Torsional vibration isolation coupling element

Abstract

The invention relates to a torsional vibration isolation coupling element (1) having an axis of rotation (1a), comprising an outer ring (2) as the input side of the coupling element (1), an inner ring (3) as the output side of the coupling element (1), and at least one energy storage unit (4) having at least one energy storage element. The torsional vibration isolation coupling element (1) has a non-linear torsional stiffness.

Description

Technical Field

[0001] The invention relates to a torsional vibration isolating coupling element according to the preamble of claim 1 . Background Art

[0002] Such torsional vibration isolating coupling elements are used to reduce undesired torsional vibrations in a large number of different applications, such as, for example, in drive trains of motor vehicles, ships, piston compressors, piston pumps and stationary power plants for generating energy.

[0003] For the last-mentioned applications, so-called genset motors are used which, unlike mobile passenger car or truck drives, have a mostly stable operating point with a constant rotational speed and a nearly constant load torque. For this purpose, the current prior art mainly provides couplings with a linear spring characteristic curve. Here, the constant positive torsion spring stiffness is usually dimensioned according to the drive torque to be transmitted. However, due to this torsional stiffness of the drive train, torsional vibrations (e.g. due to torque fluctuations) can also be transmitted.

[0004] In order to be able to transmit static drive torques without undesired torque fluctuations at a stable operating point, a nonlinear torsional stiffness with a decreasing spring characteristic curve is required. In this case, the torque first increases with increasing torsion angle of the coupling element until a nearly constant torque level is reached at the stable operating point (English: QZS Quasi-Zero-Stiffness Isolator). The negligible torsional stiffness at the operating point achieves optimal isolation of the rest of the drive train from undesired torsional vibrations.

[0005] In order to achieve such a decreasing spring characteristic curve, a linear torsion spring element already present in the drive train (e.g. a rubber coupling with a constant positive torsion stiffness) is usually supplemented with a parallel nonlinear torsion spring element. In this case, the nonlinear torsion spring element has a torsion stiffness that is dependent on the relative torsion or torsion angle of the coupling element. In this case, the nonlinear spring characteristic curve has a negative stiffness in the angular range of the stable operating point, the absolute value of which is equal to the value of the constant positive torsion stiffness of the linear spring element. The parallel connection of the two spring elements thus results in a vanishing torsion stiffness at the operating point.

[0006] In order to achieve such torsional vibration isolation in practice, nonlinear coupling elements with negative torsional spring stiffness at the operating point are required. For example, in order to increase the energy efficiency of actuators that can be used to deform wing structures in aviation, approaches for achieving negative torsional stiffness have been proposed. Apart from the basic concept, there are no known technical approaches for achieving negative torsional stiffness for use in powertrains. Summary of the invention

[0007] The object of the present invention is therefore to realize an improved torsional vibration isolating coupling element which meets two requirements, namely the transmission of static torque and simultaneously wideband isolation of the drive train, and furthermore no longer has the disadvantages of increased structural space requirement and limited frequency or speed range, or said disadvantages are at least significantly reduced.

[0008] This object is achieved by a torsional vibration isolating coupling element having the features of independent claim 1 .

[0009] Against the background of the described QZS, quasi-zero stiffness concept, for torsional vibration isolation, one inventive concept is to realize a nonlinear coupling element with negative torsional stiffness.

[0010] Thus, a torsional vibration isolating coupling element having a rotation axis comprises an outer ring as an input side of the coupling element, an inner ring as an output side of the coupling element and at least one energy storage unit having at least one energy storage element. The torsional vibration isolating coupling element has a nonlinear torsional stiffness.

[0011] The invention proposes a coupling design for realizing a nonlinear torsion spring characteristic curve with negative torsional stiffness. One possible application of the coupling element is the described torsional vibration isolation of a drive train in combination with an existing coupling element with positive torsional stiffness (quasi-zero stiffness concept). In this case, the design particularly meets the requirement of negative torsional stiffness in a limited angular range, in particular in the range of the stable operating point.

[0012] A particular advantage here is that, compared to alternative designs based on the magnetic action principle for achieving, for example, negative torsional stiffness, the proposed coupling element is distinguished by a very simple structure with purely mechanical components. Thus, in addition to low manufacturing costs, this design also benefits from simplified design, assembly and manufacturability.

[0013] The term “energy storage element” does not only refer to springs, such as, for example, compression springs, but also to alternatives such as, for example, compressed air springs with a variable pressure as preload, gas springs, hydraulic springs and the like.

[0014] One embodiment provides that the nonlinear torsional stiffness of the torsional vibration isolating coupling element has a very low or vanishing torsional stiffness, in particular a zero value, by combining a positive torsional stiffness and a negative torsional stiffness at an operating point. In this way, an optimal isolation of the rest of the drive train from undesired torsional vibrations is advantageously achieved with a negligible torsional stiffness at the operating point.

[0015] In one embodiment, the negative torsional stiffness is formed by compressing the at least one energy storage element of the at least one energy storage unit, the at least one energy storage element being a radially arranged translating compression spring which is in contact with a circumferentially extending shaped portion of the outer ring.

[0016] Of course, the compression spring may also be a compressed air spring, a gas spring, a hydraulic spring or the like with a variable pressure as preload.

[0017] It is advantageous here that the nonlinearity of the torsional stiffness, ie the variation of the torsional stiffness with the torsional angle of the coupling, is achieved primarily by compressing the at least one radially arranged translatory compression spring in accordance with the shaped portion extending in the circumferential direction.

[0018] Due to the almost unlimited number of possible profile geometries within the predetermined torsion angle range of the coupling element, the principle ensures the greatest possible flexibility in the design of the nonlinear spring characteristic curve. If the profile geometry is determined, a change in the spring preload allows the spring characteristic curve to be adjusted subsequently.

[0019] Another embodiment provides that the outer ring of the coupling element and the inner ring of the coupling element are coupled via the at least one energy storage unit, the outer ring of the coupling element and the inner ring of the coupling element being arranged coaxially relative to each other and to the axis of rotation. This enables an advantageously compact design.

[0020] In another alternative embodiment, the negative torsional stiffness is formed by compressing the at least one energy storage element of the at least one energy storage unit, the at least one energy storage element being an axially arranged, translating compression spring which contacts a shaped portion of the outer ring extending in the longitudinal direction of the rotational axis. This is advantageous because the preload of the compression spring does not change due to rotational speed-dependent centrifugal forces.

[0021] Here, it is provided that the outer ring of the coupling element and the inner ring of the coupling element are coupled via the at least one energy storage unit, and the outer ring of the coupling element and the inner ring of the coupling element are arranged axially one after the other in the direction of the rotation axis. In this case, the preload force of the compression spring also advantageously does not change due to the centrifugal force related to the rotation speed.

[0022] The axially arranged, translatory compression spring can also be designed as a compressed air spring, a gas spring, a hydraulic spring or the like with a variable pressure as preload.

[0023] Furthermore, in a further embodiment with radially arranged compression springs, it is advantageous if an intermediate space is formed between the inner circumference of the outer ring and the outer circumference of the inner ring, since this further improves the compact design.

[0024] For this purpose, in one embodiment, the outer ring has a shaped portion with a shaped portion contour on the inner circumference, which shaped portion protrudes from the inner circumference of the outer ring into the intermediate space. This is advantageous because it allows a further improvement of the compact structure.

[0025] Furthermore, it is advantageous if the profile of the profile of the profile of the outer ring is designed as a harmonic profile, for example with a cosine-shaped profile. Of course, other profiles, such as, for example, a trapezoidal profile, etc., can also be used.

[0026] Such a design of the profile advantageously allows any desired spring characteristic curves to be realized. Furthermore, by means of a symmetrical or asymmetrical profile, the same or different spring characteristic curves can be realized for both rotation directions of the coupling element. Due to the flexible profile, the negative torsional stiffness is not limited to a specific angular range, but can also be designed for a plurality of successive angular ranges. This makes it possible to achieve an optimal torsional vibration isolation for a plurality of different operating points.

[0027] In order to achieve a favorable coupling between the inner circumference of the outer ring and its molded part, it is set that, depending on the relative angle between the outer ring and the inner ring around the rotation axis, the at least one energy storage unit contacts the inner circumference of the outer ring or contacts the molded part using the molded part contour of the molded part.

[0028] In another embodiment, the at least one energy storage unit comprises at least one compression spring, a preload element with a central axis and a contact element, the at least one energy storage unit being arranged with the at least one compression spring and with a part of the preload element in the receiving space in the inner ring in the direction of the central axis and thus in the radial direction relative to the rotational axis. This design is advantageously very simple and compact.

[0029] The compression spring can also be a compressed air spring, a gas spring or the like with a variable pressure as preload.

[0030] In another embodiment, the at least one compression spring is connected or in contact with the preload element with a first spring end, the second spring end of the at least one compression spring is configured as a contact element or is connected to the contact element, and the at least one compression spring presses the contact element against the inner circumference of the outer ring or the shaped portion. For this purpose, advantageously only a small number of components are required, and these components can also be designed to be simple to install.

[0031] In an alternative embodiment, it is also possible, in the case of a radially arranged translatory spring, to arrange the shaped portion both on the inner side of the outer ring and on the outer side of the inner ring. In the latter case, the energy storage unit is located in the outer ring.

[0032] In an alternative embodiment with one or more axially arranged translatory springs, the shaped part is arranged on the left or on the right side of the energy storage cell in the axial direction.

[0033] In another embodiment, the preload force of the at least one compression spring can be adjusted by adjusting the preload element. The variable spring preload force also allows for advantageous subsequent adaptation to different applications and operating states.

[0034] Advantageously, the contact element is a rolling body, in particular a sphere, because in this way only low rolling friction is generated by the rolling body and wear is reduced. In addition, an angular compensation of the axis of rotation is achieved. The rolling body can also be, for example, a cylindrical roller.

[0035] In another embodiment, the torsional vibration isolating coupling element further comprises at least two energy storage units. It is advantageous if the at least two energy storage units are arranged symmetrically in the coupling element. An advantage here is that the radial pressures of the opposing compression springs cancel each other out. As a result, no radial resultant force occurs between the inner ring and the outer ring.

[0036] In a further embodiment, the coupling element is a coupling element of a drive train of a stationary application, in particular a drive train of a stationary internal combustion engine.

[0037] The vibration requirements on the individual components are reduced by isolating the torsional vibrations and the resulting reduced torsional loads on the drive train. In addition, additional components that are usually required to reduce torsional vibrations can be omitted. This reduces the costs and the required installation space for these additional components. In contrast to similar torsion spring designs, whose stiffness characteristics can usually only be varied within a limited parameter range, the invention described below allows the realization of a wide range of different spring characteristic curves by taking into account freely configurable profiles and allows these spring characteristic curves to be subsequently modified by means of variable spring preload.

[0038] Further advantageous embodiments of the invention can be gathered from the dependent claims. BRIEF DESCRIPTION OF THE DRAWINGS

[0039] Several embodiments of the present invention are described below with reference to the accompanying drawings. The present invention is not limited to these embodiments. In particular, the individual features of the following embodiments can be used not only in these embodiments, but also in other embodiments. Among them:

[0040] Figures 1 to 5 A schematic diagram showing an embodiment of a torsional vibration isolation coupling element according to the present invention in different positions;

[0041] Figure 6 A schematic perspective view showing another embodiment;

[0042] Figure 7 Show according to Figure 6 A schematic cross-sectional view of another embodiment of the present invention;

[0043] Figure 8 Show Figure 7 A schematic enlarged view of region VIII in FIG. 1 ; and

[0044] Figures 9 to 10 Shows a graphical representation of the spring characteristic curve. DETAILED DESCRIPTION

[0045] In the following, expressions such as “outer” or “inner” etc. relate to the corresponding drawing plane, and “axial” and “radial” relate to the rotation axis 1 a of the torsional vibration isolating coupling element 1 .

[0046] Figure 1 A schematic radial section through an embodiment of a torsional vibration isolating coupling element 1 according to the invention is shown in an initial position.

[0047] The torsional vibration isolating coupling element 1 has an axis of rotation 1 a and comprises an outer ring 2 as input side, an inner ring 3 , for example in the form of a hub, as output side, and an energy storage unit 4 .

[0048] Outer ring 2 and inner ring 3 are arranged concentrically with respect to rotation axis 1 a of coupling element 1 and can be rotated relative to one another about rotation axis 1 a by a relative angle φ.

[0049] The inner ring 3 is arranged in the aperture of the outer ring 2 .

[0050] An intermediate space ZR is formed between the inner peripheral surface 2 a of the outer ring 2 and the outer peripheral surface 3 a of the inner ring 3 .

[0051] The outer ring 1 has a shaped portion 7 on its inner circumferential surface 2a. The shaped portion 7 protrudes from the inner circumferential surface 2a into the intermediate space ZR. The shaped portion 7 has a shaped portion contour 7a.

[0052] The energy storage unit 4 comprises an energy storage element designed as a compression spring 6, a preload element 9 with a center axis 9a, and a contact element 10. The energy storage unit 4 is arranged or supported translationally in the receiving space 5 with the compression spring 6 and with a part of the preload element 9 in the inner ring 3 in the direction of the center axis 9a and thus in the radial direction relative to the rotation axis 1a.

[0053] The term “energy storage element” is understood not only to refer to springs, such as compression springs, for example, but also to alternatives such as compressed air springs with variable pressure as preload, gas springs, hydraulic springs and the like.

[0054] The compression spring 6 is connected to the preload element 9 , for example by means of a screw, fastened thereto or in contact with the preload element 9 with a first spring end 6 a in the region of the bottom of the receiving space 5 pointing toward the rotation axis 1 a .

[0055] The second spring end 6b of the compression spring 6 is designed as a contact element 10 or is connected to the contact element 10. The compression spring 6 presses the contact element 10 against the inner circumferential surface 2a of the outer ring.

[0056] Here, the contact element 10 is shown in a triangular cross section and extends parallel to the rotation axis 1a in the axial direction of the rotation axis 1a over a length section determined by the inner circumference 2a of the outer ring 2. Of course, the contact element 10 may also have a point-shaped contact section.

[0057] In this way, the compression spring 6 is in contact with the inner circumference 2a of the outer ring 1 at the contact point 8 or contact section with its second spring end 6b as contact element 10 or through the contact element 10 itself. The preload force of the compression spring 6 can be increased or reduced by tightening or loosening the preload element 9 (screw).

[0058] The coupling element 1 is Figure 1 In the initial position shown in (relative angle φ=0), a contact normal force Fc occurs in the radial direction at the contact point 8 .

[0059] The contact normal force Fc corresponds to the preload force of the compression spring 6 via the preload element 9 (screw).

[0060] Figure 2 Shows the position of the twisted position from the initial position according to Figure 1 A schematic radial cross-sectional view of a first embodiment of the present invention.

[0061] The relative angle φ is now increased compared to its value 0 in the initial position, ie the outer ring 2 has been rotated, for example, in the clockwise direction relative to the inner ring 3 .

[0062] If the relative angle φ is Figure 2If the contact point 8 is raised as shown in , it follows the profile 7 a of the profile 7 of the outer ring 1 .

[0063] Due to the radial displacement of the contact point 8 in the direction of the rotation axis 1 a , the compression spring 6 is now compressed, so that the force of the compression spring 6 increases.

[0064] Furthermore, the decomposition of the contact normal force Fc on the side of the profile contour 7a of the profile 7 results in a radial force component Fcr and a circumferential force Fcu. The circumferential force Fcu causes a torque T to occur, which reacts against the relative twisting (positive torque) occurring at the relative angle φ. The reverse acting torque T (at Figure 2 This increase in the relative angle φ (in the counterclockwise direction) with increasing relative angle φ corresponds to positive torsional stiffness. The decomposition of the contact normal force Fc or the resulting torsional stiffness as a function of the relative angle φ is influenced by the geometry of the profile contour 7a of the profile 7. The values ​​of the contact normal force Fc or its force components Fcr and Fcu are additionally dependent on the preload force of the preload element 9.

[0065] If the relative angle φ is further increased, the contact point 8 reaches the vertex of the shaped portion 7, as in Figure 3 As shown in .

[0066] In this case, the compression spring 6 is compressed to the maximum in the direction of the rotation axis 1a, so that the generated pressure reaches its maximum value. The compression of the compression spring 6 corresponds to the radial dimension or height of the profile 7a of the profile 7, that is, the distance from the top of the profile 7 to the inner circumference 2a of the outer ring 2.

[0067] Due to the radially acting contact normal force Fc, no force component circumferential force Fcu occurs and thus no torque occurs (T=0). The reduction in torque T corresponds to negative torsional stiffness when the relative angle φ increases.

[0068] If the relative angle φ is as Figure 4 If the pressure is increased further as shown in , the contact point 8 moves further following the shaped part 7 and the compression spring 6 relaxes again.

[0069] Due to the force decomposition on the side of the shaped part 7, the force component of the contact force, the circumferential force Fcu, appears again, but with Figure 2 The circumferential force Fcu in the opposite direction is opposite. This opposite circumferential force Fcu causes a torque T, but this time the torque is in the direction of the relative angle φ, that is, in Figure 4 The torque acts in the clockwise direction (negative torque).

[0070] The dependence of the negative torsional stiffness on the relative angle φ is influenced by the geometry of the profile contour 7 a of the profile 7 or the force separation. In addition, the absolute value of the negative torsional stiffness is dependent on the potential energy stored in the compression spring 6 or on the spring preload caused by the preload element 6 .

[0071] Finally, if Figure 5 As shown in FIG. 8 , the contact point 8 reaches an unformed section of the inner circumferential surface 2 a of the outer ring 2 .

[0072] Only those that have appeared here Figure 1 The radial contact normal force Fc is shown in the initial position in , and thus no torque T occurs.

[0073] In other words, the energy storage unit 4 contacts the inner circumference 2a of the outer ring 2 or the profile 7a of the profile in relation to the relative angle φ between the outer ring 2 and the inner ring 3 about the rotation axis 1a.

[0074] Figure 6 A schematic perspective view of another embodiment of a torsional vibration isolating coupling element 1 is shown. Figure 7 Show according to Figure 6 Here a radial section in the region of the energy storage unit 4 is shown. Figure 8 Shown in Figure 7 Schematic enlargement of region VIII in FIG.

[0075] Figure 9-10 Shows a graphical representation of the spring characteristic curve.

[0076] The further embodiment of the coupling element 1 has four energy storage units 4, each of which has a compression spring 6 and a preload element 9. The four energy storage units are arranged at 90° intervals around the rotation axis 1a. Of course, more or less than four energy storage units 4 (for example two energy storage units 4) can also be provided.

[0077] The contact between the profile 7a of the profile 7 and the compression spring 6 is achieved here by a rolling body as a contact element 10. The spring ends 6a and 6b are configured as plate-like components here. In this way, when the rolling body as the contact element 10 rolls on the profile 7a of the profile 7, the rolling body will not be hindered on the plate-like component of the spring end 6b.

[0078] The rolling bodies may be, for example, spheres, cylinders or the like.

[0079] The spring length of the compression spring 6 is denoted here by the letter “1”.

[0080] For example, Fig. 9 and10 middle( Fig. 9 is characteristic curve 11 and Fig.10 Characteristic curve 12 ) shows the resulting torsion spring characteristic curve of the torsionally-vibration-isolating coupling element 1 for a harmonic profile (cosine-shaped profile) on the outer ring 2 and different preload forces or screw-in depths of the preload element 9 .

[0081] exist Fig. 9 and 10 In FIG. 1 , the torque T is plotted at the relative angle φ.

[0082] Here, the preload is achieved by the length difference Δl of the spring length l of the compression spring 6: Fig. 9 In: Δl=0mm, Fig.10 In the figure: ΔI=-1 mm. Negative numbers indicate compression of the pressure spring 6.

[0083] It can be seen that the value of the negative torsional stiffness can be increased by increasing the preload (or the available potential energy of the compression spring 6). In addition, the initial position (see Figure 1 ) The symmetrical shaped portion contour 7 a ensures that the coupling element 1 has the same torsion spring characteristic curve for both directions of rotation about the rotation axis 1 a.

[0084] The symmetrical arrangement of the four energy storage units 4 with the compression springs 6 in the circumferential direction together with the corresponding shaped portions 7a on the inner circumference 2a of the outer ring 2 cancels out the radial pressures of the opposing compression springs 6. As a result, no radial resultant force occurs between the inner ring 3 and the outer ring 2.

[0085] Compared to alternative designs for achieving negative torsional stiffness, for example based on the principle of magnetic action, the torsional vibration isolating coupling element 1 described above is distinguished by a very simple construction with purely mechanical components.

[0086] Thus, in addition to low manufacturing costs, this design also benefits from simplified design, assembly and manufacturability. In addition, the variable spring preload of the compression spring 6 can also be adapted subsequently to different application conditions and operating states.

[0087] Such a configuration of the shaped part contour 7 a of the shaped part 7 on the inner circumferential surface 2 a of the outer ring 2 makes it possible to realize any desired spring characteristic curve.

[0088] Furthermore, by means of a symmetrical or asymmetrical profile 7a, identical or different spring characteristics can be achieved for both rotation directions of the coupling element 1. Due to the flexible profile 7a, the negative torsional stiffness is not limited to a specific angle range, but can also be designed for a plurality of consecutive angle ranges. This makes it possible to achieve an optimal torsional vibration isolation for a plurality of different operating points.

[0089] The invention can be modified within the scope of the attached claims.

[0090] In an embodiment which is not shown but can be easily imagined, the energy storage unit is arranged axially in the direction of the rotation axis 1a. Here, the at least one energy storage element is designed as a translational compression spring 6 arranged axially on the inner ring 3, which is in contact with a shaped portion 7 of the outer ring 2 extending in the longitudinal direction of the rotation axis 1a. Of course, the axially arranged translational compression spring 6 can also be located on the outer ring 2 and in contact with the shaped portion 7 arranged on the inner ring 3.

[0091] Here, the shaped portion 7 is located respectively on the left or right side of the compression spring 6 .

[0092] The advantage of an axially arranged compression spring 6 is that the preload force of the compression spring 6 does not change due to rotational speed-dependent centrifugal forces.

[0093] Here, outer ring 2 of coupling element 1 and inner ring 3 of coupling element 1 are coupled via at least one energy storage unit 4 , wherein outer ring 2 of coupling element 1 and inner ring 3 of coupling element 1 are arranged axially one after the other in the direction of rotation axis 1 a .

[0094] Of course, other shaped portions 7 can also be used. Such shaped portions 7 can be trapezoidal, for example.

[0095] Reference numerals list

[0096] 1 Coupling element

[0097] 1a Rotation axis

[0098] 2 Outer Ring

[0099] 2a Inner Surface

[0100] 3 Inner Ring

[0101] 3a Outer surface

[0102] 4 Energy storage unit

[0103] 5Accommodation space

[0104] 6. Pressure spring

[0105] 6a, 6b Spring ends

[0106] 7 Forming Department

[0107] 7a Molding section profile

[0108] 8 contact points

[0109] 9Preload element

[0110] 9a Central Axis

[0111] 10 contact elements

[0112] 11.12 Characteristic curve

[0113] Fc contact normal force

[0114] Fcr; Fcu force components

[0115] Spring length

[0116] T Torque

[0117] ZR Intermediate Space

[0118] φRelative angle.

Claims

1. A torsional vibration isolating coupling element (1) with a rotation axis (1a), the coupling element having an outer ring (2) as an input side of the coupling element (1), an inner ring (3) as an output side of the coupling element (1) and at least one energy storage unit (4) having at least one energy storage element, characterized in that The torsional vibration isolation coupling element (1) has nonlinear torsional stiffness.

2. The torsional vibration isolation coupling element (1) according to claim 1, characterized in that: The nonlinear torsional stiffness of the torsional vibration isolating coupling element (1) has a very low or vanishing torsional stiffness, in particular a zero value, at an operating point due to a combination of positive and negative torsional stiffness.

3. The torsional vibration isolation coupling element (1) according to claim 2, characterized in that: The negative torsional stiffness is formed by compressing the at least one energy storage element of the at least one energy storage unit (4), the at least one energy storage element being a radially arranged translating compression spring (6) which is in contact with a shaped portion (7) of the outer ring (2) extending in the circumferential direction.

4. The torsional vibration isolation coupling element (1) according to claim 3, characterized in that: The outer ring (2) of the torsional vibration isolation coupling element (1) and the inner ring (3) of the torsional vibration isolation coupling element (1) are coupled via the at least one energy storage unit (4); the outer ring (2) of the torsional vibration isolation coupling element (1) and the inner ring (3) of the torsional vibration isolation coupling element (1) are coaxially arranged relative to each other and relative to the rotation axis (1a).

5. The torsional vibration isolation coupling element (1) according to claim 2, characterized in that: The negative torsional stiffness is formed by compressing the at least one energy storage element of the at least one energy storage unit (4), the at least one energy storage element being an axially arranged translational pressure spring (6) which is in contact with a shaped portion (7) of the outer ring (2) extending in the longitudinal direction of the rotation axis (1a).

6. The torsional vibration isolation coupling element (1) according to claim 5, characterized in that: The outer ring (2) of the torsional vibration isolation coupling element (1) and the inner ring (3) of the torsional vibration isolation coupling element (1) are coupled via the at least one energy storage unit (4), and the outer ring (2) of the torsional vibration isolation coupling element (1) and the inner ring (3) of the torsional vibration isolation coupling element (1) are arranged axially in sequence in the direction of the rotation axis (1a).

7. The torsional vibration isolation coupling element (1) according to claim 4, characterized in that: An intermediate space (ZR) is formed between the inner circumferential surface (2a) of the outer ring (2) and the outer circumferential surface (3a) of the inner ring (3).

8. The torsional vibration isolation coupling element (1) according to claim 7, characterized in that: The outer ring (1) has a shaped portion (7) with a shaped portion contour (7a) on an inner circumferential surface (2a), wherein the shaped portion (7) protrudes from the inner circumferential surface (2a) of the outer ring (2) into the intermediate space (ZR).

9. The torsional vibration isolation coupling element (1) according to claim 8, characterized in that: The profile (7a) of the profile (7) of the outer ring (2) is designed as a harmonic profile (7a), for example with a cosine-shaped profile.

10. The torsional vibration isolation coupling element (1) according to claim 8 or 9, characterized in that: The at least one energy storage unit (4) is in contact with the inner circumference (2a) of the outer ring (2) or with the profile (7a) thereof, depending on the relative angle (φ) between the outer ring (2) and the inner ring (3) about the rotation axis (1a).

11. The torsional vibration isolation coupling element (1) according to any one of claims 7 to 10, characterized in that The at least one energy storage unit (4) comprises at least one compression spring (6), a preload element (9) having a central axis (9a) and a contact element (10), the at least one energy storage unit (4) being arranged in the receiving space (5) with the at least one compression spring (6) and with a part of the preload element (9) in the inner ring (3) in the direction of the central axis (9a) and thus in the radial direction relative to the rotation axis (1a).

12. The torsional vibration isolation coupling element (1) according to claim 11, characterized in that: The at least one compression spring (6) is connected to or in contact with the preload element (9) with a first spring end (6a), a second spring end (6b) of the at least one compression spring (6) is configured as a contact element (10) or is connected to the contact element (10), and the at least one compression spring (6) presses the contact element (10) against the inner circumference (2a) of the outer ring (2) or against the shaped portion (7).

13. The torsional vibration isolation coupling element (1) according to claim 12, characterized in that: The preload force of the at least one compression spring (6) can be adjusted by adjusting the preload element (9).

14. The torsional vibration isolation coupling element (1) according to any one of claims 11 to 13, characterized in that The contact element (10) is a rolling body, in particular a ball.

15. The torsional vibration isolating coupling element (1) according to claim 1, further comprising at least two energy storage units (4), characterized in that: The at least two energy storage units (4) are symmetrically arranged in the torsional vibration isolating coupling element (1).

16. A torsional vibration isolating coupling element (1) according to any one of the preceding claims, characterized in that The torsional vibration isolating coupling element (1) is a coupling element (1) of a drive train of a stationary application, in particular a coupling element of a drive train of a stationary internal combustion engine, a piston compressor or a piston pump.

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