advantages arise: Instead of a complex optimization of a complex NeSt mechanism, the simple selection of a suitable linear stiffness element k is used. l .

[0042] This concept also enables the subsequent strengthening of existing NeSt elements and their adaptation to different applications through the appropriate selection or adjustment of the linear stiffness k. l .

[0043] Some embodiments of the invention are described below with reference to the accompanying drawings. The invention is not limited to these embodiments. In particular, individual features of the following embodiments can be used not only in these but also in other embodiments. The drawings show: Fig. 1a a schematic symbolic representation of a spring arrangement from the prior art; Fig.1b to 1c schematic symbolic representations of reinforcement concepts according to the invention for a nonlinear stiffness of a spring arrangement; Fig. 2 exemplary representations of stiffness characteristic curves; Fig. 3 exemplary representations of load characteristics; Fig. Figures 4a to 4g are schematic representations of embodiments of the invention for nonlinear stiffness units with increased negative stiffness; and Fig. 5a-5c, 6a-6c, 7a-7c schematic representations of embodiments of decoupling devices according to the invention with nonlinear stiffness and increased negative stiffness.

[0044] In the following, terms such as "outside" or "inside", "below" or "above" refer to the respective drawing plane as well as "axial" and "radial".

[0045] Coordinates y and z, as well as path u, serve for orientation within the figures.

[0046] Fig.1a, which is state of the art, has already been described above.

[0047] In Fig. Figure 1b is a schematic symbolic representation of a first reinforcement concept according to the invention for a nonlinear stiffness of a spring arrangement 1".

[0048] Fig. 1c is a schematic symbolic representation of a second reinforcement concept according to the invention for a nonlinear stiffness of a spring arrangement 1'''.

[0049] Fig. Figure 2 shows exemplary representations of stiffness characteristic curves. Fig. Figure 3 shows exemplary representations of load characteristics.

[0050] The structure of a reinforcement concept for the nonlinear stiffness of the NeSt element is shown schematically in Fig. 1b shown. The corresponding stiffnesses and load distributions are shown in Fig. 2, Fig. 3 shown as an example for an optimal degree of decoupling ε = 1.

[0051] Fig.Figure 1b shows a series connection of stiffnesses k l and k nl (u) to increase the amount of negative stiffness NeSt.

[0052] In Fig. 1b A first spring element 2 and a second spring element 3 (viewed from the point of application of the load L) are connected in series and attached to the frame 4. The series connection of the first spring element 2 with a linear stiffness k l and of the second spring element 2 with a negative stiffness (NeSt stiffness) k nl (u*) results in the nonlinear stiffness k nl,ser (u*) according to equation (5). knl,ser(u*)=kl⋅knl(u*)kl+knl(u*)

[0053] In Fig. 1c is a parallel and series connection of stiffnesses k l , k l,stat and k nl (u) shown for vibration isolation (quasi-zero-stiffness isolator) with increase of the amount of negative stiffness.

[0054] Fig. Figure 1c shows the series connection of the two spring elements 2, 3 according to Fig. 1b, to which a further spring element 2a with a static stiffness k is added. l,stat is arranged in parallel.

[0055] In combination with this parallel static stiffness k l,stat According to equations (2) and (3), the nonlinear overall stiffness k results nı,ser,tot (u).

[0056] To achieve the desired degree of isolation ε at the operating point u*, the linear stiffness k is adjusted. l according to equation (6). kl=−ε⋅kl,stat⋅knl,serr(u*)ε⋅kl,stat+knl,serr(u*)

[0057] It should be noted that the magnitude of the negative stiffness can be increased arbitrarily as a result. The theoretically infinitely high gain values ​​for a vanishing denominator (k) l = k nlHowever, (u*)) in equation (5) are to be considered irrelevant for a technical application in vibration isolation, since the overcompensation (ε > 0) of the static stiffness k l,stat instability of the overall system (K nl,ser,tot (u*) < 0) would result. However, alternative applications for energy recovery are conceivable.

[0058] By the targeted coordination of the spring elements 2, 3 connected in series with k l and k nl (u) according to equation (6) it is possible to determine a nonlinear stiffness k nl,ser (u) to generate whose negative stiffness value is significantly larger than the corresponding stiffness value of the nonlinear single spring element 3 (k nl,ser (u*) < k nl (u) < 0).

[0059] Instead of the complex optimization of a complex NeSt mechanism, the simple selection of a suitable linear stiffness element k is used. lThis concept also allows for the subsequent strengthening of existing NeSt elements and their adaptation to different applications through the appropriate selection or adjustment of the linear stiffness k. l .

[0060] In Fig. Figure 2 shows a diagram in which stiffnesses k are plotted against the path u, where stiffness characteristics 100 to 104 are assigned to the above-mentioned stiffnesses k as follows: Stiffness characteristic 100 k l,stat Stiffness characteristic 101 k nl (in) Stiffness characteristic 102 k l Stiffness characteristic 103 k nl,ser (in) Stiffness characteristic 104 k nl,tot (IN) Stiffness characteristic 105 k nl,ser,tot (in)

[0061] In the diagram of Fig. 3. Loads L are plotted against the path u, with load characteristics 200 to 204 being assigned to the above-mentioned stiffnesses k as follows: load characteristic 200 k l,stat load characteristic 201 k nl (in) load characteristic 202 k l load characteristic 203 k nl,ser (in) load characteristic 204 k nl,tot (IN) load characteristic 205 k nl,ser,tot (in)

[0062] The reference symbol OP denotes the operating point.

[0063] Fig.Figures 4a-4g show schematic representations of embodiments of the invention for nonlinear stiffness units 10 with enhanced negative stiffness. The stiffness units 10 are also referred to as negative stiffness mechanisms (NeSt mechanisms).

[0064] The examples of implementation in the Fig. Figures 4a–4f show translational stiffness units 10. These representations can also be converted into corresponding rotational elements. An example of this is shown. Fig. 4g.

[0065] A first embodiment of the stiffness unit 10 in Fig. 4a comprises an input element 11, two slides 12, 12a, two first spring elements 13, lever 14 with lever axes 14a, 14b, an output element 15 and a second spring element 16.

[0066] The input element 11 is also referred to as the input side of the stiffness unit 10, while the output element 15 is also called an output side of the stiffness unit 10.

[0067] The input element 11 and the output element 15 are connected via a coupling unit KE, which connects the first slide 12, mounted on the first spring elements 13, with the second slide 12a, which is in contact with the second spring element 16. In this first embodiment, the coupling unit KE is formed by the stiffness unit 10 from the levers 14.

[0068] The entrance element 11 has a base wall 11a that extends in the direction of the path u. The base wall 11a is provided with a side wall 11b at each of its two ends. The side walls extend downwards at right angles to the u-direction and define an interior space 11c between themselves and the underside of the base wall 11a.

[0069] The first slide 12 is slidably guided in the u-direction within the interior space 11c of the entrance element 11. A first spring element 13 is located between each end face of the first slide 12 and the opposite side wall 11b. The first spring elements 13 are pre-tensioned such that the first slide 12 is positioned centrally within the interior space 11c.

[0070] The first slide 12 is pivotally connected to the levers 14 on a respective outer side in a first lever axis 14a.

[0071] In the second lever axis 14b of the levers 14, these are hinged to the outsides of a second slide 12a.

[0072] The second slide 12a is arranged in an interior space 15b of the output element 15 between two side walls 15a of the output element 15, displaceable in a z-coordinate perpendicular to the u-direction and perpendicular to the direction of movement of the first slide 12. The second spring element 16 is installed between a bottom surface of the second slide 12a and a bottom wall 15c of the output element 15.

[0073] The NeSt element to be reinforced is achieved by the compression and relaxation of the second spring element 16 in the output element 15 by the lever(s) 14. The increase in the resulting nonlinear stiffness is achieved by the first slide 12, which is elastically mounted in the input element 11 by the first spring elements 13.

[0074] A variant of the first embodiment of the stiffness unit 10 according to Fig. 4a is in Fig. 4b shown.

[0075] The variant according Fig. 4b, like the first embodiment, has an input element 11, but only one first slide 12 profiled on its underside, two first spring elements 13, an output element 15 and a second spring element 16.

[0076] The input element 11 is also referred to as the input side of the stiffness unit 10, while the output element 15 is also called an output side of the stiffness unit 10.

[0077] In contrast to the first embodiment, this variant does not have levers 14, but a rolling mechanism which is formed from a contour 17 of the profiled underside of the first slide 12 and a rolling element 18 of the output element 15.

[0078] The input element 11 and the output element 15 are connected via the coupling unit KE, which connects the first slide 12, supported by the first spring elements 13, to the second slide 12a, which is in contact with the second spring element 16. In this variant of the first embodiment, the coupling unit KE is formed by the stiffness unit 10 from the rolling mechanism with contour 17 and the rolling element 18.

[0079] The rolling element 18 is a sphere that is in contact with the second spring element 16 in the interior 15b of the output element 15 and is rotatably and displaceably arranged within it in the z-coordinate. The rolling element 18 protrudes upwards from the interior 15b through an upper opening in the interior 15b and contacts the contour 17 of the first slide 12. The spring force of the second spring element 16 presses the rolling element 18 against the contour 17.

[0080] The stiffness of the NeSt element to be reinforced is achieved by the compression and relaxation of the second spring element 16 by the rolling element 18, which rolls on the contour 7 of the profiled first slide 12. The increase in the resulting nonlinear stiffness is achieved by the first slide 12 being elastically mounted with the first spring elements 13 in the interior 11c of the input element 11.

[0081] Fig. 4c represents a second embodiment of the stiffness unit 10.

[0082] The second embodiment according to Fig. 4c, like the first embodiment, has an input element 11, but only a first slide 12, an output element 15 and a beam element 20.

[0083] Here too, the input element 11 is also referred to as the input side of the stiffness unit 10, while the output element 15 is also called an output side of the stiffness unit 10.

[0084] The first slide 12 is as in the first embodiment according to Fig. 4a and the variant according to Fig. 4b in the interior 11c of the entrance element 11 with the two first spring elements 13 arranged slidably.

[0085] The input element 11 and the output element 15 are connected via the coupling unit KE, which connects the first slide 12, supported by the first spring elements 13, to the output element 15, which is designed as a slide. In this second embodiment, the coupling unit KE is formed from the beam element 20 of the stiffness unit 10.

[0086] From the underside of the input element 11, one end of the bending beam 20 is attached to the input element 11. The beam element 20 extends downwards – here with two bulges – its imaginary center line running perpendicular to the direction of travel u. The other end of the beam element 20 is attached to the output element 15. The output element 15 could, for example, also be a type of sled.

[0087] The NeSt element to be reinforced is realized by compressing and buckling the beam element 20. The increase in the resulting nonlinear stiffness is achieved by the first slide 12, which is elastically mounted with the first spring elements 13.

[0088] In Fig. 4d is a variant of the second embodiment according to Fig. 4c shown.

[0089] The variant according Fig.4d includes an input element 11, an output element 15, a slide 19 and a beam element 20.

[0090] The input element 11, for example, is a sled that is guided in a longitudinally displaceable manner in the direction of the path u.

[0091] The input element 11 and the output element 15 are connected via the coupling unit KE, which connects the input element 11, designed as a slide, to the output element 15, also designed as a slide. In this variant of the second embodiment, the coupling unit KE is formed from the stiffness unit 10 by the beam element 20.

[0092] The beam element 20 connects the input element 11 and the output element 15. The carriage 19 is slidably guided on the beam element 20 in the direction of an imaginary longitudinal axis of the beam element 20. The carriage 19 divides the beam element 20 into a part with a bulge 20a and a part designed as a rod 21. The part of the beam element 20 with the bulge 20a is located between the input element 11 and the carriage 19, with the section of the beam element 20 between the carriage 19 and the output element 15 being the rod 21.

[0093] Beam element 20 is shown here as an example of a bending beam designed as a leaf spring.

[0094] The NeSt element to be reinforced is realized by compressing and buckling the beam element 20. The increase in the resulting nonlinear stiffness is achieved by the slide 19, which is elastically mounted to the beam element 20.

[0095] The in the Fig. The spring elements shown in 4a to 4c can also be replaced by alternative spring concepts.

[0096] Fig. 4e represents a third embodiment of the stiffness unit 10.

[0097] The third embodiment comprises an input element 11, an output element 15, a slide 19, a beam element 20 and a rod 21.

[0098] The input element 11 and the output element 15 are connected via the coupling unit KE, which connects the input element 11, designed as a slide, to the output element 15, also designed as a slide. In this variant of the second embodiment, the coupling unit KE is formed from the stiffness unit 10 by the beam element 20.

[0099] The beam element 20 is connected at one end to the input element 11 and at the other end to a slide 19. The slide 19, in turn, is supported on the output element 15 via a rod 21.

[0100] The NeSt element to be reinforced is realized by compressing and buckling the beam element 20. The increase in the resulting nonlinear stiffness is achieved by the slide 19, which is elastically mounted to the rod 21 designed as a bending beam.

[0101] The NeSt element to be reinforced is realized by compressing and buckling the beam element 20. The increase in the resulting nonlinear stiffness is achieved by the slide 19, which is elastically mounted to the rod 21 designed as a bending beam.

[0102] In Fig. 4f is a variant of the third embodiment of the stiffness unit 10 according to Fig. 4e shown.

[0103] This variant is constructed like the third embodiment, except that the beam element 20 is present three times.

[0104] The NeSt element to be reinforced is achieved by compressing and buckling the beam elements 20. The resulting nonlinear stiffness is increased by the slide 19, which is elastically mounted to the rod 21 designed as a bending beam.

[0105] Fig. Figure 4g shows a fourth embodiment of the stiffness unit 10 in radial form with an axis 10a.

[0106] The stiffness unit 10 comprises a circular input element 11, an equally circular output element 15, beam elements 20 and rods 21 as well as a hub 22.

[0107] The circular input element 11, the circular output element 15, and the hub 22 are arranged coaxially with respect to the axis 10a of the stiffness unit 10. The circular input element 11 is connected to the hub 22 via the radially arranged beam elements 20. Similarly, the bars 21 connect the hub 22 and the circular output element 15. The beam elements 20 and the bars 21 are arranged in pairs adjacent to each other in the axial direction.

[0108] The NeSt element to be reinforced is achieved by compressing and buckling the beam elements 20. The resulting nonlinear stiffness is increased by the hub 4, which is elastically supported by the bars 21 designed as bending beams. The symmetrical arrangement of the beam elements 20 and bars 21 also leads to a compensation of the radial forces between opposing elements.

[0109] The in the Fig.The exemplary stiffness units 10 shown in 4a to 4g are, as respective functional units, components of decoupling devices 50, which are described below.

[0110] These decoupling devices 50 each have two opposing NeSt mechanisms or stiffness units 10, 10' for compensating undesired force components. In addition to the translational concepts shown, corresponding rotational designs are also conceivable.

[0111] Fig. Figure 5a shows a schematic perspective view of a first embodiment of a decoupling device 50.

[0112] Fig. 5b shows a sectional view of the decoupling device 50. Fig. 5a in a uz-plane.

[0113] Fig. Figure 5c shows a sectional view of the decoupling device 50. Fig. 5a in a yz plane.

[0114] The decoupling device 50 comprises two stiffness units 10, 10'.

[0115] Each stiffness unit 10, 10' has the following characteristics: a cuboid entrance element 11, two output elements 15 as one respective output slide 23 (corresponds to the output element 15 of the Fig. 4a), a second sled 24 (corresponds to the second sled 12a of the Fig. 4a), a first sled 25 (corresponds to the first sled 12 of the Fig. 4a), first spring elements 27 (correspond to the second spring elements 16 of the Fig. 4a), second spring elements 28, third spring elements 29 (correspond to the first spring elements 13 of the Fig. 4a), two ST adjustment elements, Linear guides 30, and a coupling unit KE, which here consists of at least one lever 26 (corresponding to lever 14 of the Fig. 4a) exists.

[0116] First, the first stiffness unit 10 is described.

[0117] The cuboid entrance element 11 consists of two parallel wide base walls 11a and two parallel narrow side walls 11b. These walls 11a and 11b enclose an interior space 11d in which two NeSt mechanisms or stiffness units 10 opposite each other in the z-direction are arranged.

[0118] Each coupling unit KE of the two stiffness units 10, 10' is constructed with a lever mechanism with levers 26 similar to the first embodiment of the stiffness unit 10 according to Fig. 4a.

[0119] The first carriage 25 is mounted here via third spring elements 29 on a respective inner side of a side wall 11b centrally in the middle of the input element 11 and is guided in the z-direction by a respective linear guide 30 also on a respective inner side of a base wall 11a of the input element 11.

[0120] The output slide 23 forms the output element 15 as the output side and is supported on both sides in the u-direction by a second spring element 28 with a respective inner side wall 11b of the input element 11. The output slide 23 is slidably mounted in the z-direction relative to the two base walls 11a of the input element 11 by a respective linear guide 30.

[0121] An opening 23a of the output slide 23 faces the center of the interior 11d of the input element 11 and forms a receptacle for the second slide 24 and the first spring element 27. The first spring element 27 is arranged between the second slide 24 and a base 23b of the opening 23a and is in contact with the adjusting element ST, here a screw. The adjusting element ST serves to adjust the spring tension of the first spring element 27, which can, for example, also consist of several individual spring elements.

[0122] The second slide 24 is slidably guided in the z-direction within the opening 23a. The adjusting element ST extends from the base 23b of the opening 23a through the output slide 23 to the outside in the z-direction and can be rotated from the outside, e.g., by means of a tool, to adjust the z-position of the second slide 24 and to tension the first spring element 27 in an internal thread of the output slide 23. Of course, other adjusting mechanisms are also possible.

[0123] The levers 26 are articulated in a first lever axis 26a to the first slide 25 and in a second lever axis 26b to the second slide 24.

[0124] The second stiffness unit 10' is constructed in the same way as the first stiffness unit 10 described above and is rotated by 180° around the u-coordinate in the interior 11d of the entrance element 11 and, like the first stiffness unit 10, is mounted on the inner sides of the side walls 11b via second spring elements 28 and third spring elements 29 and is guided slidably on the inner sides of the base walls 11a of the entrance element 11 by means of linear guides 30.

[0125] The levers 26 of the second stiffness unit 10' are articulated in a first lever axis 26a on the second slide 24 opposite the levers 26 of the first stiffness unit 10.

[0126] The NeSt element to be reinforced is achieved by the compression and relaxation of the first spring elements 27 by the levers 26. The increase in the resulting nonlinear stiffness is achieved by the third spring elements 29. The preload of the first spring elements 27 can be varied via the adjusting elements ST (e.g., screws). The parallel stiffness k l,stat The absorption of the static load is achieved by the second spring elements 28. The carriages 23 and 25 are supported by the linear guides 30.

[0127] Fig. Figure 6a shows a schematic perspective view of a second embodiment of a decoupling device 50.

[0128] Fig. 6b shows a sectional view of the decoupling device 50 according to Fig. 6a in a uz-plane.

[0129] Fig. Figure 6c shows a sectional view of the decoupling device 50. Fig.6a in a yz plane.

[0130] The decoupling device 50 of the second embodiment of the decoupling device 50 comprises two stiffness units 10, 10'.

[0131] Each stiffness unit 10, 10' has the following characteristics: a cuboid entrance element 11, two output elements 15 as one respective output slide 23 (corresponds to the output element 15 of the Fig. 4b), a second sled 24 (corresponds to the second sled 12a of the Fig. 4b), a first sled 25 (corresponds to the first sled 12 of the Fig. 4b), first spring elements 27 (correspond to the second spring elements 16 of the Fig. 4a), second spring elements 28, third spring elements 29 (correspond to the first spring elements 13 of the Fig. 4a), two ST adjustment elements, Linear guides 30, and a coupling unit KE, which here consists of a rolling mechanism with a contour 17 and a rolling element 18 (corresponding to the contour 17 and the rolling element 18 of the Fig. 4b) exists.

[0132] First, the first stiffness unit 10 is described.

[0133] The cuboid-shaped input element 11 is like the input element 11 of the first embodiment according to Fig. 5a, Fig. 5b, Fig. 5c is set up and described there.

[0134] The first slide 25 is here like the first slide 25 of the first embodiment according to Fig. 5a, Fig. 5b is attached to the third spring elements 29 and supported via linear guides 30 and described there.

[0135] In contrast to the first embodiment, the first slide 25 shows Fig. 5a, Fig. 5b, Fig. 5c opposite contours 17 of the coupling unit KE.

[0136] The output slide 23 with its opening 23a, the second slide 24, and the first spring element 27 is constructed and mounted as described in the first embodiment. In contrast to the first embodiment, here, instead of levers, the rolling element 18 of the rolling mechanism of the coupling unit KE is rotatably arranged in the second slide 24. The rolling element 18 is in contact with the contour 17.

[0137] The second stiffness unit 10' is constructed in the same way as the first stiffness unit 10 described above and is rotated by 180° around the u-coordinate in the interior 11d of the entrance element 11, mounted on the inside of the side walls 11b via second spring elements 28 and third spring elements 29 and guided slidably on the inside of the base walls 11a of the entrance element 11 by means of linear guides 30.

[0138] The rolling element 18 of the second stiffness unit 10' is in contact with a further contour 17 on the first slide 25 opposite the contour 17, which interacts with the rolling element of the first stiffness unit 10.

[0139] Instead of one rolling element 18, two or more rolling elements 18 can also be used.

[0140] The stiffness element to be reinforced is achieved by the compression and relaxation of the first spring elements 27 by the rolling elements 18 rolling on the respective contour 17 of the first slide 25, which is profiled with the contours 17. The increase in the resulting nonlinear stiffness is achieved by the third spring elements 29. The preload of the first spring elements 27 can be varied via the adjusting elements ST (e.g., screws). The parallel stiffness k l,statThe absorption of the static load is achieved by the second spring elements 28. The carriages 23 and 25 are supported by the linear guides 30.

[0141] Fig. Figure 7a shows a schematic perspective view of a third embodiment of a decoupling device 50.

[0142] Fig. 7b shows a sectional view of the decoupling device 50. Fig. 7a in a uz-plane.

[0143] Fig. Figure 7c shows a sectional view of the decoupling device 50. Fig. 7a in a yz plane.

[0144] The decoupling device 50 of the third embodiment of the decoupling device 50 comprises two stiffness units 10, 10'.

[0145] Each stiffness unit 10, 10' has the following characteristics: a cuboid entrance element 11, two output elements 15 as one respective output slide 23 (corresponds to the output element 15 of the Fig. 4c), a first sled 25 (corresponds to the first sled 12 of the Fig. 4c), second spring elements 28, third spring elements 29 (correspond to the first spring elements 13 of the Fig. 4c), two ST setting elements, Linear guides 30, and a coupling unit KE, which here consists of a beam element 20 (corresponds to the beam element 20 of the Fig. 4c) exists.

[0146] The cuboid-shaped input element 11 is like the input element 11 of the first and second embodiments according to Fig. 5a, Fig. 5b, Fig. 5c or Fig. 6a, Fig. 6b, Fig. 6c is set up and described there.

[0147] The first slide 25 is here like the first slide 25 of the first embodiment according to Fig. 5a, Fig.5b is attached to the first spring elements 25a and supported via linear guides 30 and described there.

[0148] In contrast to the first and second embodiments, the first sled 25 has fastenings on both sides for a respective inner end of the beam element 20.

[0149] The output slide 23 forms the output element 15 as the output side and is supported on both sides in the u-direction by a second spring element 28 with a respective inner side wall 11b of the input element 11. The output slide 23 is slidably mounted in the z-direction relative to the two base walls 11a of the input element 11 by a respective linear guide 30.

[0150] Each of the two stiffness units 10, 10' is constructed with the beam element 20 in a similar manner to the second embodiment of the stiffness unit 10 according to Fig. 4d.

[0151] One end of the beam element 20 is fixed in the opening 23a of the output slide 23 and interacts with the adjusting element 29. The beam element 20 extends into the interior 11d of the input element 11, its imaginary center line running perpendicular to the direction of travel u in the z-direction. The other end of the beam element 20 is fixed in / to the first slide 25.

[0152] The second stiffness unit 10' is constructed in the same way as the first stiffness unit 10 described above and is rotated by 180° around the u-coordinate in the interior 11d of the entrance element 11 via second spring elements 28 on the inner sides of the side walls 11b and guided slidably by means of linear guides 30 on the inner sides of the base walls 11a of the entrance element 11.

[0153] The second end of the beam element 20 of the second stiffness unit 10' is attached opposite the second end of the beam element 20 of the first stiffness unit 10 to the first slide 25.

[0154] The NeSt element to be reinforced is realized by compressing and buckling the beam elements 20. The increase in the resulting nonlinear stiffness is achieved by the third spring elements 29. The preload of the beam elements 20 can be varied via the adjusting elements ST (e.g., screws). The parallel stiffness k l,stat The absorption of the static load is achieved by the second spring elements 28. The carriages 23 and 25 are supported by the linear guides 30.

[0155] The invention is modifiable within the scope of the attached claims. Reference symbol list 1', 1'', 1''' Spring arrangement 2, 2a First spring element 3 Second spring element 4 frames 5 plate 10, 10' stiffness unit 10a axis 11 Entrance element 11a Base wall 11b Side wall 11c Inside 11d Interior 12 First sled 12a Second sled 13 First spring element 14 levers 14a, 14b Lever axle 15 Starting element 15a Side wall 15b Interior 15c Floor wall 16 Second spring element 17 contour 18 rolling elements 19 sleds 20 beam elements 21 Staff 22 hub 23 starting sleds 23a Opening 23b Floor 24 Second sled 25 First sled 26 levers 26b Lever axis 26a, 27 First spring element 28 Second spring element 29 Third spring element 30 linear guides 50 decoupling device 100-105 Stiffness characteristic curve 200-205 Load characteristic k spring stiffness KE coupling unit L Last OP operating point ST setting element u way y, z coordinate QUOTES INCLUDED IN THE DESCRIPTION

[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0000] DE 10 2022 117 077 A1

[0012] DE 10 2022 128 006 A1

[0013]

Claims

[1] Decoupling device (50) of vibrating systems, comprising at least one nonlinear stiffness element with negative stiffness k nl (u) comprising at least one first spring element (27) and at least one linear stiffness element with positive stiffness k connected thereto in parallel l,stat , which has at least one second spring element (28), characterized by , that the at least one nonlinear stiffness element has negative stiffness k nl (u) in series with at least one further stiffness element with a linear stiffness K l , which has at least one third spring element (29), is connected, and that this series connection is connected in parallel with the at least one linear stiffness element with positive stiffness k l,stat is connected, wherein a quasi-zero-stiffness insulator with increase of the amount of negative stiffness k nl,ser,tot (u) is formed. [2] Decoupling device (50) according to claim 1, characterized by , that the decoupling device (50) has at least one stiffness unit (10, 10') comprising an input element (11), at least one output element (15), comprising at least one first spring element (27), at least one second spring element (28) and at least one third spring element (29), a first slide (25) and a second slide (24) and linear guides (30), wherein the second slide (24) is slidably guided in / on the output element (15). [3] Decoupling device (50) according to claim 2, characterized by, that the first slide (25) is connected to the input element (11) via the at least one third spring element (29) and is coupled to the second slide (24) via a coupling unit (KE), wherein the at least one first spring element (27) is arranged between the second slide (24) and the output element (15), and wherein the at least one output element (15) is connected to the input element (11) via the at least one second spring element (28). [4] Decoupling device (50) according to claim 3, characterized by , that the coupling unit (KE) has at least one lever (26) which is articulated to the first slide (25) with a first lever axis (26a) and to the second slide (24) with a second lever axis (26b). [5] Decoupling device (50) according to claim 3, characterized by , that the coupling unit (KE) has a rolling mechanism with a contour (17) and a rolling element (18). [6] Decoupling device (50) according to claim 5, characterized by , that the contour (17) of the rolling mechanism is arranged on the first slide (25) and the rolling element (18) on the second slide (24), or that the contour (17) of the rolling mechanism is arranged on the second slide (25) and the rolling element (18) on the first slide (24). [7] Decoupling device (50) according to claim 6, characterized by , that the rolling element (18) of the rolling mechanism is a rotatably mounted ball. [8] Decoupling device (50) according to claim 3, characterized by , that the coupling unit (KE) has at least one beam element (20, 21). [9] Decoupling device (50) according to any one of claims 2 to 8, characterized by, that the decoupling device (50) has a first stiffness unit (10) and a second stiffness unit (10') of the same construction, wherein the two stiffness units are arranged rotated by 180° in an interior space (11d) of the input element (11). [10] Decoupling device (50) according to claim 9, characterized by , that the two stiffness units (10, 10') have a common first slide (25) which is connected to the input element (11) via the at least one first spring element (29).

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