Hybrid module with a speed-adaptive torsional vibration damper

Abstract

Hybrid module (100, 200, 300, 400, 500, 600, 700, 800, 900) with an electric machine (101, 901) arranged about an axis of rotation (d) with a fixed stator (102) and a rotor (103, 903) arranged rotatably relative to the stator about the axis of rotation (d), which rotor is accommodated on an axial extension (105, 205, 305, 405, 605, 705, 805, 905) of a rotor carrier (104, 204, 304, 504, 604, 704, 804, 904), wherein radially inside the extension (105, 205, 305, 605, 705, 805, 905) Torsional vibration isolation device (109) is arranged, wherein the rotor carrier (104, 204, 304, 504, 604, 704, 804, 904) directly forms an output (107) of the hybrid module (100, 200, 300, 400, 500, 600, 700, 800, 900) and the torsional vibration isolation device (109) is used exclusively as a torsional vibration damper (110, 110a, 110b, 110c, 110d, 110e, 110f) with a carrier part (112, 112a, 112b, 112c, 112d, 112e, 112f, 212, 512, 612, 712, 812,912) and pivotable damper masses (113, 113a, 113b, 113c, 113d, 113e, 113f, 513) are formed thereon, wherein the carrier part (612) is formed from two side parts (114, 114d, 214, 314, 414, 514, 614, 714, 814, 914, 115, 115d, 515) which are connected to one another at an axial distance and which receive damper masses (113, 113d, 513) which are arranged between them and distributed over the circumference and which are pivotably mounted on the side parts (114, 114d, 214, 314, 414, 514, 614, 714, 814, 914, 115, 115d, 515), wherein at least one side part (114, 114d, 214, 314, 414, 614, 714, 814, 914, 115d, 515) extends radially beyond the extension (605) of the rotor carrier and is connected to the rotor carrier (104, 204, 304, 504, 604, 704, 804, 904), wherein the axial extension (605) has a plurality of rivet pins (626) distributed over the circumference at its end,which extend into openings of the side part (614) of the support part (612) which extends radially beyond the shoulder (605) and are formed on the opposite side with rivet heads (627).

Description

[0001] The invention relates to a hybrid module with an electric machine arranged about an axis of rotation with a fixed stator and a rotor arranged rotatably relative to the stator about the axis of rotation, which rotor is received on an axial extension of a rotor carrier, wherein a torsional vibration isolation device is accommodated radially within the extension.

[0002] Hybrid modules are used between an internal combustion engine and the drive wheels of a motor vehicle's hybrid drive train to provide hybrid propulsion with purely electric driving, boosting, recuperation, and the like. For this purpose, the hybrid module contains an electric motor and, if appropriate, additional devices radially within the rotor to utilize the radial installation space radially within the rotor. For example, a generic hybrid module is known from the publication DE 10 2018 106 285 A1, in which a separating clutch and a torsional vibration isolation device formed by a torsional vibration damper are housed radially within the rotor. The torsional vibration damper is connected in the torque path between the rotor of the electric motor and an output of the hybrid module.

[0003] The object of the invention is to further develop a hybrid module. In particular, the object of the invention is to propose a hybrid module with a torsional vibration isolation device with reduced torsional elasticity.

[0004] The problem is solved by the subject matter of claim 1.

[0005] The proposed hybrid module, in conjunction with an internal combustion engine, serves to provide a hybrid drive for a hybrid powertrain of a motor vehicle. For this purpose, the hybrid module contains an electric motor arranged around a rotational axis, with a stationary stator and a rotor arranged relative to the stator so as to be rotatable about the rotational axis. The stator can, for example, be housed in a housing that is firmly connected to a housing of the internal combustion engine or, for example, to a housing of a transmission connected downstream of the hybrid module.

[0006] The rotor is rotatable relative to the stator, forming a predetermined air gap, and is axially fixed. For this purpose, a rotor carrier is provided, which is constantly mounted relative to the stator and has an axial extension on which the rotor is mounted radially outward. A torsional vibration isolation device is arranged radially inside the axial extension and thus radially inside the rotor to save axial installation space and utilize the installation space radially inside the rotor.

[0007] To enable torsional elasticity within the hybrid module, i.e., between the rotor and an output of the hybrid module, the rotor carrier directly forms the output of the hybrid module, and the torsional vibration isolation device is designed exclusively as a torsional vibration damper with a support part rotating with the rotor carrier and damper masses pivotable on this depending on centrifugal force. By designing the rotor carrier as an output, for example by means of a hub or sleeve with internal gearing, a torsionally rigid connection of the rotor to a shaft section, for example a transmission input shaft, a shaft journal of a dual clutch, or the like, can be formed. Nevertheless, torsional vibration isolation of torsional vibrations, for example of the internal combustion engine, is possible in that the torsional vibration damper, which is not connected to the torque flow, provides a corresponding damper torque that counteracts the torsional vibrations.

[0008] In the simplest case, the torsional vibration damper can be designed as a mass damper with absorber masses elastically coupled to the support part of the torsional vibration damper by means of spring elements. In order to provide speed-adaptive torsional vibration damping, the absorber masses can be designed to pivot depending on centrifugal force. For example, a centrifugal pendulum can be provided for this purpose. For example, a support part mounted on the rotor arm can be arranged as a pendulum flange with absorber masses arranged on both sides and distributed over the circumference. The absorber masses are mounted on the support part in a pendulum-like manner by means of self-aligning bearings. Axially opposite absorber masses are each connected to one another to form a pendulum mass unit. Recesses with raceways in the pendulum flange and in the absorber masses, as well as spherical rollers rolling on the axially opposite raceways, determine the raceway of the absorber masses in the centrifugal force field.

[0009] Alternatively, the self-aligning bearings can be arranged between the center sections connecting the axially opposite damper masses and the pendulum flange. The raceways of the center sections and the pendulum flange are arranged radially one above the other and in the same plane. The center sections are accommodated in recesses in the pendulum flange, with shoulders intersecting the raceways and the corresponding raceways in areas of the center sections in the circumferential direction.

[0010] The pendulum mass units can be constructed as a single piece and beveled to form center sections and damper masses. The pendulum mass units can have additional masses radially on the outside.

[0011] In one embodiment of a speed-adaptive torsional vibration damper according to the invention, the support member can be formed from two axially spaced-apart side parts, which accommodate damper masses distributed over the circumference between them. The damper masses are suspended from the side parts by means of self-aligning bearings in a pendulum-like manner, with at least one side part being connected to the rotor carrier. The damper masses can contain additional masses radially on the outside, which axially overlap the outer circumferences or recesses of the side parts.

[0012] The damper masses arranged around the circumference can be preloaded in the circumferential direction, for example, by means of spring elements. For example, helical compression springs can be preloaded at the ends of the damper masses adjacent in the circumferential direction.

[0013] In a further embodiment of a speed-adaptive torsional vibration damper, at least one damper ring can be arranged coaxially with the carrier part, with damper masses being arranged between the carrier part and the at least one damper ring and distributed over the circumference. The damper masses have recesses with raceways on one side to form self-aligning bearings and a rotary connection such as a swivel joint on the side spaced apart from this in the circumferential direction. For the limited rotatable connection of the at least one damper ring to the carrier part, the damper masses are each connected to the carrier part or to the at least one damper ring by means of a self-aligning bearing and to the at least one damper ring or to the carrier part by means of the rotary connection. As a result, in the centrifugal force field of the rotating carrier part, in the presence of torsional vibrations, a pendulum movement of the damper masses occurs, which changes the moment of inertia of the at least one damper ring.

[0014] The torsional vibration damper is connected to the rotor arm by its support member. For example, the support member can be screwed, riveted, latched, welded, and / or caulked to the rotor arm. It has been shown that caulking the support member to the rotor arm can reduce manufacturing costs and reduce axial space requirements due to the generally soft rotor arm and the harder support member.

[0015] For example, caulking can be carried out on the axial shoulder that holds the rotor relative to the support part.

[0016] For example, a fastening, such as caulking, riveting, screwing, welding, and / or the like, can be provided radially within the damper masses on the rotor carrier. For example, a caulking or welding can be formed radially within the damper masses on an axial shoulder, for example, a cup of the rotor carrier.

[0017] For example, caulking of the support part in the rotor carrier can be formed in the axial and / or radial direction. In the case of radial caulking, the outer circumference can have a profile, for example at least a depression or notch, into which material of the rotor carrier is displaced to ensure that the support part is secured against rotation. Alternatively, an anti-rotation feature can be provided by the inner circumference of the rotor carrier and the outer circumference of the support part having a complementary radial profile. To form the caulking, recesses can be provided in the rotor carrier to counteract the material displacement.

[0018] Furthermore, with radial caulking of the support part, an anti-rotation lock and / or axial locking in at least one direction can be provided by means of another means. For example, the support part can be placed against an axial stop of the rotor carrier and caulked against it. Alternatively, axial locking can be provided by means of a retaining ring, a pressed-in ring, a weld, a retaining ring preloading the support part, or the like.

[0019] The invention is described in the Fig. 1 to 17 are explained in more detail. These show: Fig. 1 the upper part of a hybrid module arranged around a rotation axis in a schematic sectional view, Fig. 2 the rotor carrier of the hybrid module of the Fig. 1 in view, Fig. 3 the rotor carrier of the Fig. 1 and Fig. 2 in 3D view, Fig. 4 the upper part of a hybrid module of the Fig. 1 modified hybrid module in schematic sectional view, Fig. 5 the upper part of a hybrid module of the Fig. 1 and Fig. 4 modified hybrid module in schematic sectional view, Fig. 6 the upper part of a hybrid module of the Fig. 1, Fig. 4 and Fig. 5 modified hybrid module in schematic sectional view, Fig. 7 the upper part of a hybrid module of the Fig. 1 and 4 to 6 modified hybrid module in schematic sectional view, Fig. 8 the upper part of a hybrid module of the Fig. 1 and 4 to 7 modified hybrid module in schematic sectional view, Fig. 9 the upper part of a hybrid module of the Fig. 1 and 4 to 8 modified hybrid module in schematic sectional view, Fig. 10 the upper part of a hybrid module of the Fig. 1 and 4 to 9 modified hybrid module in schematic sectional view, Fig. 11 the upper part of a hybrid module of the Fig. 1 and 4 to 10 modified hybrid module in schematic sectional view, Fig. 12 the upper part of a instead of the torsional vibration damper of the Fig. 1 and 4 to 11 of the torsional vibration damper that can be used in the hybrid modules in a schematic sectional view, Fig. 13 the upper part of a instead of the torsional vibration damper of the Fig. 1 and 4 to 12 usable torsional vibration damper in schematic sectional view, Fig. 14 the upper part of a instead of the torsional vibration damper of the Fig. 1 and 4 to 13 usable torsional vibration damper in schematic sectional view, Fig. 15 the upper part of a instead of the torsional vibration damper of the Fig. 1 and 4 to 14 usable torsional vibration damper in schematic sectional view, Fig. 16 a schematic functional representation of a torsional vibration damper instead of the Fig. 1 and 4 to 15 usable torsional vibration dampers and Fig. 17 a view of a torsional vibration damper instead of the Fig. 1 and 4 to 16 usable torsional vibration dampers.

[0020] The Fig. 1 shows a schematic sectional view of the upper part of the hybrid module 100 arranged around the rotational axis d. The hybrid module 100 contains the electric machine 101 with the stator 102 and the rotor 103, which can be rotated relative to the stator. The rotor 103 is fixedly mounted on the axial projection 105, for example, a molded-on grommet of the rotor carrier 104. The stator 102 is fixedly attached to a housing of the internal combustion engine connected upstream of the hybrid module 100 or to a transmission connected downstream of the hybrid module. The rotor 103 is rotatable relative to the stator 102, for example by means of the rotor carrier 104 while setting a defined air gap 106, and is axially fixed relative to the stator 102, for example by mounting the rotor carrier 104 on the same housing or on a bearing flange of a housing accommodating the stator 102.

[0021] In addition to a connection to the crankshaft of the internal combustion engine, optionally with the interposition of a torsional vibration damper such as a dual-mass flywheel and / or a separating clutch arranged, for example, radially inside the extension 105 and axially adjacent to the torsional vibration isolation device 109, the rotor carrier 104 directly forms the torsionally rigid output 107 of the hybrid module 100. For this purpose, openings 108 are provided radially inside the rotor carrier 104 distributed over the circumference, by means of which the rotor carrier 104 is connected, for example riveted, to an output flange (not shown), which is connected in a rotationally fixed manner to a shaft section of the transmission and optionally to a drive part of the internal combustion engine by means of a toothing such as internal toothing. Alternatively, the rotor carrier 104 itself can form the toothing directly or by means of a hub.

[0022] The torsional vibration isolation device 109 is arranged within the axial and radial installation space of the extension 105 and is designed as a torsional vibration damper 110 to form a torsionally rigid transmission of the torque from the rotor 103 to the output 107. The torsional vibration damper 110 is not effectively arranged in the torque path between the rotor 103 and the output 107 and is nevertheless effective with regard to isolating torsional vibrations.

[0023] In the illustrated embodiment, the torsional vibration damper 110 is designed as a centrifugal pendulum 111 with the support part 112 and the damper masses 113 arranged distributed over the circumference. The support part 112 is divided into the two axially spaced side parts 114, 115, which are connected to one another, for example, by means of spacer bolts arranged between the damper masses 113, and which axially accommodate the damper masses 113 between them. The damper masses 113 are accommodated in a pendulum-like manner in the centrifugal force field of the support part 112 rotating about the rotational axis d, along a pendulum path defined by the pendulum bearings, for example, by means of self-aligning bearings arranged circumferentially between the spacer bolts and not visible. The self-aligning bearings are formed from axially opposite recesses with curved raceways in the side parts 114, 115 and the damper masses 113, with a self-aligning roller axially penetrating the recesses and rolling on the raceways.

[0024] The support part 112 of the centrifugal pendulum 111 is connected to the rotor carrier 104. In the exemplary embodiment shown, the side part 114 of the support part 112 is fastened radially outwardly to the axial extension 105 of the rotor carrier 104 by means of caulking 116 distributed over the circumference. The caulking takes place without significantly impairing the side part 114, since the side part 114 is heat-treated, for example, due to the hard design of the raceways of the self-aligning bearings, and therefore the rotor carrier 104 is softer than the side part 114. To accommodate the side part 114 flatly on the inner circumference of the extension 105, the outer circumference of the side part 114 is folded over, whereby the axial extension 117 formed thereby forms a contact surface with the inner circumference of the extension 105 and is pressed against the axial stop 118. The caulkings 116 can radially overlap the projection 117 and form an axial securing means for the side part 114.The side part 114 is secured against rotation relative to the rotor carrier 104 by providing corresponding recesses at the caulkings 116 in the side part 114. To axially secure the side part 114 to the axial stop 118, additional caulkings radially covering the side part 114 can be provided as an alternative to the caulkings 116.

[0025] The openings 119 arranged around the circumference serve to counter-hold the rotor carrier 104 during the formation of the caulkings 116, in that corresponding counter-holders engage in the openings and counteract the resulting axial forces.

[0026] The Fig. 2 shows with reference to Fig. 1 shows a view of the rotor carrier 104 of the hybrid module 100, arranged around the rotational axis d, with the caulked carrier part 112 of the torsional vibration isolation device 109. The axial extension 105 of the rotor carrier 104 has the caulkings 116, which are radially displaced into the recesses 120 of the side part 114 of the carrier part 112, thus preventing the carrier part 112 from rotating relative to the rotor carrier 104. The openings 108 formed in the rotor carrier 104 form both the input and output of the hybrid module and are correspondingly connected to an output flange and a drive component, for example, to an output part of a torsional vibration damper.

[0027] The Fig. 3 shows with reference to the Fig. 1 and Fig. 2 shows the rotor carrier 104 in 3D view. The rotor 103 is mounted radially outward on the axial projection 105, and the torsional vibration isolation device 109 is mounted radially inward. The openings 119 serve to counter-hold the rotor carrier 104 during the caulking of the side part 114 to the rotor carrier 104 and, for this purpose, have the force application surfaces 121. The openings 108 serve for the drive and output of the hybrid module 100.

[0028] The Fig. 4 shows the upper part of the hybrid module 100 arranged around the rotation axis d, Fig. 1 modified hybrid module 200 in a schematic sectional view. In contrast to the hybrid module 100, the side part 214 of the support part 212, which rests against the axial stop 218 of the extension 205 of the rotor support 204, is axially secured by means of the weld 216, for example, by means of weld points 222 distributed over the circumference. As an additional anti-rotation device of the support part 212 relative to the rotor support 204, a circumferentially effective profiling can be provided between the axial extension 217 of the side part 214 and the axial extension 205.

[0029] The Fig. Figure 5 shows the upper part of the hybrid module 300 arranged around the rotation axis d in a schematic sectional view. In contrast to the hybrid module 200 of Fig. 4, the side part 314 pressed into the shoulder 305 of the rotor carrier 304 is designed without a shoulder and is axially secured against the axial stop 318 by means of the additional pressed-in annular part 316. Alternatively, an annular groove can be introduced into the shoulder 305, and a retaining ring can be inserted into this groove to secure the side part, which can be designed with or without an axial shoulder.

[0030] The Fig. Figure 6 shows the upper part of the hybrid module 400 arranged around the rotation axis d in a schematic sectional view. In contrast to the hybrid module 300 of Fig. 5, the side part 414, which is pressed against the axial stop 418, is axially secured by means of the axially elastic retaining ring 416. For this purpose, the annular groove 423 is formed in the projection 405 at an axial distance from the side part 414, into which the retaining ring 416 is inserted under axial preload of the side part 414 against the axial stop 418.

[0031] The Fig. Figure 7 shows the upper part of the hybrid module 500 arranged around the rotation axis d in a schematic sectional view. In contrast to the hybrid modules 100, 200, 300, 400 of Fig. 1, 4 to 7, the centrifugal pendulum 511 forming the torsional vibration isolation device 509 is attached radially inside the damper masses 513 to the rotor carrier 504. In the illustrated embodiment, the rotor carrier 504 has the cup 524 with the axial shoulder 525. The axial stop 518 is machined onto the shoulder 525. The side part 515 of the carrier part 512 is radially expanded relative to the side part 514 and is pressed with its inner circumference into the shoulder 525 against the axial stop 518. The caulkings 516 radially overlap the side part 515 and secure it axially. An anti-twist device can be provided by means of a radial profiling between the inner circumference of the side part 515 and the shoulder 525.

[0032] Fig. Figure 8 shows a schematic sectional view of the upper part of the hybrid module 600 arranged around the rotation axis d. Unlike the hybrid modules of the previous figures, the support part 612 is riveted to the rotor support 604. For this purpose, the extension 605 has a plurality of rivet pins 626 distributed around the circumference at its end, which extend into openings in the side part 614 of the support part 612, which extends radially beyond the extension 605, and are shaped into the rivet heads 627 on the opposite side.

[0033] The Fig. 9 shows the upper part of the hybrid module 700 arranged around the axis of rotation d in a schematic sectional view with a Fig. 4 modified design with a weld 716 of the support part 712 with the rotor carrier 704. The side part 714 of the support part 712 is pressed axially flush with the end face of the extension 705 against the axial stop 718 and is welded on the end face by means of the weld 716 all around or by means of welding points distributed over the circumference.

[0034] The Fig. Figure 10 shows a schematic sectional view of the upper part of the hybrid module 800 arranged around the rotation axis d. In contrast to the hybrid module 700 of Fig. 9, the welding 816 of the side part 814 of the support part 812 to the front side of the extension 805 of the rotor carrier 804 takes place by means of the annular disc 828. The annular disc 828 is riveted to the side part 814 by means of the rivet 829 or rivet projections pressed out of the side part 814. Subsequently, the side part 814 is welded to the extension 805 by means of the circumferential or spot welding 816 on the annular disc 828, after the latter has been centered on the front side of the extension 805.

[0035] The Fig. Figure 11 shows a schematic sectional view of the upper part of the hybrid module 900 arranged around the rotation axis d. In contrast to the hybrid modules of the previous figures, the support part 912 is screwed to the rotor carrier 904. For this purpose, the shoulder 905 of the rotor carrier 904 is radially expanded on its front side and provided with the thread 930. The radially expanded side part 914 is screwed to the shoulder 905 by means of screws 931 that penetrate openings in the side part 914. Alternatively, the shoulder 905 can be shortened and axially flush with the rotor 903 of the electric machine 901, so that the side part can be screwed directly to the rotor 903.

[0036] The Fig. 12 to 14 show alternative embodiments of torsional vibration dampers 110a, 110b, 110c, 110d, 110e, 110f for the hybrid modules 100, 200, 300, 400, 500, 600, 700, 800 of the Fig. 1, 4 to 11.

[0037] The Fig. Figure 12 shows a schematic sectional view of the upper part of the torsional vibration damper 110a arranged around the rotational axis d. The torsional vibration damper 110a is designed as a mass damper 111a with a disc-shaped support part 112a connected to the rotor carrier, on which the damper masses 113a are mounted in the circumferential direction, counteracting the action of the spring elements, such as helical compression springs 132a in this case, and distributed over the circumference.

[0038] The Fig. Figure 13 shows a schematic sectional view of the upper part of the torsional vibration damper 110b, which is arranged so as to rotate about the rotational axis d. The torsional vibration damper 110b is designed as a centrifugal pendulum 111b with the disc-shaped support part 112b and the damper masses 113b arranged on both sides of the latter and distributed around the circumference. Axially opposite damper masses are connected to form pendulum mass units 133b. For example, recesses in the support part 112b, axially penetrating spacer bolts or disc-shaped center sections are provided between the damper masses 113b. The pendulum mass units 133b are mounted on the support part 112b in a pendulum-like manner by means of self-aligning bearings (not visible) in the centrifugal force field of the support part 112b rotating about the rotational axis d. For this purpose, two circumferentially spaced self-aligning bearings are provided for each pendulum mass unit 133b.In a first embodiment, the self-aligning bearings can be formed between the damper masses 113b and the support part 112b. For this purpose, axially opposing recesses with complementary raceways are formed in the damper masses 113b and in the support part 112b, on which a self-aligning roller spanning the recesses rolls.

[0039] In an alternative embodiment, the self-aligning bearings are formed between the center sections connecting the damper masses 113b and the support part 112a. The center sections are accommodated in recesses that have bearing points for raceways arranged radially outside the bearing points of the center sections. A self-aligning roller arranged axially between the damper masses 113b rolls on each of the raceways, which are arranged in a plane and radially one above the other. Depending on the design, the support part 112b is attached to the rotor carrier of the hybrid module radially inside or outside the damper masses 113b.

[0040] The Fig. Figure 14 shows a schematic sectional view of the upper part of the torsional vibration damper 110c, which is arranged rotatably about the rotational axis d. The torsional vibration damper 110c, designed as a centrifugal pendulum 111c with the disc-shaped support part 112c, contains damper masses 113c distributed over the circumference and arranged on both sides of the support part 112c. Axial opposing damper masses 113c are connected to pendulum mass units 133c by means of the center parts 134c. The self-aligning bearings 135c are formed between the center parts 134c and the support part 112c. For this purpose, a center part 134c is received in a recess 136c of the support part 112c. To form a respective self-aligning bearing 135c, the central part 134c has the raceway 138c radially inside the raceway 137c machined on the recess 136c, on which the self-aligning roller 139c rolls.

[0041] The Fig. Figure 15 shows a schematic sectional view of the upper part of the torsional vibration damper 110d, which is designed as a centrifugal pendulum 111d and is rotatable about the rotational axis d. The support part 112d of the centrifugal pendulum 111d is designed in accordance with the centrifugal pendulum 111 of the Fig. 1 is divided into two axially spaced and interconnected side parts 114d, 115d, which accommodate the damper masses 113d, which are distributed around the circumference, between them by means of non-visible pendulum bearings. In contrast to the centrifugal pendulum 111 of Fig. 1, the damper masses 113d are provided on both sides with additional masses 140d, 141d. To accommodate the additional mass 140d facing the side part 114d, the recess 142d is provided in the side part 114d at the height of the oscillation angle of the damper mass 113d.

[0042] The Fig. 16 shows a functional diagram of the torsional vibration damper 110e, which is arranged so as to be rotatable about the rotational axis d. The torsional vibration damper 110e is designed to be speed-adaptive in that the damper masses 113e arranged around the circumference are arranged so as to be able to pendulum in the centrifugal force field of the torsional vibration damper 110e rotating about the rotational axis d. The carrier part 112e is connected to the rotor carrier of the hybrid module. The damper ring 143e is arranged coaxially and rotatably to the carrier part 112e. The damper masses 113e are operatively arranged between the carrier part 112e and the damper ring 143e. The connection between the carrier part 112e and the damper masses 113e is established by means of the self-aligning bearing 135e.The connection between the damper masses 113e and the damper ring 143e is made at a distance in the circumferential direction from the self-aligning bearing 135e by means of the rotary joint 144e, for example a rotary bearing which is stiff in the circumferential direction and which allows rotation in the radial direction between the damper ring 143e and the damper mass 113e.

[0043] When the support part 112e rotates, a predetermined angle around the rotational axis d is established between the support part 112e and the damper ring 143e due to centrifugal force. If torsional vibrations occur, a pendulum movement of the damper masses 113e occurs at the self-aligning bearings 135e, which forces the angle between the damper ring 143e and the support part 112e counter to the effect of the mass moment of inertia of the damper ring 143e, so that a centrifugal force-dependent and thus speed-adaptive damping occurs due to the change in the moment of inertia and the pendulum movement of the damper masses 113e at different radii relative to the rotational axis d.

[0044] The torsional vibration damper 110e can be configured in different ways. For example, the support part 112e can be formed from two spaced-apart and interconnected side parts, with one side part being attached to the rotor carrier. The damper ring 143e and the damper masses 113e can be arranged axially between the side parts. Alternatively, the support part 112e can be disk-shaped and connected to the rotor carrier, with damper rings 143e being arranged on both sides of the support part 112e, and damper masses 113e being arranged in their recesses.

[0045] The Fig. Figure 17 shows a view of the torsional vibration damper 110f designed as a centrifugal pendulum 111f. The centrifugal pendulum 111f essentially corresponds to the centrifugal pendulum 111b of the Fig.13. The support part 112f is disc-shaped, and on both sides of it—here divided into three—the damper masses 113f are arranged distributed around the circumference. The damper masses 113f are mounted on the support part 112f in a pendulum-like manner by means of the self-aligning bearings 135f. In contrast to the centrifugal pendulum-absorbing element 111b, the damper masses 113f of the centrifugal pendulum-absorbing element 111f are elastically coupled to one another in the circumferential direction. For this purpose, the damper masses 113f have spring cups 145f on their circumferential end faces, into which spring elements 146f in the form of helical compression springs 147f are inserted with their spring ends. List of reference symbols 100 hybrid modules 101 Electric Machine 102 Stator 103 Rotor 104 rotor carrier 105 Approach 106 air gap 107 downforce 108 Opening 109 Torsional vibration isolation device 110 torsional vibration dampers 110a torsional vibration damper 110b torsional vibration damper 110c torsional vibration damper 110d torsional vibration damper 110e torsional vibration damper 110f torsional vibration damper 111 Centrifugal pendulum 111a Mass absorber 111b Centrifugal pendulum 111c Centrifugal pendulum 111d centrifugal pendulum 111f centrifugal pendulum 112 carrier part 112a support part 112b support part 112c carrier part 112d carrier part 112e carrier part 112f carrier part 113 absorber mass 113a absorber mass 113b absorber mass 113c absorber mass 113d absorber mass 113e absorber mass 113f absorber mass 114 side panel 114d side panel 115 side panel 115d side panel 116 Caulking 117 Approach 118 Axial stop 119 Opening 120 depression 121 force application area 132a helical compression spring 133b Pendulum mass unit 133c pendulum mass unit 134c Middle section 135c self-aligning bearing 135e self-aligning bearing 135f self-aligning bearing 136c recess 137c career 138c career 139c pendulum roller 140d additional mass 141 Additional mass 141d Additional mass 142d recess 143e absorber ring 144e Slewing ring 145f spring bowl 146f spring element 147f helical compression spring 200 hybrid modules 204 rotor carrier 205 approach 212 carrier part 214 side panel 216 Welding 217 approach 218 Axial stop 222 welding point 300 hybrid modules 304 rotor carrier 305 approach 314 side panel 316 ring part 318 Axial stop 400 hybrid modules 405 approach 414 side panel 416 retaining ring 418 Axial stop 423 ring groove 500 hybrid modules 504 rotor carrier 509 Torsional vibration isolation device 511 centrifugal pendulum 512 carrier part 513 absorber mass 514 side panel 515 side panel 516 Caulking 518 axial stop 524 Potting 525 shoulder 600 hybrid module 604 rotor carrier 605 approach 612 carrier part 614 side panel 626 rivet pins 627 rivet head 700 hybrid module 704 rotor carrier 705 approach 712 carrier part 714 side panel 716 Welding 718 axial stop 800 hybrid module 804 rotor carrier 805 approach 812 carrier part 814 side panel 816 Welding 828 ring disc 829 rivet 900 hybrid module 901 electric machine 903 Rotor 904 rotor carrier 905 approach 912 carrier part 914 side panel 930 thread 931 screw d axis of rotation

Claims

[1] Hybrid module (100, 200, 300, 400, 500, 600, 700, 800, 900) with an electric machine (101, 901) arranged about an axis of rotation (d) with a fixed stator (102) and a rotor (103, 903) arranged rotatably relative to the stator about the axis of rotation (d), which rotor is accommodated on an axial extension (105, 205, 305, 405, 605, 705, 805, 905) of a rotor carrier (104, 204, 304, 504, 604, 704, 804, 904), wherein radially inside the extension (105, 205, 305, 605, 705, 805, 905) a torsional vibration isolation device (109) is arranged, wherein the rotor carrier (104, 204, 304, 504, 604, 704, 804, 904) directly forms an output (107) of the hybrid module (100, 200, 300, 400, 500, 600, 700, 800, 900) and the torsional vibration isolation device (109) is used exclusively as a torsional vibration damper (110, 110a, 110b, 110c, 110d, 110e, 110f) with a carrier part (112, 112a, 112b, 112c, 112d, 112e, 112f, 212, 512, 612, 712, 812,912) and pivotable damper masses (113, 113a, 113b, 113c, 113d, 113e, 113f, 513) are formed thereon, wherein the carrier part (612) is formed from two side parts (114, 114d, 214, 314, 414, 514, 614, 714, 814, 914, 115, 115d, 515) which are connected to one another at an axial distance and which receive damper masses (113, 113d, 513) which are arranged between them and distributed over the circumference and which are pivotably mounted on the side parts (114, 114d, 214, 314, 414, 514, 614, 714, 814, 914, 115, 115d, 515), wherein at least one side part (114, 114d, 214, 314, 414, 614, 714, 814, 914, 115d, 515) extends radially beyond the extension (605) of the rotor carrier and is connected to the rotor carrier (104, 204, 304, 504, 604, 704, 804, 904), wherein the axial extension (605) has a plurality of rivet pins (626) distributed over the circumference at its end,which extend into openings of the side part (614) of the support part (612) which extends radially beyond the shoulder (605) and are formed on the opposite side with rivet heads (627).

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