Torsional vibration isolation coupling

Abstract

A torsional vibration isolation coupling (1) is provided, comprising a rotation axis (1a) as a torsional vibration isolation coupling (1), and including a first coupling part (2) as an input side of the coupling (1), a second coupling part (3) as an output side of the coupling (1), and a damping unit (4), wherein the damping unit (4) comprises at least one spring assembly (10, 10') designed as a non-linear spring assembly (10, 10') having a damping spring characteristic curve (13).

Description

Technology Field

[0001] The present invention relates to a torsional vibration isolation coupling according to the preamble of claim 1. Background Technology

[0002] Torsional vibration isolation couplings are used, for example, in stationary internal combustion engines.

[0003] These stationary internal combustion engines are also known as so-called genset engines, used to produce electrical energy in conjunction with generators. They are used for a wide range of purposes, from emergency power supply to supplying electrical energy for ship propulsion systems. These engines are typically run on diesel or natural gas. Another application is in piston compressors.

[0004] Unlike mobile passenger car or truck drive systems that are affected by variable speed and frequently changing loads during ferry operation, these applications are characterized by a mainly fixed operating point with a constant speed and nearly constant load torque.

[0005] Current prior art provides torsional vibration isolation couplings primarily having linear spring characteristic curves for this purpose. The torsional spring stiffness of the torsional vibration isolation is typically dimensioned using the driving torque to be transmitted in this case.

[0006] In this case, two requirements for the torsional vibration isolation coupling are presented.

[0007] The first requirement is the transmission of static driving torque. The primary challenge of such stationary application examples is to provide nearly constant torque at a fixed speed. This torque acts as a static load on the drive train and must be transmitted by a coupling. Therefore, to be able to transmit static torque, the torsional stiffness of the coupling must be correspondingly high.

[0008] On the other hand, isolation of torque fluctuations, that is, wide-range vibration isolation, is required.

[0009] In relation to drivetrain dynamics during engine operation, the coupling must isolate the parts connected to each other through the drivetrain (e.g., engine and generator or ship propeller) from interference effects (e.g., variations in drive- or load torque). To maximize the vibration isolation range of the coupling, a correspondingly low torsional stiffness of the coupling is required.

[0010] These two requirements result in conflicting objectives regarding the optimal torsional stiffness of the coupling. On the one hand, this torsional stiffness must be high enough to transmit static torque, but at the same time, it must be as low as possible to isolate interfering drive vibrations.

[0011] Since the primary challenge of a drive train is to transmit static torque, coupling stiffness is generally selected to be high accordingly. Consequently, a disadvantage of such drive trains is that additional components are required to dampen unwanted torsional vibrations (e.g., torsional vibration dampers), or the components must be designed to handle increased torsional vibrations. This results in additional costs on one hand, and generally increases assembly space requirements due to the mutual axial length of the entire train. Furthermore, the damping effect of these additional components is typically tuned to a limited frequency- or speed range. The problem to be solved

[0012] Therefore, the objective of the present invention is to provide a torsional vibration isolation coupling that satisfies two requirements: the transmission of static torque and the isolation of a wide range of drive trains, while also not having the disadvantages of increased assembly space requirements and a limited frequency or speed range, or at least significantly reducing them. means of solving the problem

[0013] The above problem is solved by a torsional vibration isolation coupling having the features of claim 1.

[0014] Accordingly, the torsional vibration isolation coupling comprises a rotating shaft and includes a first coupling member as the input side of the coupling, a second coupling member as the output side of the coupling, and a damping unit. The damping unit comprises at least one spring assembly designed as a non-linear spring assembly having damping spring characteristics.

[0015] A torsional vibration isolation coupling comprising a damping unit having a non-linear spring assembly having a damping spring characteristic curve has the special advantage that static torque transmission is possible until the operating point is reached in a drive train of a fixed-actuation application example.

[0016] Unlike the zero stiffness concept, which achieves vibration isolation only through negligibly low stiffness and makes static load transfer impossible, the torsional vibration isolation coupling according to the present invention provides the possibility of static torque transfer along with vibration isolation at the point of operation. This concept utilizes the nonlinearity of the damping spring characteristic curve of the spring assembly of the damping unit for this purpose.

[0017] In the embodiment, at least one non-linear spring assembly has a positive spring stiffness (k PSE At least one spring member having ) and negative spring stiffness (k NSE It comprises at least one spring member having ). This preferably enables a simple and compact structure.

[0018] In another embodiment, a first coupling part as the input side of the coupling and a second coupling part as the output side of the coupling are provided to be coupled to at least one non-linear spring assembly through a damping unit.

[0019] Unlike couplings having linear spring characteristics, the torsional vibration isolation coupling according to the present invention preferably enables wide-range vibration isolation during stationary operation of the application example, while simultaneously transmitting static driving torque. Thus, the proposed concept provides the advantages of improved drive train dynamics without the need for additional damping components.

[0020] In another embodiment, at least one nonlinear spring assembly is provided to form a plate-shaped interface between at least one spring assembly acting together with a plate for bidirectional force transmission and motion transmission and a first coupling portion of the coupling. This preferably enables a simple design.

[0021] In another embodiment, the plate is coupled to a second coupling portion of the coupling through a connecting rod. The connecting rod is preferably of a simple design.

[0022] When the plate is guided to be displaceable in the translational direction (u) within the receiving space of the first coupling part of the coupling, and the translational direction (u) extends in the tangential direction of the first coupling part of the coupling, a preferably compact structure is possible.

[0023] Negative spring stiffness (k NSE At least one spring member of at least one spring assembly having ) comprises two spring members arranged in pairs in a manner inclined with respect to the translational direction (u), the first ends of the two spring members are connected to a first coupling portion of the coupling spaced apart from each other, and the other ends of the two spring members are preferably connected to a plate or an intermediate plate acting together with the plate in a combined state at a common connection point. In this way, a structure having negative stiffness can be achieved with simple spring members.

[0024] The space between the first ends of the spring members is provided to extend in a direction perpendicular to the translational direction (u). In this case, the advantage is that the structure is simple.

[0025] When the intermediate plate is placed on the end face of the plate without being connected to the plate, this allows the torsional vibration isolation coupling to preferably enable torsional vibration isolation for both positive static torque (T) and negative static torque (T).

[0026] For a compact and simple structure, it is preferable for the first coupling part of the coupling and the second coupling part of the coupling to be arranged coaxially with each other.

[0027] In the embodiments, the torsional vibration isolation coupling is a coupling of a drive train of a stationary application example, particularly a drive train of a stationary internal combustion engine. This preferably enables vibration isolation of a wide range of the drive train.

[0028] The present invention presents a concept having a damping spring characteristic curve for a drive train of a stationary operating application. In this case, unlike the prior art, this concept satisfies both the requirements for static torque transmission and a wide range of vibration isolation without additional functional units. When a conventional coupling is used with a negative stiffness member, a non-linear spring characteristic curve is obtained. Negligibly low spring stiffness at the stationary operating point of the engine enables almost perfect vibration isolation of the connected parts.

[0029] Other preferred embodiments of the present invention are presented in dependent claims.

[0030] Some 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 are applicable not only to these embodiments but also to other embodiments. Brief explanation of the drawing

[0031] FIGS. 1 and 2 are schematic diagrams of a first embodiment of a torsional vibration isolation coupling according to the present invention in a load-free state. FIGS. 3 and 4 are schematic diagrams of the first embodiment according to FIGS. 1 and 2 under load conditions. FIGS. 5 and 6 are schematic diagrams of a second embodiment of a torsional vibration isolation coupling according to the present invention in a load-free state. FIGS. 7 and 8 are schematic diagrams of a second embodiment according to FIGS. 5 and 6 under load conditions. FIGS. 9 and FIGS. 10 are drawings symbolically illustrating a spring assembly. Figure 11 is a diagram of the spring characteristic curve of a spring assembly. Specific details for implementing the invention

[0032] In the following, terms such as "external" or "internal" relate to the corresponding drawing plane, and "axial" and "radial" relate to the axis of rotation (1a) of the torsional vibration isolation coupling (1).

[0033] FIG. 1 shows a schematic radial cross-sectional view of an embodiment of a torsional vibration isolation coupling (1) according to the present invention.

[0034] FIG. 2 shows a schematic cross-sectional view of the torsional vibration isolation coupling (1) according to the present invention according to FIG. 1 in a load-free state.

[0035] The torsional vibration isolation coupling (1) includes a first coupling part (2) as an input side in the form of a disc having a central groove (2a), a second coupling part (3) as an output side in the form of a hub or circular cylinder, and a damping unit (4).

[0036] The first coupling part (2) and the second coupling part (3) are arranged concentrically with respect to the rotation axis (1a) of the coupling (1). The second coupling part (3) is placed within the groove (2a) of the first coupling part (2).

[0037] In the annular region (2b) of the first coupling part (2), a damping unit (4) is placed within the receiving space (5).

[0038] Here, the receiving space (5) is formed in a cube shape in the annular region of the first coupling part (2) and has inner side walls (5a and 5b) facing each other in a tangential direction with respect to the rotation axis (1a). Radially with respect to the rotation axis (1a), the receiving space (5) is defined by an inner base wall (5c) and an inner ceiling wall (5d).

[0039] In this first embodiment, the damping unit (4) includes a plate (6) and a spring assembly (10).

[0040] The plate (6) is guided to be displaceable in the translational direction (u) within the receiving space (5) through the base wall (5c) and the ceiling wall (5d).

[0041] Between the plate (6) and one inner side wall (5a) [here positioned to the left of the plate (6)], the spring assembly (10) connects the plate (6) to the inner side wall (5a) of the receiving space (5) of the first coupling part (2).

[0042] The spring assembly (10) has a positive spring stiffness (k PSE A spring member (8) having ) and negative spring stiffness (k NSE It is designed as a non-linear spring assembly (10) comprising a spring member (9) having a positive spring stiffness (k). PSE A spring member (8) having ) and negative spring stiffness (k NSE The spring members (9) having ) are arranged in parallel connections.

[0043] Positive spring stiffness (k PSE A spring member (8) having ) is connected to the inner side wall (5a) of the receiving space (5) of the first coupling part (2) by the first spring end and is coupled to the first coupling part (2) accordingly.

[0044] Positive spring stiffness (kPSE The other spring end of the spring member (8) having ) is connected to the plate (6).

[0045] Negative spring stiffness (k NSE The spring member (9) having ) is implemented with two spring members (9a and 9b) arranged in pairs in a manner inclined with respect to the translational direction (u). The first ends of the spring members (9a, 9b) are connected to the inner side wall (5a) of the receiving space (5) of the first coupling member (2) with space between them. This space extends in a direction perpendicular to the translational direction (u). The other spring ends of the two spring members (9a, 9b) are connected to the plate (6) in a joined state at a common connection point.

[0046] The connecting rod (7) couples the plate (6) and the second coupling part (3). In this way, the first coupling part (2) as the input side of the coupling (1) and the second coupling part (3) as the output side of the coupling (1) are coupled to the spring assembly (10) through the damping unit (4), in this case by the connecting rod (7).

[0047] In this way, the plate (6) forms an interface for bidirectional force transmission between the first coupling part (2), the spring assembly (10), and the second coupling part (3), in this case through the connecting rod (7). Additionally, the plate (6) forms a motion bias of the connecting rod (7) that transmits the rotational motion of the second coupling part (3) to the plate (6).

[0048] FIG. 2 shows a torque (T) having a value of 0 and a twist angle (φ) between the first coupling part (2) and the second coupling part (3) around the axis of rotation. tAlso illustrates a coupling (1) in an unloaded state having a value of 0. In the unloaded state, all spring members (8, 9a, 9b) of the spring assembly (10) are fully relaxed. At this time, the plate (6) is located in the center of the receiving space (5), and from the center, the plate has the same distance in the translational direction (u) with respect to both inner side walls (5a, 5b) of the receiving space (5).

[0049] FIG. 3 shows a coupling (1) as in FIG. 1 in a schematic radial cross-sectional view. FIG. 4 schematically shows a cross-section of the torsional vibration isolation coupling (1) according to the present invention as in FIG. 3 under load conditions.

[0050] In FIG. 4, the coupling (1) is illustrated at the operating point (WP, see FIG. 11) under a load condition, for example, by a positive static torque (T). In the illustrated example, the torque (T) acts counterclockwise around the axis of rotation (1a). The twist angle (φ) between the first coupling part (2) and the second coupling part (3) t ) is not 0.

[0051] The plate (6) is displaced relative to the left inner side wall (5a) of the receiving space (5) of the first coupling part (2), and in this case, the spring members (8, 9a, 9b) of the spring assembly (10) are compressed.

[0052] The illustrated spring assembly (10) enables the transmission of static torque (T) regardless of its direction. Torsional vibration isolation by the torsional vibration isolation coupling (1) is achieved only for static torque (T) acting in the positive direction [here, counterclockwise around the axis of rotation (1a)]. Here, the term “positive direction” means that the torque (T) displaces the plate (6) of the damping unit (4) in the positive translational direction (u), and in this case, the plate (6) compresses the spring members (8, 9a, 9b) against the left inner side wall (5a) of the receiving space (5) of the first coupling part (2).

[0053] FIG. 5 shows a schematic radial cross-sectional view of the coupling (1) of FIG. 1. FIG. 6 shows a schematic cross-sectional view of a second embodiment of the torsional vibration isolation coupling (1) according to the present invention in a no-load state (T=0).

[0054] Unlike the first embodiment according to FIG. 2, the damping unit (4) of the coupling (1) is provided with two non-linear spring assemblies (10 and 10'), which are arranged reflectively symmetrically with respect to a virtual radial centerline of the plate (6) within the receiving space (5) of the first coupling part (2).

[0055] A further difference from the first embodiment is that the other ends of the spring members (8, 9a, 9b) of the first spring assembly (10) and the spring members (8', 9'a, 9'b) of the second spring assembly (10'), which are arranged in reflection symmetry with respect to the first spring assembly (10), are each connected to intermediate plates (6c, 6d). In this way, the nonlinear damping unit (4) each has a positive stiffness (k PSE A spring member (8, 8') having ) and negative stiffness (k NSE It includes two parallel connections composed of spring members (9, 9') having ).

[0056] The first intermediate plate (6c) is placed on the first end surface (6a) of the plate (6), and the second intermediate plate (6d) is placed on the second end surface (6b) of the plate (6). However, the intermediate plates (6c, 6d) are not connected to the plate (6).

[0057] In FIG. 8, the first load state at the operating point (WP) under load by positive static torque (T) is exemplarily illustrated in the load states of the second embodiment of the coupling (1), and the intermediate plate (6d) is maintained in the unloaded position because it is not connected to the plate (6), in which case the other intermediate plate (6c) is pressed against the spring assembly (10) by the plate (6), and the spring members (8, 9a, 9b) are compressed against the inner side wall (5a).

[0058] In this way, the second embodiment of the torsional vibration isolation coupling (1) enables torsional vibration isolation for both positive static torque and negative static torque (T).

[0059] FIGS. 9 and FIGS. 10 symbolically illustrate a spring assembly (10, 10').

[0060] The concept regarding torsional vibration isolation of the torsional vibration isolation coupling (1) is schematically illustrated in FIGS. 9 and FIGS. 10.

[0061] The first spring assembly (10) has a positive spring stiffness (k PSE A spring member (8) having ) and negative spring stiffness (k NSE It includes a spring member (9) having a spring member (9a and 9b). The spring assembly (10) is positioned between the first coupling part (2) and the plate (6) as described above.

[0062] Spring member (8; k PSE and 9a, 9b;k NSE Total spring stiffness (k) through parallel connection total ) is obtained, and the stiffness of the spring member is two spring members (8; k PSE and 9; k NSE This is the result of adding the damping spring characteristic curves (11, 12) of ), which is schematically illustrated in FIG. 10. This is explained in more detail below in relation to FIG. 11.

[0063] The above description describes a spring member (8'; k PSE and 9'a, 9'b'; k NSE The same applies to the second spring assembly (10') having ).

[0064] FIG. 11 illustrates the corresponding spring characteristic curve, which represents the spring characteristic curve of the spring assembly (10, 10').

[0065] The twist angle (φ) between the coupling parts (2, 3) t ) is displayed in degrees on the X-axis of the diagram. Torque (T) is displayed in Nm on the Y-axis.

[0066] This diagram shows positive stiffness (k PSE A spring characteristic curve (11) of a spring member (8, 8') having ) is illustrated, and negative stiffness (k NSE A spring characteristic curve (12) of a spring member (9, 9') having ) is illustrated, and the total stiffness (k total A damping spring characteristic curve (13) of a spring assembly (10, 10') having ) is illustrated.

[0067] Transmits torque (T) = 5000 Nm and twist angle (φ t The operating point of the coupling (1) where a static coupling torsion having ) = 2° is achieved is indicated by reference numeral 14. At this operating point (14), a positive stiffness (k PSE The stiffness of the spring member (8, 8') having ) is negative stiffness (k NSE Since it is compensated by the spring member (9, 9') having ), the resulting damping spring characteristic curve (13) of the coupling (1) has a total stiffness that is negligible at this operating point (14) [horizontal curve of the spring characteristic curve (13)].

[0068] Outside this operating point (14), the damping spring characteristic curve (13) of the coupling (1) increases as the deflection increases, i.e., as the twist angle (φ) tIt has a torque (T) that increases as ) increases. The nonlinearity of this damping spring characteristic curve (13) of the coupling (1) enables, on the one hand, the transmission of a statically operating coupling torque (T) and, on the other hand, the separation of the drive train from the torque (T) fluctuation occurring at a fixed operating point (14). Explanation of the symbols

[0069] 1: Coupling 1a: Rotation axis 2: First coupling part 2a: Home 2b: Annular region 3: Second coupling part 4: Damping unit 5: Accommodation space 5a, 5b: Side walls 5c: Base wall 5d: Ceiling wall 6: Plate 6a, 6b: End surfaces 6c, 6d: Intermediate plates 7: Connecting rod 8, 8': Spring member 9, 9a, 9b; 9', 9'a, 9'b: Spring member 10 10': Spring assembly 11, 12, 13: Spring characteristic curves 14: Actuation point k: spring stiffness u: translational direction T: Torque φ t: Twist angle

Claims

Claim 1 A torsional vibration isolation coupling (1) having a rotation axis (1a), wherein the torsional vibration isolation coupling (1) comprises a first coupling part (2) as an input side of the coupling (1), a second coupling part (3) as an output side of the coupling (1), and a damping unit (4), wherein the damping unit (4) comprises at least one spring assembly (10, 10') formed by a non-linear spring assembly (10, 10') having a damping spring characteristic curve (13), and the at least one non-linear spring assembly (10, 10') has a positive spring stiffness (k PSE At least one spring member (8, 8') having ) and negative spring stiffness (k NSE A torsional vibration isolation coupling comprising at least one spring member (9, 9') having a) and a first coupling part (2) as an input side of the coupling (1) and a second coupling part (3) as an output side of the coupling (1) are coupled to at least one non-linear spring assembly (10, 10') through a damping unit (4), and at least one non-linear spring assembly (10, 10') forms a plate-shaped interface between the plate (6) and the first coupling part (2) of the coupling (1) and the second coupling part (3) for bidirectional force transmission and motion transmission. Claim 2 A torsional vibration isolation coupling according to claim 1, characterized in that the plate (6) is coupled to the second coupling part (3) of the coupling (1) through the connecting rod (7). Claim 3 A torsional vibration isolation coupling according to claim 1 or 2, wherein the plate (6) is guided to be displaceable in a translational direction (u) within the receiving space (5) of the first coupling part (2) of the coupling (1), and the translational direction (u) extends in a tangential direction of the first coupling part (2) of the coupling (1). Claim 4 In paragraph 3, negative spring stiffness (k NSE A torsional vibration isolation coupling characterized in that at least one spring member (9, 9') of at least one spring assembly (10, 10') having ) comprises two spring members (9a, 9b) arranged in pairs in a manner inclined with respect to the translational direction (u), the first ends of the two spring members (9a, 9b) are connected to a first coupling portion (2) of the coupling (1) with space between them, and the other ends of the two spring members (9a, 9b) are connected to a plate (6) or an intermediate plate (6c, 6d) acting together with the plate (6) in a combined state at a common connection point. Claim 5 A torsional vibration isolation coupling according to claim 4, characterized in that the space between the first ends of the spring members (9a, 9b) extends in a direction perpendicular to the translational direction (u). Claim 6 A torsional vibration isolation coupling according to claim 4, characterized in that the intermediate plates (6c, 6d) are disposed on the end surfaces (6a, 6b) of the plate (6) without being connected to the plate (6). Claim 7 A torsional vibration isolation coupling according to claim 1 or 2, characterized in that the first coupling part (2) of the coupling (1) and the second coupling part (3) of the coupling (1) are arranged coaxially with each other. Claim 8 A torsional vibration isolation coupling according to claim 1 or 2, characterized in that the coupling (1) is a coupling (1) of a drive train of a fixed-actuated application example. Claim 9 delete Claim 10 delete Claim 11 delete

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