TORSION DAMPING ARRANGEMENT FOR THE POWERTRAIN IN A VEHICLE

Abstract

A torsional vibration damping arrangement includes: an input region, an output region, and a coupling arrangement communicating with the output region. A phase shifter arrangement communicates with the input region. A torque transmission path extending between the input region and the output region transmits a total torque. The torque transmission path is divided into first and second torque transmission paths, which paths are guided back together again at the coupling arrangement. An input torsional vibration is divided into two torsional vibration components by being conducted respectively via the first and second torque transmission paths and are destructively superimposed at the coupling arrangement to form a minimized output torsional vibration relative to the input torsional vibration. A planet wheel carrier is constructed as a modular building block planet carrier element and includes at least a first connection area.

Claims

1-7. (canceled)

8. A torsional vibration damping arrangement (10) for a powertrain of a motor vehicle, comprising: an input region (50) arranged to be driven in rotation around an axis of rotation (A), the input region (50) including a primary mass (1); an output region (55) including a secondary mass (20); and a coupling arrangement (41) that communicates with the output region (55), the coupling arrangement (41) including a planetary gear unit (61) having a planet wheel carrier (9), a planet wheel pin (11), and a planet wheel element (45); a first input element (53); a second input element (54); an output element (85); a torque transmission path (46) configured to transmit a total torque (Mges), the torque transmission path (46) extending between the input region (50) and the output region (55), wherein the torque transmission path (46) from the input region (50) to the coupling arrangement (41) is divided into a first torque transmission path (47), for transmitting a first torque component (Ma1), and a parallel second torque transmission path (48), for transmitting a second torque component (Ma2), and wherein the first torque transmission path (47), and the second torque transmission path (48), and the respective first torque component (Ma1) and second torque component (Ma2), are guided back together at the coupling arrangement (41) to form an output torque (Maus); and a phase shifter arrangement (43) in the first torque transmission path (47), the phase shifter arrangement (43) including a vibration system (56) with a first stiffness (35), the first stiffness (35) including a spring arrangement (4), wherein an input torsional vibration (EDSw) proceeding from the input region (50) is divided into a first torsional vibration component (DSwA1) and a second torsional vibration component (DSwA2) by being conducted via the first torque transmission path (47) and via the second torque transmission path (48) respectively, wherein during an operation of the vibration system (56) in a speed range above at least one limit speed at which the vibration system (56) is operated in a resonant range, the first torsional vibration component (DSwA1) is superposed with the second torsional vibration component (DSwA2) at the coupling arrangement (41) such that the first torsional vibration component (DSwA1) and the second torsional vibration component (DSwA2) are destructively superimposed, such that an output torsional vibration (ADSw) minimized relative to the input torsional vibration (EDSw) is present at the output element (85) of the coupling arrangement (41), and wherein the planet wheel carrier (9) is constructed as a modular building block planet carrier element (95) and includes at least a first connection area (31) radially outwardly of a fastening of the planet wheel pin (11) at the planet wheel carrier (9), by which first connection area (31) the modular building block planet carrier element (95) is connected to the primary mass (1) so as to be fixed with respect to rotation relative to primary mass (1).

9. The torsional vibration damping arrangement (10) according to claim 8, wherein the first input element (53) of the coupling arrangement (41) is connected to an output element (36) of the phase shifter arrangement (43) and the planet wheel element (45), the second input element (54) of the coupling arrangement (41) is connected to the input region (50) and the planet wheel element (45), and the planet wheel element (45) is connected to the first input element (53), the second input element (54) and the output element (85), and wherein the output element (85) forms the output region (55).

10. The torsional vibration damping arrangement (10) according to claim 8, wherein the phase shifter arrangement (43) includes a vibration system (56) with the primary mass (1) and an intermediate element (57) rotatable with respect to the primary mass (1) around the axis of rotation (A) against the action of a spring arrangement (4).

11. The torsional vibration damping arrangement (10) according to claim 8, wherein the modular building block planet carrier element (95) includes a fastening region (62) by which the modular building block planet carrier element (95) is connected to the input region (50) so as to be fixed with respect to rotation relative to the input region (50).

12. The torsional vibration damping arrangement (10) according to claim 8, wherein the modular building block planet carrier element (95) comprises a second connection area (32) by which the modular building block planet carrier element (95) is connected to a connection element (15) of the input region (50) so as to be fixed with respect to rotation relative to the connection element (15) of the input region (50).

13. The torsional vibration damping arrangement (10) according to claim 12, wherein the first connection area (31) and the second connection area (32) are constructed so as to be impermeable to a viscous medium.

14. The torsional vibration damping arrangement (10) according to claim 8, wherein the torsional vibration damping arrangement (10) includes a torque converter (88) and a lockup clutch (89).

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Preferred embodiment examples of the invention will be described in the following with reference to the accompanying drawings. In the drawings:

[0022] FIG. 1 is a torsional vibration damping arrangement with a modular building block planet carrier element and a first connection area;

[0023] FIG. 2 is a torsional vibration damping arrangement as in FIG. 1, but with a second connection area;

[0024] FIG. 3 is a torsional vibration damping arrangement as in FIG. 1, but with a different position of the seal elements and a modified cover element;

[0025] FIG. 4 is a detail in the area of the phase shifter arrangement;

[0026] FIG. 5 is a torsional vibration damping arrangement, but in combination with a torque converter and a lockup clutch;

[0027] FIG. 6 is a torsional vibration damping arrangement as described in FIG. 1, but with a modified cover element;

[0028] FIG. 7 is a torsional vibration damping arrangement as described in FIG. 1, but with a modified cover element; and

[0029] FIG. 8 is a torsional vibration damping arrangement with a modular building block planet carrier element in connection with a two-row phase shifter arrangement.

DETAILED DESCRIPTION OF THE PRESENTLY PREFERRED EMBODIMENTS

[0030] FIG. 1 shows a torsional vibration damping arrangement 10 that operates on the principle of power splitting or torque splitting. The torsional vibration damping arrangement 10 can be arranged in a powertrain of a vehicle between a drive unit 60 and the following segment of the powertrain, i.e., for example, a starting element 65 such as a friction clutch, a hydrodynamic torque converter or the like.

[0031] The torsional vibration damping arrangement 10 comprises an input region, designated generally by 50. This input region 50 can be connected, for example, as in the present case, through a crankshaft 18 of a drive unit 60 configured as an internal combustion engine. In the input region 50, the torque received by the drive unit 60 splits into a first torque transmission path 47 and a second torque transmission path 48. In the region of a coupling arrangement, designated generally by reference numeral 41, the torque components guided via the two torque transmission paths 47, 48 are introduced into the coupling arrangement 41 by a first input element 53 and a second input element 54 and are guided together again and then conveyed to an output region 55.

[0032] A vibration system, designated generally by reference numeral 56, is integrated in the first torque transmission path 47. The vibration system 56 operates as phase shifter arrangement 43 and comprises a primary mass 1, which is to be linked, for example, to the drive unit 60, and an intermediate element 57, which guides the torque farther and which is constructed in this instance as an input ring gear carrier 84 at which an additional mass 20 can also be arranged so as to be fixed with respect to rotation relative to the input ring gear carrier 84 as is also shown in FIG. 1. The primary mass 1 and a cover element 22, which are connected to one another, preferably by a weld joint 78, so as to be fixed with respect to rotation relative to one another substantially completely enclose toward the radially outer side a spatial region 33 in which is received, with respect to the radial arrangement, a spring arrangement 4 for the vibration system 56. A starter gear 34 is fastened in this instance to the cover element 22 (see FIG. 3) so as to be fixed with respect to rotation relative to it, preferably by a weld joint. Alternatively, the starter gear 34 can also be fastened to the primary mass 1. The spring arrangement 4 comprises a plurality of spring arrangements 58 which are arranged successively in circumferential direction and possibly also so as to be nested one inside the other. Each spring arrangement preferably comprises at least one helical compression spring or bow spring. The spring arrangement 58 of the spring arrangement 4 is supported by a control plate 2 at the primary mass 1 on the one hand and at an input element 82 on the other hand, and in this case the input element 82 comprises the input ring gear carrier 84 and an input ring gear 83, which is connected to the latter so as to be fixed with respect to rotation relative to it. The input element 82 can also be fashioned from one structural component part, not shown here. The rotationally locked connection of input ring gear carrier 84 and input ring gear 83 is preferably carried out by a weld joint, a rivet connection, a screw joint, a glue joint, an interference fit, a positive engagement connection or a comparable joining method, or a combination of the joining methods mentioned above. The input ring gear 83 guides the torque that was guided via the first torque transmission path 47 and, therefore, via the phase shifter arrangement 43 to a planet wheel element 45 of the coupling arrangement 41. In this case, the planet wheel element 45 comprises an input planet wheel 80 and an output planet wheel 81 arranged so as to be axially staggered. The input ring gear 83, which meshes with the input planet wheel 80, constitutes the first input element 53 of the coupling arrangement 41.

[0033] In the second torque transmission path 48, the torque is guided proceeding from the drive unit 60 via the crankshaft 18 into the second input element 54. This second input element 54 is connected, preferably by a screw joint 68, in this case by the crankshaft screw 17, to the crankshaft 18 so as to be fixed with respect to rotation relative to the crankshaft and forms the carrier element 12 of the planet wheel carrier 9 of the coupling arrangement 41. Accordingly, together with the flange element 70, the carrier element 12 and the flange element 70 form the actual planet wheel carrier 9. This is particularly advantageous because the planet wheel pin 11 is supported on both sides, i.e., at the carrier element 12 on the one hand and the flange element 70 on the other hand. This prevents a tilting of the planet wheel pin. The first torque transmission path 47, which is guided via the input ring gear 83 into the coupling arrangement 41, and the second torque transmission path 48, which is guided via the second input element 54 formed by the planet wheel carrier 9, are guided together to form one torque by the planet wheel element 45 of the coupling arrangement 41, which planet wheel element 45 is rotatably supported at the planet wheel carrier 9 by a planet wheel pin 11. The combined torque is conveyed via an output ring gear 86 and an output ring gear carrier 87, which is connected to the output ring gear carrier 86 so as to be fixed with respect to rotation relative to it and which output ring gear 86 and output ring gear carrier 87 together form an output element 85, to an output flange element 75, which is connected to the output ring gear carrier 87 so as to be fixed with respect to rotation relative to the output ring gear carrier 87 and which forms output element 49 in this instance and, from there, for example, is supplied to a secondary mass, not shown here, a friction clutch, or directly to a transmission.

[0034] A first seal element 24 and a second seal element 25 are used to seal a wet space 63 relative to a surrounding area 69, this wet space 63 preferably being filled with a viscous medium such as oil or grease to reduce friction and, therefore, wear. In this regard, the first seal element 24 is positioned between the output ring gear carrier 87 and a flange element 70. A relative rotation may take place between the output ring gear carrier 87 and the flange element 70. The first seal element 24, which is preferably constructed as a radial shaft sealing ring 28, can be installed between these two structural component parts and takes over a sealing function for the wet space 63 relative to the surrounding area 69 even though the output ring gear carrier 87 and the flange element 70 rotate relative to one another. The flange element 70 is connected to the planet wheel carrier 9 so that no viscous medium can escape to the surrounding area 69 from the wet space 63 at an area where the flange element 70 is connected to the planet wheel carrier 9. In addition, the flange element 70 is constructed such that it further supports the planet wheel pin 11. The planet wheel pin 11 is advantageously secured against tilting through this embodiment form.

[0035] The second seal element 25 is positioned between the cover element 22 and the output flange element 75. A relative rotation can take place between the cover element 22 and the output flange element 75. The second seal element 25, which is likewise preferably constructed as a radial shaft sealing ring 29, can seal the wet space 63 relative to the surrounding area 69 even when there is a relative rotation between the cover element 22 and the output flange element 75.

[0036] It is advantageous to use carry over parts to enable economical production. For this reason, the first seal element 24 and the second seal element 25 are constructed in this instance so as to be structurally identical. This results in advantages for purchasing component parts and for using a smaller number of assembly tools because only one size is used for the seal elements. However, different sizes of seal elements can also be used, although this is not shown in the drawing.

[0037] To allow even more carry over parts to be used for an economical production, the planet wheel carrier 9 is constructed as a modular building block planet carrier element 95 with a first connection area 31. The modular building block planet carrier element 95 is constructed in such a way that it can be installed as a standardized component part in combination with differently constructed connection component parts. This is particularly advantageous when the spring set 4 of the phase shifter arrangement 43 must be constructed differently because of different engine types. The modular building block planet carrier element 95 can then be connected by the first connection area 31, which is located radially outside in this instance to the primary mass 1, so as to be fixed with respect to rotation relative to it, which primary mass 1 also receives the spring set 4 in this instance. This is advantageously carried out by a weld joint or a similar known and suitable connection. This connection is advantageously constructed so as to be impermeable to a viscous medium.

[0038] In a radially inner region, the modular building block planet carrier element 95 is constructed as a fastening flange 21 in order to connect the modular building block planet carrier element 95 to the crankshaft 18 so as to be fixed with respect to rotation relative to it, preferably by crankshaft screws 17.

[0039] In an advantageous construction, a modular system of the torsional vibration damping arrangement 10 can be realized by dividing the primary mass 1 in two in this way.

[0040] FIG. 2 shows a torsional vibration damping arrangement 10 as in FIG. 1, but in which the modular building block planet carrier element 95 comprises an additional second connection area 32 located radially inside in this instance. As a result of this second connection area 32, the modular building block planet carrier element 95 can be standardized to an even greater degree because a connection to a corresponding crankshaft fastening geometry is no longer effected through the modular building block planet carrier element 95, but rather through a separate structural component part, such as a connection element 15, as in this case. The modular building block planet carrier element 95 is connected to the connection element 15 so as to be fixed with respect to rotation relative to it by the second connection area 32, preferably by a weld joint or another known and suitable connection, which is preferably impermeable to a viscous medium. As a result of this embodiment form, the modular building block planet carrier element 95 is available for an even broader embodiment form of different torsional vibration damping arrangements. Consequently, the modular building block planet carrier element 95 can be manufactured as a standardized component part.

[0041] FIG. 3 shows a torsional vibration damping arrangement 10 such as was already described in FIG. 1, but with a first seal element 24 and second seal element 25, and the first seal element 24 and second seal element 25 have different sizes. Further, the output flange element 75 is also rotatably mounted at the flange element 70 additionally by a bearing element 77 which can advantageously be constructed as a ball bearing. To this end, the cover element 22 is provided with a lateral stabilization geometry 23, which additionally forms a centering edge 26 for receiving a starter gear 34. The stabilization geometry 23 serves not only to receive the starter gear, but rather also serves to stabilize the cover element 22, which has a positive outcome during high centrifugal forces and is likewise beneficial for sealing with the second seal element 25 because the cover element 22 deforms less under the influence of centrifugal force due to the stabilization geometry.

[0042] FIG. 4 shows a detail from FIG. 3 in the region of the phase shifter arrangement 43. Advantageously shown therein is a formation 90, which is formed from the primary mass 1 by a shaping process, for example. The formation 90 receives the control plate 3 and can clamp or press the control plate 3 through a further shaping process. The formation 90 can be constructed like a rivet 91 formed from the primary mass 1. The advantages arise as a result of the fact that the formation 91 can be used as rivet 91 without needing to provide the primary mass with a bore hole for a rivet to pass through. This is particularly advantageous when this area is to be impermeable to a viscous medium. Alternatively, laser welding, soldering, a riveting process, a spot welding process or resistance welding can also be provided.

[0043] FIG. 5 shows a torsional vibration damping arrangement 10 with modular building block planet carrier element 95 installed in combination with a torque converter 88 and a lockup clutch 89. In this respect, two torque transmission paths must be distinguished on principle: the torque transmission with a closed lockup clutch 89 or with an open clutch 89. These two distinct torque transmission paths are known from the prior art. The torque transmission path with closed lockup clutch 89 will be addressed herein by preference. With closed lockup clutch 89, the torque introduced from the crankshaft 18 runs via the primary mass 1, via the lockup clutch 89 and via an output element 99 of the lockup clutch 89 to two cover plates 27. From this point, the torque is divided and is guided further via a first torque transmission path 47 and a second torque transmission path 48. In the first torque transmission path 47, the torque component is guided from the cover plates 27 via a radially inner spring arrangement 5 and via a hub disk 14 to a radially outer spring arrangement 4. Only one spring arrangement can also be installed, although this is not shown. Proceeding from the radially outer spring arrangement 4, the torque component arrives at a coupling arrangement 41 in the form of a planetary gear unit 61 in this instance via an input ring gear carrier 84 and via an input ring gear 83 connected to the latter so as to be fixed with respect to rotation relative to it.

[0044] The second torque transmission path 48 runs from the output element 99 of the lockup clutch 89 directly to a planet wheel carrier 9 of a modular building block planet carrier element 95. In this case, the modular building block planet carrier element 95 is connected by a first connection area 31, located radially outwardly in this case, by a rivet connection 64 to the output element 99 of the lockup clutch 89 so as to be fixed with respect to rotation relative to it.

[0045] Accordingly, one torque component is guided directly to the planetary gear unit, where it is reunited with and superposed with the torque component that was guided via the first torque transmission path 47. The reunited torque reaches an output flange element 72 by an output ring gear 86 connected to an output ring gear carrier 87 and a turbine 71 of the torque converter 88 so as to be fixed with respect to relative rotation. The output flange element 72 can be connected, for example, to a transmission input shaft, not shown.

[0046] FIG. 5 shows the configuration of the modular building block planet carrier element 95, which can also be installed in its embodiment form in torsional vibration damping arrangements without torque converters 88 as is shown in FIGS. 1 and 2. Accordingly, the advantages of the modular building block planet carrier element 95 result from its wide range of possible applications in combination with differently constructed component parts of a torsional vibration damping arrangement without requiring modification of the modular building block planet carrier element 95. This is particularly advantageous for an economical production.

[0047] FIG. 6 shows a torsional vibration damping arrangement 10 such as was already described in FIG. 1, but with a modified cover element 22. The aim is to form the cover element such that it deforms only minimally under the influence of a centrifugal force and such that the resulting enclosed space is as small as possible so that only a small amount of viscous material is required for lubrication. As has already been described, the rotationally locked connection between the cover element 22 and the primary mass 1 is to be constructed so as to be impermeable to the viscous material. The rotationally locked connection between the cover element and the primary mass is preferably carried out by a weld joint 78. A central position of the weld joint has the further advantage that the connection is located as far as possible from elevated stress concentrations in the corners.

[0048] FIG. 7 shows a torsional vibration damping arrangement 10 such as was already described with reference to FIG. 6, but with a modified cover element 22. The description referring to FIG. 6 also applies here for a configuration of the cover element 22. The cover plate 22 is to be constructed so as to be as stiff as possible. In this instance, the cover plate 22 has an additional centering structure 26 that can be used to receive a starter gear, not shown.

[0049] FIG. 8 shows a torsional vibration damping arrangement 10 that operates on the principle of power splitting or torque splitting as in FIG. 1. In contrast to the embodiment form shown in FIG. 1, the embodiment form in this case comprises a two-row phase shifter arrangement 44 with a first spring arrangement 51, arranged radially outwardly in this case, and a second spring arrangement 59 which is arranged radially inwardly of the first spring arrangement 51. The two spring sets 51 and 59 are connected in series. As has already been described referring to FIG. 1, the torsional vibration damping arrangement 10 comprises an input region 50. In the input region 50, the received torque branches into a first torque transmission path 47 and a second torque transmission path 48. In the region of the coupling arrangement 41, which can also be constructed in this instance as a planetary gear unit 61, the torque components Ma1 and Ma2, which are guided via the two torque transmission paths 47, 48, and the torsional vibration components DSwA1 and DsWA2 contained therein, are guided by a first input element 53 and a second input element 54 into the coupling arrangement 41 and guided together again and then conveyed onward to an output region 55 as an output torque Maus with an output torsional vibration ADSw contained therein.

[0050] The two-row phase shifter arrangement 44 with the first spring arrangement 51 and the second spring arrangement 59 is integrated in the first torque transmission path 47. The spring arrangements 51 and 59 can be formed of a plurality of helical compression springs arranged successively in circumferential direction and, depending on the embodiment form, also nested one inside the other or can also be constructed as bow springs. The first spring arrangement 51 is supported by control elements 6 connected to the primary mass 1 at the primary mass 1 on the one hand and at a hub disk 66 on the other hand. The second spring arrangement 59 is supported at the hub disk 66 on the one hand and at an intermediate element 57 on the other hand and with a cover plate 67 fixedly connected thereto. The input ring gear 83 is fastened by a connection element 73 to the intermediate element 57, which can also be designated as input ring gear carrier 84. so as to be fixed with respect to rotation relative to it. The use of the connection element 73 is only a constructional variant. The input ring gear can also be fastened directly to the intermediate element 57. The figure shows the additional masses 20 which, depending on embodiment form and required piece numbers, can be fastened to the intermediate element 57 so as to be fixed with respect to rotation relative to the intermediate element 57 in order to increase the mass moment of inertia of the intermediate element 57 so as to improve the functioning of the phase shifter arrangement. The also shows in this embodiment form with a two-row phase shifter arrangement 44 the modular building block planet carrier element 95 fastened to the primary mass 1 so as to be fixed with respect to rotation relative to it by means of a connection flange 74 in this case. The output is carried out in a known manner via an output ring gear 86 and an output ring gear carrier 87 to the output region 55. In this case, a disk element 79 that can receive a known friction disk clutch, not shown, is connected to the output ring gear carrier 87 so as to be fixed with respect to rotation relative to the output ring gear carrier 87. In another embodiment form, not shown herein, the disk element 79 can be omitted and the output ring gear carrier 87 can then be directly connected to the transmission, for example, a dual clutch transmission.

[0051] Thus, while there have been shown and described and pointed out fundamental novel features of the invention as applied to a preferred embodiment thereof, it will be understood that various omissions and substitutions and changes in the form and details of the devices illustrated, and in their operation, may be made by those skilled in the art without departing from the spirit of the invention. For example, it is expressly intended that all combinations of those elements and/or method steps which perform substantially the same function in substantially the same way to achieve the same results are within the scope of the invention. Moreover, it should be recognized that structures and/or elements and/or method steps shown and/or described in connection with any disclosed form or embodiment of the invention may be incorporated in any other disclosed or described or suggested form or embodiment as a general matter of design choice. It is the intention, therefore, to be limited only as indicated by the scope of the claims appended hereto.

REFERENCE CHARACTERS

[0052] 1 primary mass [0053] 2 secondary mass [0054] 3 control plate [0055] 4 spring arrangement [0056] 5 spring arrangement [0057] 6 control element [0058] 9 planet wheel carrier [0059] 10 torsional vibration damping arrangement [0060] 11 planet wheel pin [0061] 12 carrier element [0062] 14 hub disk [0063] 15 connection element [0064] 17 crankshaft screw [0065] 18 crankshaft [0066] 20 additional mass [0067] 21 fastening flange [0068] 22 cover element [0069] 23 stabilization geometry [0070] 24 first seal element [0071] 25 second seal element [0072] 26 centering edge [0073] 27 cover plate [0074] 28 radial shaft sealing ring [0075] 29 radial shaft sealing ring [0076] 31 first connection area [0077] 32 second connection area [0078] 33 spatial region [0079] 34 starter gear [0080] 35 first stiffness [0081] 36 output element [0082] 41 coupling arrangement [0083] 43 phase shifter arrangement [0084] 44 two-row phase shifter arrangement [0085] 45 planet wheel element [0086] 46 torque transmission path [0087] 47 first torque transmission path [0088] 48 second torque transmission path [0089] 50 input region [0090] 51 first spring arrangement [0091] 52 superposition unit [0092] 53 first input element [0093] 54 second input element [0094] 55 output region [0095] 56 vibration system [0096] 57 intermediate element [0097] 58 spring arrangement [0098] 59 second spring arrangement [0099] 60 drive unit [0100] 61 planetary gear unit [0101] 62 fastening region [0102] 63 wet space [0103] 64 rivet connection [0104] 65 starting element [0105] 66 hub disk [0106] 67 cover plate [0107] 68 screw joint [0108] 69 surrounding area [0109] 70 flange element [0110] 71 turbine [0111] 72 output flange element [0112] 73 connection element [0113] 74 connection flange [0114] 75 output flange element [0115] 77 bearing element [0116] 78 weld joint [0117] 79 disk element [0118] 80 input planet wheel [0119] 81 output planet wheel [0120] 82 input element [0121] 83 input ring gear [0122] 84 input ring gear carrier [0123] 85 output element [0124] 86 output ring gear [0125] 87 output ring gear carrier [0126] 88 torque converter [0127] 89 lockup clutch [0128] 90 formation [0129] 91 rivet [0130] 95 modular building block planet carrier element [0131] 99 output element [0132] A axis of rotation [0133] Mges total torque [0134] Ma1 torque component 1 [0135] Ma2 torque component 2 [0136] Maus output torque [0137] EDSw input torsional vibration [0138] DSwA1 torsional vibration component 1 [0139] DSwA2 torsional vibration component 2 [0140] ADSw output torsional vibration