Torsional vibration damper system for a drive train of a motor vehicle and method for producing the torsional vibration damper system

Abstract

Torsional vibration damper system (35) for a drive train (10) of a motor vehicle, - wherein the torsional vibration damper system (35) has a first damper stage (80) and a rotor shaft (105), - wherein the first damper stage (80) has a first damper part (125) rotatably mounted about a rotation axis (15) with a flange section (130) to which a rivet connection (160) is fastened, - wherein the rotor shaft (105) has a shaft shoulder (190) extending outwards in the radial direction, - wherein the shaft shoulder (190) has an axial overlap with the rivet connection (160), - wherein the shaft shoulder (190) has a support surface (230) for riveting the riveted connection (160) on an axial side facing the riveted connection (160).

Description

[0001] The invention relates to a torsional vibration damper system according to patent claim 1 and a method for producing the torsional vibration damper system according to patent claim 8.

[0002] A torsional vibration damper is known from document DE 10 2009 042 838 A1. Further prior art is provided by DE 10 2011 102 821 A1, DE 10 2019 115 350 A1, and DE 10 2010 034 094 A1.

[0003] The object of the invention is to provide an improved torsional vibration damper system for a drive train of a motor vehicle. Furthermore, it is an object to provide an improved method for manufacturing the torsional vibration damper system.

[0004] This object is achieved by means of a torsional vibration damper system according to claim 1 and by means of a method for producing the torsional vibration damper system according to claim 8. Advantageous embodiments are specified in the dependent claims.

[0005] It has been recognized that an improved torsional vibration damper system for a drive train of a motor vehicle can be provided in that the torsional vibration damper system has a first damper stage and a rotor shaft. The first damper stage has a first damper part which is rotatably mounted about an axis of rotation and has a flange section to which a riveted connection is fastened. The rotor shaft has a shaft shoulder which extends outwards in the radial direction. The shaft shoulder has an axial overlap with the riveted connection. The shaft shoulder has a support surface for riveting the riveted connection on an axial side facing the riveted connection.

[0006] This design has the advantage that the riveted joint can be arranged so that it is concealed in the axial direction by the shaft shoulder, and the riveted joint can be created by the support surface. This eliminates the need for a different type of connection than the riveted joint, and the riveted joint is particularly well suited for connecting the flange section to another component of the torsional vibration damper system. Furthermore, the riveted joint is particularly cost-effective.

[0007] In a further embodiment, the first damper stage has a first spring element and a second damper part, wherein the first damper part is rotatable about the axis of rotation relative to the second damper part against the action of the first spring element, wherein the rotor shaft has a shaft section which adjoins the shaft shoulder, wherein the first damper part and / or second damper part is arranged on the shaft section so as to be rotatable relative to the rotor shaft, wherein an axial positioning device with at least one clamping element is arranged on the shaft section for the axial positioning of the first damper part or the second damper part, wherein the axial positioning device is arranged axially between the first damper part and / or the second damper part and the shaft shoulder,wherein the first damper part and / or the second damper part is arranged to be displaceable from a first position, against the action of the clamping element of the axial positioning device, in the direction of the shaft shoulder into a second position different from the first position. Due to the axial displaceability, the riveted joint can be brought into contact with the support surface in the second position to establish the riveted joint. In the first position, grinding of the riveted joint on the support surface is avoided.

[0008] In a further embodiment, the torsional vibration damper system has an input side and an output side, wherein a torque subjected to the rotational irregularity can be introduced into the torsional vibration damper system via the input side, wherein the first damper stage is arranged downstream of the input side with respect to a torque flow of the torque from the input side to the output side and is designed to cancel the rotational irregularity, wherein the output side is arranged on the flange section, wherein the flange section can be connected in a rotationally fixed manner to a plate carrier of a clutch device by means of the rivet connection.

[0009] In a further embodiment, the torsional vibration damper system has a second damper stage and an input side, wherein a torque subjected to the rotational irregularity can be introduced into the torsional vibration damper system via the input side, wherein the second damper stage is arranged between the input side and the first damper stage with respect to a torque flow of the torque that can be provided at the input side, wherein the second damper stage has a third damper part rotatably mounted about an axis of rotation, a second spring element and a fourth damper part for at least partially eliminating the rotational irregularity, wherein the rivet connection connects the fourth damper part to the flange section in a rotationally fixed manner, wherein the third damper part is rotatable about the axis of rotation relative to the fourth damper part against the action of the second spring element.

[0010] In a further embodiment, the riveted connection has a rivet extending in the axial direction. The rivet extends through a second rivet opening in the flange section, with a second rivet head of the riveted connection being formed on a side of the rivet facing away from the shaft shoulder, with the second rivet head directly or indirectly fastening the flange section. It is particularly advantageous if the second rivet head is formed from a material of the rivet, in particular from an original rivet shank of the rivet. The rivet and the second rivet head are thus formed in one piece and from the same material. Alternatively, the riveted connection can also be designed in two parts.

[0011] In a further embodiment, the shaft shoulder has a contact surface for the contact of a counterholder on an axial side facing away from the riveted connection, wherein the contact surface and / or the support surface is preferably flat and preferably extends in a rotational plane perpendicular to the rotational axis. This configuration has the advantage that riveting forces for establishing the riveted connection can be particularly well supported by the counterholder and, on the other hand, can be introduced into the counterholder via the support surface and the shaft shoulder. This allows the rivet head to be particularly well formed.

[0012] In a further embodiment, the second damper part has a flange connection with a through-hole, wherein the through-hole in the flange connection and the riveted connection are arranged so as to axially overlap. From a manufacturing perspective, it is particularly advantageous if the through-hole and the riveted connection are arranged so as to axially overlap when the torsional vibration damper system is unloaded. This makes the riveted connection particularly easy to manufacture.

[0013] A method for producing the torsional vibration damper system described above can be achieved by providing the first damper stage, wherein a rivet is guided through a second rivet opening of the flange section, wherein the first damper part is arranged in a first position, wherein a riveting tool pushes the first damper part and the rivet in the direction of the shaft shoulder from the first position into a second position different from the first position, wherein in the second position the rivet rests against the shaft shoulder, wherein in the second position the rivet is riveted with the riveting tool. This configuration has the advantage that the rivet can be arranged concealed in the axial direction by the first damper part.

[0014] In a further embodiment, the clamping element of the axial positioning device is clamped during the movement from the first position to the second position, wherein upon release of the riveting tool, the clamping element moves the first damper part from the second position to the first position. Riveting and the production of the riveted connection can take place in the second position, wherein the first damper part or the second damper part is held in the first position by the axial positioning device during operation of the torsional vibration damper system. This prevents the riveted connection from touching the shaft shoulder during operation of the torsional vibration damper system.

[0015] In a further embodiment, the counterholder is arranged on the contact surface, wherein a riveting force acting in the axial direction toward the shaft shoulder is introduced into the rivet via the riveting tool, wherein a counterforce acting opposite to the riveting force is introduced into the rivet via the shaft shoulder by the counterholder, wherein the rivet is formed under the action of the riveting force and the counterforce to form the riveted connection. This configuration has the advantage that the riveting force can be supported and the rivet can be reliably formed by means of the counterforce, without causing mechanical damage, in particular mechanical deformation, of the first damper part and / or the flange section.

[0016] The invention is explained in more detail below with reference to the figures. These show: Fig. 1 a schematic representation of a drive train according to a first embodiment for a motor vehicle, Fig. 2 a section A of a half-longitudinal section through a structural design of the Fig. 1 shown drive train, Fig. 3 one in Fig. 2 marked section B of the Fig. 2 shown torsional vibration damper system, Fig. 4 a section A of a semi-longitudinal section through the Fig. 2 shown structural design of the Fig. 1 shown drive train after a second assembly step. Fig. 5 the in Fig. 4 shown section A during a fourth and fifth assembly step, Fig. 6 the in Fig. 4 shown section A during a sixth and seventh assembly step, Fig. 7 to 10 each in Fig. 2 marked section B of a torsional vibration damper system of a drive system according to a second to fifth embodiment, Fig. 11 shows a semi-longitudinal section through a section of a structural design of a drive train with a torsional vibration damper system according to a sixth embodiment, Fig. 12 one in Fig. 11 marked section C of a torsional vibration damper system of a drive train according to a seventh embodiment and Fig. 13 one in Fig. 11 marked section C of a torsional vibration damper system according to an eighth embodiment.

[0017] Fig. 1 shows a schematic representation of a drive train 10 according to a first embodiment for a motor vehicle.

[0018] In the schematic diagram, a torque transmission is schematically represented by straight lines. Rotating masses around a rotational axis 15 are represented by rectangular boxes.

[0019] The drive train 10 has a drive motor 20. The drive motor 20 is embodied, for example, as a hybrid drive motor and includes, for example, an internal combustion engine 25 and a first electric machine 30. Furthermore, the drive train 10 has a torsional vibration damper system 35, a clutch device 40, a second electric machine 45, a transmission device 50, and a drive train distribution system 55.

[0020] The torsional vibration damper system 35 has an input side 60, an output side 65, and at least one first damper stage 80. Additionally, the torsional vibration damper system 35 may have at least one second damper stage 75.

[0021] The first electric machine 30 has a first stator 85 and a first rotor 90. The second electric machine 45 has a second stator 95 and a second rotor 100. Both the first rotor 90 and the second rotor 100 are, for example, mounted for rotation about the rotational axis 15. The drive motor 20 and the second electric machine 45 are each configured to drive the motor vehicle via the transmission device 50 and the phase distribution 55 to propel the motor vehicle.

[0022] In the activated state, for example, the drive motor 20 provides a torque M acting about the rotational axis 15. The torque M is transmitted in order to propel the motor vehicle in the drive train 10 from the drive motor 20 to the train distribution 55 via the torsional vibration damper system 35 and the clutch device 40. The corresponding arrangement of the components 35, 40, 45, 50, 55 is specified below, each with respect to a torque flow of the torque M for driving the motor vehicle.

[0023] The torsional vibration damper system 35 is connected downstream of the drive motor 20. The input side 60 is connected in a rotationally fixed manner to the first rotor 90. The second damper stage 75 is arranged between the input side 60 and the first damper stage 80. The first damper stage 80 is arranged downstream of the second damper stage 75 with respect to the torque flow and is thus arranged between the second damper stage 75 and the output side 65. The two damper stages 80, 75 are each designed to absorb rotational irregularities that may be superimposed on the torque M. The rotational irregularities can be generated, for example, by the internal combustion engine 25.

[0024] The output side 65 is connected upstream of the clutch device 40. Furthermore, the clutch device 40 is connected upstream of the second electric machine 45. The clutch device 40 is switchable. When the clutch device 40 is closed, the clutch device 40 connects the output side 65 to the second rotor 100 in a torque-locking, preferably rotationally fixed, manner. When the clutch device 40 is open, torque transmission between the output side 65 and the second rotor 100 is interrupted. The transmission device 50 is arranged downstream of the second rotor 100 with respect to the torque flow of the torque M. Furthermore, the transmission device 50 is connected upstream of the phase distribution 55.

[0025] Fig. 2 shows a section A of a half-longitudinal section through a structural design of the Fig. 1 shown drive train 10.

[0026] The torsional vibration damper system 35 has a rotor shaft 105, a rotor carrier 110, and, for example, an output hub 115. The rotor shaft 105, the rotor carrier 110 connected to the rotor shaft 105, and the output hub 115 are mounted for rotation about the rotation axis 15. The first rotor 90 of the first electric machine 30 is attached to the outside of the rotor carrier 110. A crankshaft of the internal combustion engine 25 can be connected to the rotor shaft 105. The rotor shaft 105 and the rotor carrier 110 thus form the input side 60. The rotor carrier 110 delimits a receiving space 120, wherein the first and second damper stages 80, 75 are arranged in the receiving space 120, which is arranged substantially radially overlapping the first electric machine 30.In this case, a radial overlap is understood to mean that when two components, for example the receiving space 120 and the first electrical machine 30, are projected in the radial direction into a projection plane in which the axis of rotation 15 runs, the two components, for example the receiving space 120 and the first electrical machine 30, overlap.

[0027] The first damper stage 80 and the second damper stage 75 are connected in series, with the second damper stage 75 being connected upstream of the first damper stage 80. The second damper stage 75 is connected to the rotor carrier 110 on the input side in a rotationally fixed manner.

[0028] The first damper stage 80 has a first damper part 125. The first damper part 125 has a flange section 130, which in the embodiment is arranged, for example, radially on the inside of the first damper part 125. The flange section 130 extends substantially in a rotational plane perpendicular to the rotational axis 15. Furthermore, the first damper stage 80 can have a further first damper part 125, which is connected to the first damper part 125 in a rotationally fixed manner.

[0029] Furthermore, the first damper stage 80 has a first spring element 135 and a second damper part 140. The second damper part 140 and the first spring element 135 are arranged, for example, between the first damper part 125 and the further first damper part 125. The second damper part 140 is connected, for example, to the output hub 115 in a rotationally fixed manner. For this purpose, the second damper part 140 can be fastened to the output hub 115 by means of a welded connection 145. The first damper part 125 is rotatable relative to the second damper part 140 about the rotation axis 15 against the action of the first spring element 135, which is designed, for example, as a bow spring or helical spring.

[0030] The second damper part 140 has a flange connection 150, wherein the flange connection 150 extends substantially in a rotational plane perpendicular to the rotational axis 15. The flange section 130 is arranged at an axial distance from the flange connection 150. The flange section 130 is the component closest to the rotor shaft 105, starting from the flange connection 150. The flange section 130 and the flange connection 150 are arranged to axially overlap. Axial overlap is understood to mean that when two components are projected in the axial direction into a further projection plane arranged perpendicular to the rotational axis 15, the two components, for example the flange section 130 and the flange connection 150, overlap in the further projection plane.

[0031] A through-opening 155 is arranged in the flange connection 150. The through-opening 155 extends parallel to the rotation axis 15 completely through the flange connection 150. The through-opening 155 can be designed such that a riveting tool 270 (not shown in Fig. 2) through the through opening 155.

[0032] The first damper part 125 is coupled to the input side 60 of the torsional vibration damper system 35 via the flange section 130 and the second damper stage 75, which is arranged upstream of the first damper stage 80. The second damper stage 75 is configured similarly to the first damper stage 80. The second damper stage 75 has a third damper part 165, a second spring element 170, and a fourth damper part 175.

[0033] The third damper part 165 is non-rotatably connected to the rotor carrier 110 and thus non-rotatably connected via the rotor carrier 110 to both the rotor shaft 105 and the first rotor 90. The third damper part 165 is rotatable relative to the fourth damper part 175 about the rotation axis 15 against the action of the second spring element 170, which is designed, for example, as a bow spring or helical spring. The fourth damper part 175 is further non-rotatably connected to the flange portion 130 of the first damper stage 75 via a rivet connection 160.

[0034] If the torque M is provided by the drive motor 20, the torque M is transmitted from the rotor shaft 105 to the rotor carrier 110 to the third damper part 165. The torque M is transmitted from the third damper part 165 to the second spring element 170, which is compressed by the torque M. The second spring element 170 transmits the torque M to the fourth damper part 175. The fourth damper part 175 introduces the torque M into the flange section 130 of the first damper part 125 via the rivet connection 160. The first damper part 125 transmits the torque M to the first spring element 135, which is compressed by the torque M and transmits the torque M to the second damper part 140. The torque M is passed on from the second damper part 140 to the output hub 115 via the welded connection 145.The output hub 115 has the output side 65 of the torsional vibration damper system 35, via which the torque M is transmitted to the clutch device 40. The rotational irregularity is at least partially compensated for by the two spring elements 135, 170 during the transmission of the torque M from the input side 60 to the output side 65. As a result, the torque M provided at the output side 65 is smoother than the torque M provided at the input side 60, which is superimposed with the rotational irregularity.

[0035] In the unloaded state of the torsional vibration damper system 35, i.e., when the torsional vibration damper system 35 is not transmitting the torque M, the riveted joint 160 and the through-hole 155 overlap in the axial direction. In the unloaded state of the torsional vibration damper system 35, the arrangement of the riveted joint 160 relative to the through-hole 155 is such that the through-hole 155 and the riveted joint 160 are aligned and thus have no angular offset. Furthermore, the through-hole 155 and the riveted joint 160 are arranged to completely overlap in the axial direction.

[0036] Fig. 3 shows a Fig. 2 marked section B of the Fig. 2 shown torsional vibration damper system 35.

[0037] The rotor shaft 105 has a shaft section 180. The shaft section 180 can be stepped and extends substantially in the axial direction. The shaft section 180 can engage, for example, in sections with the output hub 115. The shaft section 180 has an outer circumferential side 185. Axially adjacent to the shaft section 180 is a shaft shoulder 190, which extends substantially in the radial direction and radially projects beyond the outer circumferential side 185 of the shaft section 180. Radially outwardly, the shaft shoulder 190 is connected to the rotor carrier 110, for example by means of a further welded connection, in a rotationally fixed manner to the rotor shaft 105.

[0038] On the shaft portion 180, the flange portion 130 and the fourth damper part 175 are axially movable between a first position (in Fig. 3) and a second position. Furthermore, the rotor shaft 105 is rotatable relative to the flange portion 130, the fourth damper part 175, and the output side 65.

[0039] In order to fix the first position of the flange section 130 and preferably of the fourth damper part 175 on the shaft section 180 in the axial direction, an axial positioning device 195 and a fastening means 200 are provided. In the embodiment, the axial positioning device 195 has at least one first positioning unit 205. In addition, the axial positioning device 195 can have a second, not Fig. 3 shown, positioning unit.

[0040] In this embodiment, the first positioning unit 205 has at least one first clamping element 210. Additionally, the first positioning unit 205 can have a second clamping element 215. In this embodiment, the clamping elements 210, 215 are designed, for example, as two disc springs arranged next to one another. Of course, it would also be conceivable for the first positioning unit 205 to be designed differently.

[0041] The first positioning unit 205 is, for example, in an axial gap 220 between the shaft shoulder 190 and, for example, the flange section 130, in Fig. 3, in particular axially between the fourth damper part 175 and the shaft shoulder 190. In addition, a receptacle 225 can be provided in the shaft shoulder 190, wherein the receptacle 225 is arranged on an end face of the shaft shoulder 190 facing the flange section 130 and is open on the side facing the flange section 130. The receptacle 225 radially adjoins the outer circumferential side 185 of the shaft section 180 in the circumferential direction. The receptacle 225 is shorter in the radial direction than the shaft shoulder 190. The receptacle 225 can be designed to extend annularly around the axis of rotation 15. The first positioning unit 205 engages, for example, at least partially in the receptacle 225.

[0042] The fastening means 200 is arranged on an axial side of the fourth damper part 175 facing away from the shaft shoulder 190. The fastening means 200 can, for example, comprise a retaining ring that engages in a retaining groove arranged in the shaft section 180.

[0043] The first positioning unit 205 secures the flange portion 130 and, for example, the fourth damper part 175 in the first position to the shaft portion 180, which axially extends through the flange portion 130 and the fourth damper part 175. It is particularly advantageous if the first clamping element 210 and preferably the second clamping element 215 are preloaded in the first position. Thus, the first clamping element 210 and the second clamping element 215 press the flange portion 130 and the fourth damper part 175 toward the fastening means 200. In the exemplary embodiment, the fourth damper part 175 rests axially opposite the first positioning unit 205 in the first position against the fastening means 200, so that the axial position of both the flange portion 130 and the fourth damper part 175 is fixed in the first position.

[0044] As already explained above, the flange section 130 is connected to the fourth damper part 175 in a rotationally fixed manner via the riveted connection 160. The flange section 130 and the fourth damper part 175 are rotatably mounted on the shaft section 180 relative to the shaft section 180, which extends through the fourth damper part 175 and the flange section 130. The through-opening 155 is wider in the radial direction than the riveted connection 160. Furthermore, the through-opening 155 is arranged in alignment with the riveted connection 160 in the first position and in the unloaded state of the torsional vibration damper system 35.

[0045] The shaft shoulder 190 has, on the end face, on the axial side facing the flange section 130, a support surface 230, which is, for example, annular and flat. The support surface 230 is aligned so as to axially overlap the through-opening 155 and the riveted connection 160. In the embodiment, the support surface 230 is arranged, for example, in a rotational plane perpendicular to the axis of rotation 15. The support surface 230 adjoins the receptacle 225 radially on the outside, for example. In the embodiment, the support surface 230 is, for example, radially wider than a maximum radial width of the riveted connection 160. The support surface 230 has at least the maximum radial width of the through-opening 155.

[0046] Axially opposite the support surface 230, a contact surface 235 is arranged on the shaft shoulder 190 on the axial side facing away from the flange section 130. The contact surface 235 preferably extends in a further rotational plane relative to the axis of rotation 15 and is thus preferably aligned parallel to the support surface 230. The contact surface 235 can be wider in the radial direction than the support surface 230. The contact surface 235 is also preferably flat. The contact surface 235 can be designed to extend annularly around the axis of rotation 15.

[0047] The support surface 230 and the contact surface 235 have an axial overlap with both the rivet connection 160 and the through opening 155.

[0048] Fig. 4 shows a section A of a semi-longitudinal section through the Fig. 2 shown structural design of the Fig. 1 shown drive train after a second assembly step. Fig. 5 shows the Fig. 4 shown section A during a fourth and fifth assembly step. Fig. 6 shows the Fig. 4 shown section A during a sixth and seventh assembly step.

[0049] In the first assembly step, the first damper stage 80 and the second damper stage 75 are pre-assembled separately from each other. Furthermore, in the first assembly step, the flange connection 150 is welded to the output hub 115 in a rotationally fixed manner, for example, to form the welded connection 145.

[0050] During assembly of the torsional vibration damper system 35 of the drive train 10, the torsional vibration damper system 35 is unloaded and not loaded with the torque M. Furthermore, the fourth damper part 175 is in the first position by the axial positioning device 195 and rests on the front side against the fastening means 200.

[0051] Furthermore, in the first assembly step, the second damper stage 75 is inserted into the receiving space 120, and a rivet 240 of the riveted connection 160 is pushed through a first rivet opening 245, which is arranged, for example, in the fourth damper part 175. A first rivet head 250 of the rivet 240 is positioned in the axial gap 220. The rivet 240 extends through the first rivet opening 245 with a rivet shank 255 and projects beyond the end face of the fourth damper part 175 in the axial direction. The first rivet head 250 is arranged axially overlapping the support surface 230.

[0052] In order to connect the first damper stage 80 with the output hub 115 to the second damper stage 75, a second rivet opening 260 arranged in the flange portion 130 and the through opening 155 are aligned with the rivet shaft 255.

[0053] In a second assembly step (not shown), the through-hole 155 and the second rivet opening 260 are aligned with the rivet shaft 255.

[0054] In a third assembly step (symbolically in Fig. 4), the first and second damper stages 80, 75 are assembled by an axial movement towards each other, wherein the rivet shaft 255, which protrudes from the first rivet opening 245, is inserted through the second rivet opening 260.

[0055] In a fourth assembly step (see Fig. 5), a riveting tool 270 is guided through the through-opening 155. In this case, the cross-section of the through-opening 155 can be adapted to an external geometry of the riveting tool 270 such that the through-opening 155 supports the riveting tool 270 as it is guided through in the axial direction parallel to the rotation axis 15. The riveting tool 270 can have a riveting punch 275 and a hold-down device 280. The hold-down device 280 can, for example, be shaped like a hollow body, in particular cylindrical. In the hold-down device 280, for example, Fig. 5, the riveting punch 275 is arranged to be axially displaceable. Furthermore, a counterholder 300 is attached to the contact surface 235 on the axial side of the shaft shoulder 190 opposite the riveting tool 270.

[0056] After the riveting tool 270 has been guided through the through-opening 155, the hold-down device 280 rests circumferentially with a first end face 285 against a second end face 290 of the flange portion 130. The hold-down device 280 engages around the rivet shank 255 protruding from the second rivet opening 260, with a radial gap preferably being provided between the rivet shank 255 and an inner circumferential contour of the hold-down device 280. The riveting punch 275 is arranged at a distance from a rivet surface 295, which is arranged on the axial side facing the rivet shank 255, in the fourth assembly step. This ensures that the rivet shank 255 protruding from the flange portion 130 is completely encompassed by the hold-down device 280.

[0057] In a fifth assembly step, the hold-down device 280 is actuated with an actuating force F (in Fig. 5). The actuating force F acts in the axial direction and presses against the front side of the flange section 130 in the direction of the shaft shoulder 190. The actuating force F is greater than the preload of the clamping element 210, 215. By means of the actuating force F and against the action of the axial positioning device 195, in particular the first and second clamping elements 210, 215, the flange section 130 and the rivet 240, together with the fourth damper part 175, are moved from the first position into a second position along the axis of rotation 15 in the direction of the shaft shoulder 190. When the second position is reached, the first rivet head 250 rests against the support surface 230.

[0058] In a sixth procedural step following the fifth procedural step (cf. Fig. 6) a riveting force F N introduced into the riveting die 275. With the riveting force F NOn the one hand, the riveting punch 275 is moved towards the rivet shaft 255, on the other hand, the riveting force F N the rivet punch 275 onto the rivet shaft 255. The hold-down device 280 continues to act with the actuating force F on the flange section 130 and the fourth damper part 175. The hold-down device 280 secures the first and second damper stages 80, 75, in particular the rivet 240, the flange section 130 and the fourth damper part 175, in the second position on the shaft shoulder 190. The counter-holder 300 provides a counter-force F G ready, whereby the counterforce F G essentially a sum of the riveting force F N and the actuating force F. The counterforce F G is introduced into the contact surface 235 via the counterholder 300 and acts opposite to the riveting force F N and the actuating force F.

[0059] With the riveting force F NOn the side of the flange portion 130 facing away from the shaft shoulder 190, a second rivet head 305 is plastically formed from the rivet shaft 255 by the rivet punch 275. A radial configuration of the second rivet head 305 is determined by a geometric configuration of the hold-down device 280 in the embodiment.

[0060] It should be noted that the hold-down device 280 could, of course, also be dispensed with. In this case, the geometric design of the second rivet head 305 is determined by the riveting process and the riveting punch 275. In this case, the riveting punch 275 pushes with the riveting force F N the flange portion 130 and the rivet 240 together with the fourth damper part 175 into the second position.

[0061] During riveting, the counterforce F G, which is provided by the counterholder 300, ensures the axial position of the rotor shaft 105 and prevents unwanted yielding of the rotor shaft 105, in particular of the shaft shoulder 190. Furthermore, the counterholder 300 can prevent mechanical damage to the rotor shaft 105, in particular of the shaft shoulder 190.

[0062] By arranging the axial positioning device 195 in the receptacle 225, overpressure of the clamping element 210, 215 and thus mechanical damage to the clamping element 210, 215 can be avoided.

[0063] In a seventh assembly step following the sixth assembly step, the riveting tool 270 is withdrawn in the axial direction after the riveting of the riveted joint 160 has been completed. Likewise, the counterholder 300 is removed (in Fig. 6 symbolically represented by dashed arrows). By relieving the load on the flange section 130 and the fourth damper part 175, the tensioned clamping element 210, 215 of the axial positioning device 195 presses the flange section 130 and the fourth damper part 175 from the second position back into the first position.

[0064] This completes the connection between the first damper stage 80 and the second damper stage 75.

[0065] The axial positioning device 195 holds the flange portion 130 and the fourth damper part 175, and thus the first and second damper stages 80, 75, in the first position during operation of the torsional vibration damper system 35. Furthermore, an axial force can be supported on the shaft shoulder 190 via the axial positioning device 195.

[0066] Fig. 7 shows the Fig. 2 marked section B of a torsional vibration damper system 35 of a drive system 10 according to a second embodiment.

[0067] The drive train 10 is essentially identical to that shown in the Fig. 1 to 6. In the following, only the differences of the drive train 10 shown in Fig. 7 shown drive train 10 compared to the one shown in the Fig. The structural design of the drive train 10 shown in Figures 2 to 6 will be discussed.

[0068] In Fig. 7, the second clamping element 215 is omitted. The first clamping element 210, which in the embodiment is designed as a disc spring, is connected via the rivet connection 160 in a rotationally fixed manner to the fourth damper part 175 and to the flange section 130. In the embodiment, the Fig. 4 to 6, the first clamping element 210 is additionally riveted to the flange section 130.

[0069] Fig. 8 shows the Fig. 2 marked section B of a torsional vibration damper system 35 of a drive system 10 according to a third embodiment.

[0070] The drive train 10 is essentially identical to that shown in the Fig. 1 to 6. In the following, only the differences of the drive train 10 shown in Fig. 8 shown drive train 10 compared to the one shown in the Fig. The structural design of the drive train 10 shown in Figures 2 to 6 will be discussed.

[0071] In Fig. 8, the second clamping element 215 is omitted for example. The first clamping element 210 is additionally connected to the flange portion 130 and, for example, to the fourth damper part 175 via an additional rivet connection 310. For example, the additional rivet connection 310 is arranged radially outwardly of the rivet connection 160.

[0072] Fig. 9 shows the Fig. 2 marked section B of a torsional vibration damper system 35 according to a fourth embodiment.

[0073] The drive train 10 is essentially identical to that shown in the Fig. 1 to 6. In the following, only the differences of the drive train 10 shown in Fig. 9 shown drive train 10 compared to the one shown in the Fig. The structural design of the drive train 10 shown in Figures 2 to 6 will be discussed.

[0074] Instead of the Fig. 2 to 6, the axial positioning device 195 has a friction control disk 315 in addition to the first clamping element 210. The friction control disk 315 is arranged axially adjacent, for example, to the fourth damper part 175 between the first clamping element 210 and the fourth damper part 175 and thus to the flange section 130. Thus, for example, the friction control disk 315 is arranged axially on a side of the axial positioning device 195 facing away from the shaft shoulder 190. The first clamping element 210 is arranged axially on the side facing the shaft shoulder 190. The second clamping element 215 is omitted in this embodiment, for example. The friction control disk 315 has the advantage that it serves as a type of plain bearing relative to the first clamping element 210, thus preventing wear on the first clamping element 210.Furthermore, in the embodiment, the first clamping element 210 is made of an elastomer and has, for example, an annular configuration.

[0075] Fig. 10 shows the Fig. 2 marked section B of a torsional vibration damper system 35 according to a fifth embodiment.

[0076] The drive train 10 is essentially identical to that shown in the Fig. 1 to 6. In the following, only the differences of the drive train 10 shown in Fig. 10 shown drive train 10 compared to the one shown in the Fig. The structural design of the drive train 10 shown in Figures 2 to 6 will be discussed.

[0077] In the embodiment, the second clamping element 215 is omitted for the axial positioning device 195. The first clamping element 210 is designed in the embodiment as a helical spring, which extends, for example, between the fourth damper part 175 (and the flange portion 130 attached to the fourth damper part 175) and the shaft shoulder 190.

[0078] Fig. 11 shows a semi-longitudinal section through a section of a structural design of a drive train 10 with a torsional vibration damper system 35 according to a sixth embodiment.

[0079] The drive train 10 is essentially identical to that shown in the Fig. 1 to 6. In the following, only the differences of the drive train 10 shown in Fig. 10 shown drive train 10 compared to the one shown in the Fig. The structural design of the drive train 10 shown in Figures 2 to 6 will be discussed.

[0080] In this embodiment, the second damper stage 75 is omitted, so that, for example, the torsional vibration damper system 35 is only designed as a single stage. Furthermore, the arrangement of the first and second damper parts 125, 140 is interchanged. Fig. 11, the first damper part 125 is arranged axially between two second damper parts 140. Furthermore, in the embodiment, the flange section 130 of the first damper part 125 is connected to the disk carrier 320 in a rotationally fixed manner via the rivet connection 160. The flange connection 150 of the second damper part 140 is connected to the output hub 115 in the embodiment with a disk carrier 320 of the clutch device 40. The disk carrier 320 is arranged radially inwardly to a friction pack 325 of the clutch device 40. The disk carrier 320 is connected to the flange section 130 in a rotationally fixed manner via the rivet connection 160. The axial positioning device 195 thus secures an axial position of the flange section 130 on the rotor shaft 105 in the embodiment. The axial positioning device 195 can, as in the Fig. 2 to 10. In the embodiment, only the first clamping element 210 is provided, which presses the flange portion 130 of the first damper part 125 toward the fastening means 200 in order to hold the flange portion 130 in the first position during operation of the torsional vibration damper system 35.

[0081] The passage opening 155 is in Fig. 11 in the first damper part 125 is arranged radially outward in the flange portion 130. The through-opening 155 is arranged substantially radially outward relative to a toothed portion 335 of the disk carrier 320 extending parallel to the rotational axis 15. The through-opening 155 can have an axial overlap with an external toothing 340 of the toothed portion 335.

[0082] The flange connection 150 of the second damper part 140 is connected to the rotor carrier 110 by means of a further rivet connection 330. The further rivet connection 330 is arranged axially overlapping the through-opening 155. As already described in Fig. 2 to 6, the riveting tool 270 is used to create the further rivet connection 330 and thus to connect the flange connection 150 of the second damper part 140 in a rotationally fixed manner to the rotor carrier 110. In this case, the counterholder 300 is placed on the side of the rotor carrier 110 facing away from the first damper stage 80.

[0083] In addition, the Fig. 2 to 6 can also be used to form the rivet connection 160. The only difference to the assembly method described in the Fig. 2 to 6 described method for riveting the riveted joint 160 is to rivet the riveted joint 160 in Fig. 11 in such a way that the riveting tool 270 for producing the riveted connection 160 does not have to be passed through the through-opening 155. Likewise, when producing the riveted connection 160, the counterholder 300 is placed on the side of the shaft shoulder 190 facing away from the riveted connection 160, and both the hold-down device 280 and the riveting punch 275 are placed on the end face, on the side facing away from the shaft shoulder 190, on a further flange section 345 of the disk carrier 320 extending essentially in a plane of rotation. By moving both the flange section 130 and the further flange section 345 from the first position to the second position, the riveted connection 160 can be formed in a simple manner.After the rivet connection 160 has been produced, the axial positioning device 195 and, in the embodiment, the first clamping element 210, for example, presses the flange connection 150 and thus the second damper part 140 together with the plate carrier 320 back into the first position.

[0084] In addition, Fig. 11, the receptacle 225 in the shaft shoulder 190 is omitted, so that the support surface 230 extends radially inward, for example, to the outer circumferential side 185.

[0085] Fig. 12 shows one in Fig. 11 marked section C of a torsional vibration damper system 35 of a drive train 10 according to a seventh embodiment.

[0086] The torsional vibration damper system 35 is essentially identical to that in Fig. 11 is designed according to the sixth embodiment. In addition, the first clamping element 210 is rotationally fixedly secured to the flange connection 150 by means of the further rivet connection 330.

[0087] Fig. 13 shows one in Fig. 11 marked section C of a torsional vibration damper system 35 of a drive train according to an eighth embodiment.

[0088] The torsional vibration damper system 35 is essentially identical to that in Fig. 11 shown drive beach 10. In the following, only the differences of the Fig. 13 shown drive train 10 according to the eighth embodiment compared to the one in Fig. 11 shown drive train 10 according to the sixth embodiment.

[0089] In Fig.13, the first clamping element 210, which is designed as a disc spring, for example, has a clearance 350 on the further rivet connection 330, so that when the flange connection 150 is moved between the first position and the second position in which the further rivet connection 330 is produced, overpressing of the first clamping element 210 during riveting can be avoided. List of reference symbols 10 Drivetrain 15 axis of rotation 20 drive motor 25 internal combustion engine 30 first electric machine 35 Torsional vibration damper system 40 Coupling device 45 second electric machine 50 translation facilities 55 Strand distribution 60 Entrance page 65 Exit page 75 second damper stage 80 first damper stage 85 first stator 90 first rotor 95 second stator 100 second rotor 105 Rotor shaft 110 rotor carrier 115 Output hub 120 recording room 125 first damper part 130 flange section 135 first spring element 140 second damper part 145 Welded joint 150 flange connection 155 passage opening 160 riveted joint 165 third damper part 170 second spring element 175 fourth damper part 180 wave section 185 outer circumference 190 wave heel 195 Axial positioning device 200 fasteners 205 first positioning unit 210 first clamping element 215 second clamping element 220 axial gap 225 recording 230 support area 235 contact area 240 rivets 245 first rivet opening 250 first rivet head 255 rivet shank 260 second rivet opening 270 riveting tool 275 riveting dies 280 hold-down clamps 285 first front side 290 second front side 295 rivet surface 300 counterholders 305 second rivet head 310 Additional rivet connection 315 friction control disc 320 slat carriers 325 friction package 330 additional rivet connections 335 Gear section 340 external gearing 345 additional flange section 350 exemption F Actuating force F G Counterforce F N Riveting force M torque

Claims

[1] Torsional vibration damper system (35) for a drive train (10) of a motor vehicle, - wherein the torsional vibration damper system (35) has a first damper stage (80) and a rotor shaft (105), - wherein the first damper stage (80) comprises a first damper part (125) rotatably mounted about a rotation axis (15) with a flange portion (130) to which a rivet connection (160) is fastened, - wherein the rotor shaft (105) has a shaft shoulder (190) extending outwards in the radial direction, - wherein the shaft shoulder (190) has an axial overlap with the rivet connection (160), - wherein the shaft shoulder (190) has a support surface (230) for riveting the riveted connection (160) on an axial side facing the riveted connection (160). [2] Torsional vibration damper system (35) according to claim 1, - wherein the first damper stage (80) comprises a first spring element (135) and a second damper part (140), - wherein the first damper part (125) is rotatable against the action of the first spring element (135) about the axis of rotation (15) relative to the second damper part (140), - wherein the rotor shaft (105) has a shaft section (180) which adjoins the shaft shoulder (190), - wherein the first damper part (125) and / or second damper part (140) is arranged on the shaft section (180) so as to be rotatable relative to the rotor shaft (105), - wherein an axial positioning device (195) with at least one clamping element (210, 215) is arranged on the shaft section (180) for the axial positioning of the first damper part (125) or the second damper part (140), - wherein the axial positioning device (195) is arranged axially between the first damper part (125) and / or the second damper part (140) and the shaft shoulder (190), - wherein the first damper part (125) and / or the second damper part (140) is arranged to be displaceable from a first position against the action of the clamping element (210, 215) of the axial positioning device (195) in the direction of the shaft shoulder (190) into a second position different from the first position. [3] Torsional vibration damper system (35) according to claim 1 or 2, - having an input side (60) and an output side (65), - wherein a torque (M) subjected to rotational irregularity can be introduced into the torsional vibration damper system (35) via the input side (60), - wherein the first damper stage (80) is connected downstream of the input side (60) with respect to a torque flow of the torque (M) of the input side (60) to the output side (65) and is designed to eliminate the rotational irregularity, - wherein the output side (65) is arranged on the flange section (130), - wherein the flange portion (130) can be connected in a rotationally fixed manner to a plate carrier (320) of a coupling device (40) by means of the rivet connection (160). [4] Torsional vibration damper system (35) according to claim 1 or 2, - comprising a second damper stage (75) and an input side (60), - wherein a torque (M) subjected to rotational irregularity can be introduced into the torsional vibration damper system (35) via the input side (60), - wherein, with respect to a torque flow of the torque (M) that can be provided on the input side (60), the second damper stage (75) is arranged between the input side (60) and the first damper stage (80), - wherein the second damper stage (75) has a third damper part (165) rotatably mounted about a rotational axis (15), a second spring element (170) and a fourth damper part (175) for at least partially eliminating the rotational irregularity, - wherein the rivet connection (160) connects the fourth damper part (175) to the flange section (130) in a rotationally fixed manner, - wherein the third damper part (165) is rotatable about the rotation axis (15) relative to the fourth damper part (175) against the action of the second spring element (170). [5] Torsional vibration damper system (35) according to one of the preceding claims, - wherein the riveted connection (160) has a rivet (240) extending in the axial direction, - wherein the rivet (240) passes through a second rivet opening (260) of the flange portion (130), - wherein a second rivet head (305) of the rivet connection (160) is formed on a side of the rivet (240) facing away from the shaft shoulder (190), - wherein the second rivet head (305) fastens the flange portion (130). [6] Torsional vibration damper system (35) according to one of the preceding claims, - wherein the shaft shoulder (190) has, on an axial side facing away from the riveted connection (160), a contact surface (235) for the contact of a counter-holder (300). [7] Torsional vibration damper system (35) according to one of the preceding claims, - wherein the second damper part (140) has a flange connection (150) with a through opening (155), - wherein the through-opening (155) in the flange connection (150) and the rivet connection (160) are arranged to overlap axially. [8] Method for producing a torsional vibration damper system (35) according to one of the preceding claims, - wherein the first damper stage (80) is provided, - wherein a rivet (240) is guided through a second rivet opening (260) of the flange portion (130), - wherein the first damper part (125) is arranged in a first position, - wherein a riveting tool (270) pushes the first damper part (125) and the rivet (240) in the direction of the shaft shoulder (190) from the first position into a second position different from the first position, - wherein in the second position the rivet (240) rests against the shaft shoulder (190), - wherein in the second position the rivet (240) is riveted with the riveting tool (270). [9] Method according to claim 8 for producing a torsional vibration damper system (35) according to claim 2, - wherein in the movement from the first position to the second position the clamping element (210, 215) of the axial positioning device (195) is clamped, - wherein when the riveting tool (270) is released, the clamping element (210, 215) moves the first damper part (125) from the second position to the first position. [10] Method according to claim 8 or 9 for producing a torsional vibration damper system (35) according to claim 6 and 7, - wherein the counterholder (300) is arranged on the contact surface (235), - wherein a riveting force (F N ) is introduced into the rivet (240), - whereby the counterholder (300) generates a force corresponding to the riveting force (F N ) opposing counterforce (F G ) is introduced into the rivet (240) via the shaft shoulder (190), - wherein the rivet (240) is driven by the riveting force (F N) and the counterforce (F G ) is formed into the riveted connection (160).

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