WO2022268250A1

WO2022268250A1 - Hybrid module

Info

Publication number: WO2022268250A1
Application number: PCT/DE2022/100236
Authority: WO
Inventors: Mario Degler
Original assignee: Schaeffler Technologies AG & Co. KG
Priority date: 2021-06-22
Filing date: 2022-03-29
Publication date: 2022-12-29
Also published as: DE102021116065A1

Abstract

The invention relates to a hybrid module (100) for a hybrid powertrain of a motor vehicle, comprising an electric machine (101) arranged between an internal combustion engine and a transmission. The stator (102) of the electric machine (101) is arranged in a stationary manner and has a support part (103) which is oriented radially inwards and on which a shaft section (111) that is rotated by the internal combustion engine and a rotor support (107) with a rotor (109) are each supported in a separately rotatable and axially fixed manner. The hybrid module also comprises a separating clutch (117) and a torsional vibration insulating device (130). In order to provide a hybrid module (100) with a structure which is as axially narrow as possible, the separating clutch (117) is functionally arranged between the shaft section (111) and the rotor support (107), and the torsional vibration insulating device (130) is received radially outside of the separating clutch (117) and within an installation area of the electric machine (101).

Description

hybrid module

The invention relates to a hybrid module for a hybrid drive train of a motor vehicle with an electric machine arranged between an internal combustion engine and a transmission, the stator of the electric machine being fixed and having a carrier part pointing radially inwards, on which a shaft section driven in rotation by the internal combustion engine and a Rotor carrier with egg nem rotor are each separately rotatable and axially fixed and with a clutch and a torsional vibration isolation device.

Hybrid modules are in hybrid drive trains of motor vehicles, for example, between the internal combustion engine and the transmission and typically have an electric motor, a clutch and a torsional vibration isolation device for isolating torsional vibrations of the internal combustion engine. Hybrid modules known from the publication DE 10 2018 106287 A1, for example, require a large axial installation space as a result of the components that are axially expanded over the electric machine.

The object of the invention is the further development of a hybrid module. In particular, the object of the invention is to propose a hybrid module with a small axial space in front of given, unchanged radial dimensions.

The object is solved by the subject matter of claim 1. The claims dependent on claim 1 provide advantageous embodiments of the subject-matter of claim 1.

The proposed hybrid module is used to support an internal combustion engine by means of its electric machine, so that the motor vehicle can be driven exclusively by means of the internal combustion engine, hybridly or purely electrically. means The internal combustion engine can be coupled to the separating clutch and also operated in a recuperative manner. The torsional vibration isolation device additionally contained in the hybrid module isolates torsional vibrations of the internal combustion engine. The stator of the electric machine is arranged in a fixed manner, for example by means of a housing connected to a motor housing of the internal combustion engine, screwed on for example. The stator has a radially inwardly directed carrier part, on which a shaft section driven by the internal combustion engine and a rotor carrier with a rotor are each separately rotatably and axially fixed, so that the gap between the stator and rotor is precisely specified and the shaft section is opposite centered on the rotor.

Between the internal combustion engine and the electric machine and thus the rest of the hybrid drive train, there is a separating clutch which is effectively arranged between the shaft section and the rotor carrier and decouples the internal combustion engine during electric ferry operation and recuperation so that it can be shut down. Furthermore, the separating clutch allows an impulse start of the internal combustion engine when the electric machine is rotating at a higher speed.

In order to limit the hybrid module to an axially narrow construction, in particular to limit the axial extent of the electric machine, the separating clutch and the torsional vibration isolation device are accommodated within a construction space of the electric machine. The torsional vibration isolation device is arranged radially outside the separating clutch, which means that the separating clutch is arranged with a small diameter and a small radial space requirement directly outside the bearing between the rotor carrier and the carrier part. The separating clutch can be designed as a single-disc or multiple-disc clutch. It is particularly advantageous here if the separating clutch is a cone clutch with two conically complementary ramps, for example on the carrier part and one that is non-rotatably connected to the shaft section. where axially displaceable by an actuating device pressing part if given form with the interposition of friction linings. The actuating device is arranged axially adjacent to the separating clutch and essentially with the same diameter inside the electric machine, so that for the torsional vibration isolation device there is an annular space between the rotor or the rotor carrier and the combination of which is essentially constant over the axial installation space of the electric machine Separating clutch and actuator can be net angeord. The actuating device preferably works hydraulically, with an axially displaceable, pressurized piston acting on the pressing part. The piston is pressurized by means of pressure chambers that can be filled with pressure medium. Pressure medium is supplied by means of supply lines in the transmission input shaft and pressure ducts connecting these to the pressure lines.

Depending on the intended application, the hybrid module can contain different embodiments of the torsional vibration isolation device. In a first embodiment, the torsional vibration isolation device can contain at least one torsional vibration damper. The input part of the at least one torsional vibration damper is operatively connected to the rotor. For example, the input part can intersect the rotor radially and be fastened to a radially widened shoulder of the rotor carrier. In this case, an axial offset is provided between the stator and the rotor, so that the attachment of the input part to the rotor carrier can be provided within the installation space of the stator and thus within the electric machine.

The output part of the torsional vibration damper is provided for a non-rotatable connection to a subsequent drive train device. For example, an output sleeve can be connected in a rotationally fixed manner to the output part, for example riveted or welded. This can be done by means of teeth, for example an internal nenverzahnung with a transmission input shaft of a transmission, a shaft journal fen, shaft socket or a shaft sleeve of a subsequent drive train device such as a dual clutch, a hydrodynamic torque converter or the like to be rotationally test connected. A spring device effective in the circumferential direction is provided between the input part and the output part. In the simplest case, the torsional vibration isolation device can contain a single torsional vibration damper arranged radially inside the rotor carrier and radially outside the separating clutch. This can be arranged axially in line with the separating clutch, axially overlapping or axially adjacent to this.

The at least one torsional vibration damper is preferably designed in a so-called three-disc design. This means that a damper part - here preferably the input part - has two axially spaced disk parts connected to one another and between these disk parts a disk-shaped flange part as a second damper part - here preferably the output part - is arranged. Between the damper parts are distributed over the circumference screws compression springs, for example pre-bent on their use diameter, long Bo gene springs, arranged for example in twos, threes or fours. The end faces of the helical compression springs, such as arc springs, are each effectively acted upon on the input side and output side by corresponding means arranged on the damper parts such as stops, embossings or the like in the circumferential direction.

For example, the at least one torsional vibration damper can be arranged in one or more stages. For example, two separately designed torsional vibration dampers can be provided side by side, connected in parallel or in series. Alternatively, a single torsional vibration damper with two axially side-by-side ordered spring packs with parallel or series-connected, distributed over the circumference arranged helical compression springs can be provided. If helical compression springs designed as arc springs are used, at least one of the two disc parts connected to one another at an axial distance can form a retaining device for supporting the arc springs against centrifugal force.

In a further embodiment of the torsional vibration isolation device, this can contain at least one centrifugal pendulum with a pendulum mass carrier connected to the rotor and on this pendulum masses arranged in a pendulum-type manner and distributed over the circumference in a pendulum-type manner. The pendulum mass carrier of the at least one centrifugal pendulum can be designed as a pendulum flange connected to the rotor carrier, on which pendulum masses distributed over the circumference are arranged on both sides. In this case, pendulum masses arranged axially opposite one another are connected by means of parts to form pendulum mass units. The middle parts pass through corresponding recesses in the pendulum flange. The formation of the self-aligning bearing between tween the pendulum masses and the pendulum flange can be provided on the one hand by means of radially opposite ge, axially in line at the central parts and at the recesses worked raceways on which a spherical roller rolls. On the other hand, axially opposite recesses with raceways can be provided in the pendulum masses and in the pendulum flange, on which raceways an axially extending spherical roller rolls through the recesses.

The pendulum mass carrier of the at least one centrifugal pendulum is preferably formed from two axially spaced-apart, for example riveted, disk parts that are connected to one another radially on the outside and connected to one another on the rotor or rotor carrier in accordance with the input part of the torsional vibration damper described above. In the resulting axi alen free space between the disk parts are distributed over the circumference in one piece or pendulum masses formed from several loosely layered or interconnected metal discs. To form the self-aligning bearing, the pen delmasses and the disc parts have axially opposite recesses with running tracks, on which running tracks a spherical roller axially overlapping the recesses rolls.

The pendulum masses or pendulum mass units of the at least one centrifugal pendulum can be provided in twos, threes or fours. Higher divisions are also possible, but are less advantageous due to the large number of recesses in the pendulum flange or in the disk parts and due to the larger number of components. All pendulum masses can be matched to the same absorber order. Alternatively, a part of the pendulum masses can be tuned to a first absorber order and the other part by changing the pendulum track, mass of the pendulum mass and the like to a second absorber order. For example, a possible cylinder deactivation of the internal combustion engine can be taken into account.

For example, a hybrid module can be provided in whose torsional vibration isolation device two centrifugal pendulums arranged side by side are provided. Here, one of the centrifugal pendulum can be arranged axially at the same height as the separating clutch and the other centrifugal pendulum axially spaced from this. To save axial installation space and to reduce the number of components to be used, a single disc part can be provided between the two axially adjacent pendulum masses of the two centrifugal pendulums, which has the recesses necessary to form the self-aligning bearings with raceways of both centrifugal pendulums and connection points such as rivet openings to the axial Connection of the axially opposite disk parts of both centrifugal pendulum has. Here, the recesses for forming the self-aligning bearings are over the circumference arranged alternately. The connection points can be provided by means of corresponding bolts from standoffs on the same circumference for connection to the two other discs or offset in the circumferential direction for one of the two remaining discs.

The two centrifugal pendulums can be matched to the same absorber order. Alternatively, the centrifugal pendulum can be tuned to different absorber orders. In rare cases, further absorber orders can be provided by having one or both centrifugal pendulums each having parts of the pendulum masses that are tuned to different absorber orders.

According to an advantageous embodiment of a flybrid module, its torsional vibration isolation device can contain a torsional vibration damper and a centrifugal pendulum axially next to one another, radially outside the clutch with its actuating device and radially inside the rotor and inside the installation space of the electric machine.

In a preferred embodiment, the damper parts and the pendulum mass carrier are designed as disc parts arranged axially next to one another, with the pendulum masses arranged distributed over the circumference between axially spaced disc parts of the centrifugal pendulum and between the axially spaced disc parts of one of the damper parts the flange-shaped disc part of the other damper part being arranged are. The two axially spaced disk parts of the torsional vibration damper preferably form the input part of the torsional vibration damper and are connected radially on the outside both to one another and to the rotor or rotor carrier of the electric machine.

To save axial installation space and reduce the number of components, the axially adjacent disk parts of the pendulum mass carrier of the centrifugal pendulum and the damper part of the torsional vibration damper, which is preferably designed as an input part, are fers integrally formed into a single disk part. This disc contains the recesses with raceways for the self-aligning bearing of the centrifugal pendulum, the connection points such as rivet openings for the axially spaced accommodation of the second disc part of the centrifugal pendulum and the loading means for the helical compression springs, for example arc springs of the spring device of the torsional vibration damper. The loading means can be designed as embossings. This disk part can have an axial section radially on the outside to form a restraint device for the helical compression springs designed, for example, as arc springs, and a radially extended end, circumferential shoulder for fastening the torsional vibration isolation device to the rotor or to the rotor carrier.

In this case, the centrifugal pendulum can be arranged directly radially above the separating clutch, ie axially in line with it. The torsional vibration damper is axially adjacent to be as spaced from the separating clutch and arranged radially above the actuation device of the separating clutch. Conversely, the torsional vibration damper can be arranged radially above and axially in line with the separating clutch and the centrifugal force pen del axially adjacent as spaced apart and radially outside the actuating device of the separating clutch.

Furthermore, the centrifugal pendulum can be assigned to the input part or the output part of the torsional vibration damper, so that an effect of the centrifugal pendulum is achieved on the primary side, ie directly connected to the rotor. Alternatively, when the centrifugal pendulum is arranged on the output part of the torsional vibration damper, a secondary side effect of the centrifugal pendulum, ie the downstream hybrid drive train, is achieved. In this case, an axial shoulder provided on the flange part of the output part can be attached to one or both disc parts reach through the provided openings and drive the pendulum mass carrier of the centrifugal pen dels with it in the circumferential direction.

The invention is explained in more detail with reference to the exemplary embodiments shown in FIGS. 1 to 14. These show:

1 is a sectional view of the upper part of a flybrid module arranged about an axis of rotation with a torsional vibration isolation device containing a torsional vibration damper,

FIG. 2 shows the upper part of the flybridge module from FIG. 1 along a modified section line,

3 shows the upper part of a flybrid module arranged about a rotation axis with a torsional vibration damper modified compared to the torsional vibration damper of the flybrid module of FIGS. 1 and 2, in section,

FIG. 4 shows the upper part of the flybridge module from FIG. 3 along a modified section line,

5 shows the upper part of the flybridge module of FIGS. 3 and 4 along a further section line,

6 is a sectional view of the upper part of a flybrid module that is modified compared to the flybrid module of FIGS.

FIG. 7 shows the upper part of the flybridge module from FIG. 6 along a modified section line,

8 shows the upper part of the flybridge module of FIGS. 6 and 7 along a further section line,

FIG. 9 shows the upper part of a flybrid module which is modified compared to the flybrid modules of FIGS. 1 to 8 and is arranged around an axis of rotation a sectional view of a torsional vibration isolation device containing a torsional vibration damper and a centrifugal pendulum pendulum assigned to the secondary side,

FIG. 10 shows the upper part of the flybridge module from FIG. 9 along a modified section line,

11 shows the upper part of the flybridge module of FIGS. 9 and 10 along a further section line,

12 is a sectional view of the upper part of a flybrid module that is modified compared to the flybrid modules of FIGS.

Figure 13 shows the upper part of the flybridge module of Figure 12 along a modified section line and

FIG. 14 shows the upper part of the flybridge module of FIGS. 12 and 13 along a further sectional line.

FIGS. 1 and 2 show the upper part of the flybrid module 100 arranged around the axis of rotation d in a section along two different cutting lines.

The Flybridmodul 100 contains the electric machine 101, the stator 102 is attached to its housing, for example, to a motor housing of an internal combustion engine, not shown, for example screwed. The stator 102 has, on the end face facing the internal combustion engine, the support part 103 which has the bearing flange 104 radially on the inside on its inner circumference. On the outer surface of the bearing flange 104 is by means of the tilting bearing 105 - here by means of the double row Angular ball bearing 106 - the rotor carrier 107 rotatable and axially fixed. The rotor carrier 107 has on its outer circumference the rotor sleeve 108, on the outer surface of which the rotor 109 is accommodated with a constant formation of an air gap relative to the stator 102.

The bearing 110 of the shaft section 111 is provided on the inner surface of the bearing flange 104 , which by means of the deep groove ball bearing 112 accommodates the shaft section 111 in a rotatable and axially fixed manner on the carrier part 103 . The shaft section 111 forms the interface to the internal combustion engine and for this purpose has the non-rotatably fastened connecting flange 113, which is attached to a flywheel attached to a crankshaft of the internal combustion engine, to the crankshaft itself or to an output part of a torsional vibration damper attached to the crankshaft, such as a two-mass flywheel or the like is connected.

The shaft section 111 is mounted on the transmission input shaft 115 of a transmission (not shown in detail) as the downstream drive train device by means of the bearing 114, such as a pilot bearing, with the end of the transmission input shaft 115 and the shaft section 111 receiving the bearing 114, such as a pilot bearing, being non-rotatably connected to the transmission input shaft 115 connected shaft socket 116 is provided.

The separating clutch 117 is arranged between the shaft section 111 and the rotor carrier 107 and is automatically actuated by the actuating device 118 . The separating clutch 117 is formed as a cone clutch with the axially interlocking ko niche ramps 119, 120, on the ramps 119, 120 rotationally fixed in the recesses 122 recorded friction linings are arranged, which form a frictional engagement when the separating clutch 117 is closed or closed. The ramp 119 is arranged in an axially fixed manner on the carrier part 103 , the ramp 120 is attached to the pressing part 121 . The pressing part 121 is non-rotatable and axially displaceable on the shaft lenabschnitt 111 was added and is acted upon by the axially displaceable piston 125 axially. To control the separating clutch 117, pressurized pressure medium is introduced via lines (not shown) in the transmission input shaft 115 and the pressure chambers 128, 129 are pressurized via the rotary feedthroughs 126, 127 to displace the piston 125.

In the exemplary embodiment shown, the torsional vibration isolation device 130 is formed exclusively from the torsional vibration damper 131 . Torsional vibration damper 131 uses its input part 132 to dampen torsional vibrations by transmitting the torque present on rotor 109 via spring device 133 to output part 134 and from there by means of output sleeve 135 to transmission input shaft 115 or shaft socket 116.

The input part 132 is formed from the two disc parts 136, 137 which are connected to one another at a distance from one another. For this purpose, the disk parts 136, 137 radially joined together on the outside, circumferential fastening sections 138, 139, the sleeve 108 connected to the radially outwardly flared mounting flange 140 of the rotor - here by means of the screws 141 within the axial construction space of the stator 102 - are screwed .

The flange part 142 is arranged between the disk parts 136, 137, which is potted radially inward in the direction of the output sleeve 135 and is riveted to it by means of the rivet 180. The disc parts 136, 137 and the flange part 142 have axially ge opposite and distributed over the circumference of recessed spring windows that receive the helical compression springs 143 of the spring device 133 and act on the front side. The spring window of the disc parts 136, 137 also have axially provided support areas 144, 145 to support the helical compression springs 143. FIGS. 3 to 5 show the upper part of the hybrid module 200 arranged around the axis of rotation d along three different lines of intersection. The only difference to the hybrid module 100 of FIGS. 1 and 2 is that the torsional vibration isolation device 230 contains the torsional vibration damper 231 designed as an arc spring damper. which are arranged in twos, threes or fours and thus occupy a correspondingly large circumferential angle.

The input part 232 of the torsional vibration damper 231 is formed from the two disc parts 236, 237, which are screwed to the rotor carrier 207 radially on the outside by means of the screws 241.

The disc part 236 is potted directly inside the rotor sleeve 208 and, as a retaining device 246, supports the arc springs 243, 247 against the effect of centrifugal force radially outward.

The front sides of the arc springs 243, 247 are acted upon on the input side by means of the embossings 248, 249 provided in the disk parts 236, 237.

The output part 234 contains the radially inner potted flange part 242, which forms the output-side loading means radially on the outside by means of the radially expanded flange wings 250 and the output of the torsional vibration damper 231 and thus of the torsional vibration isolation device 230 radially on the inside by riveting it to the output sleeve 235 using rivets 280 is.

To provide friction superimposed on the effect of the spring device 233, the friction device 251 can be provided between the flange part 242 and the disc part 237, here in the form of the plate spring 252 pretensioned between them. 6 to 8 show the upper part of the hybrid module 300 arranged around the axis of rotation d, which, in contrast to the hybrid modules 100, 200 of the previous figures, has the torsional vibration isolation device 330 with two centrifugal pendulums 353, 354. Since the centrifugal pendulum 353, 354 are speed-adaptive torsional vibration absorbers, the torque applied to the rotor carrier 307 is transmitted directly to the output sleeve 335. For this purpose, the driven pulley 355 is arranged between the radially outwardly widened mounting flange 340 and the output sleeve 335, which is connected radially outside by means of the screws 341 to the mounting flange 340 and radially inside by means of the rivet 380 to the output sleeve 335. Radially between these connections are the centrifugal pendulum 353, 354 by means of the rivet 380 with the driven pulley 355 connected.

The centrifugal pendulum 353, 354 are placed axially next to each other in the space between the separating clutch 317 and the rotor sleeve 308 within the electric machine 301. The pendulum mass carriers 356, 357 of the centrifugal pendulums 353, 354 are formed from the axially spaced disk parts 336, 337, 358, which each receive a set of pendulum masses 361, 362 distributed over the circumference in the intermediate spaces 359, 360 formed by them. The disk part 337 is connected to the driven disk 355 by means of the rivet 380, and the disk parts 336, 337, 358 to one another by means of the spacer bolts 363, 364 distributed over the circumference. Two spacer bolts 363, 364 are each arranged radially one above the other and each take a stop buffer 365, 366 on. The axially central disk part 358 has the receptacles for the spacer bolts 363, 364 of the two adjacent disk parts 336, 337. These are arranged alternately over the circumference.

The pendulum masses 361, 362, which are layered from several sheet metal discs, are pendulum-fed by means of pendulum bearings 367, 368 in the centrifugal force field of which the pendulum mass carrier 356, 357 rotates about the axis of rotation d along a predetermined aerial tramway. high recorded. For this purpose, in the pendulum masses 361 and in the disk parts 336, 358 or in the pendulum masses 362 and in the disk parts 358, 337 there are axially opposite recesses 369, 370, 371 or recesses 372, 373, 374 with complementary, the pendulum trajectories of the pendulum masses 361 , 362 predetermined raceways provided on which raceways the spherical rollers 375, 376, which are designed here in a stepped manner, roll off. The recesses 369, 370, 371 alternate with the recesses 372, 373, 374 and with the spacer bolts 363, 364 over the circumference, so that the pendulum masses 361 of one centrifugal pendulum 353 with the pendulum masses 362 of the other centrifugal pen dels 354 change the scope. The axially central disk part 358 has spacer bolts 363, 364 and recesses 371, 374 of both centrifugal pendulums 353, 354 distributed over the circumference.

The two centrifugal pendulum 353, 354 can be matched to the same absorber order or un ferent absorber orders.

FIGS. 9 to 11 show the upper part of the hybrid module 400 arranged around the axis of rotation d along three different cutting lines. In contrast to the hybrid modules 100, 200, 300 of the previous figures, the torsional vibration isolation device 430 of the hybrid module 400 contains a combination of the torsional vibration damper 431 and the centrifugal pendulum 454 the separating clutch 417 and the rotor sleeve 408 of the rotor carrier 407 are arranged. The torsional vibration damper 431 is at the axial level of the separating clutch 417 and the centrifugal pendulum 454 is arranged axially adjacent to this.

The torsional vibration damper 431 is connected to the rotor carrier 407 by means of its input part 432 . The output part 434 of the torsional vibration damper 431 drives the centrifugal pendulum 454. Thus, the centrifugal pendulum 454 is on the secondary side, ie assigned to the output part 434 and downstream of the torsional vibration damper 431 .

The disk part 436 of the input part 432 is connected to the fastening flange 440 of the rotor sleeve 408, screwed here by means of screws that are not shown.

Disk part 436 is potted directly radially inside rotor sleeve 408 and forms retaining device 446 for arc springs 443, 447. Disk part 437 is connected radially outward to disk part 436 in the region of retaining device 446, for example welded. The output part 434 contains the flange part 442, which has the axially angled projection 475 radially on the inside, which engages in corresponding recesses 476 of the disc parts 477, 478 of the pendulum mass carrier 457 of the centrifugal pendulum 454.

Between the disk parts 477, 478 of the pendulum mass carrier 457, the pendulum masses 462 distributed over the circumference are accommodated and suspended by means of the pendulum bearings 468 on the pendulum mass carrier 457 in a pendulum-able manner. The Schei benteile 477, 478 are spaced apart axially by means of the approach 475 a related party. Between the disk parts 477, 478, the stop buffers 466 for the pendulum masses 462 are accommodated on the approach 475.

The disk part 478 is connected to the output sleeve 435 by means of the rivet 480, so that the torque path of the torque applied to the rotor carrier 407 from the disk parts 436, 437 via the spring device 433 with the arc springs 443, 447, the flange part 442 and the disk part 478 in the output sleeve 435 is passed.

FIGS. 12 to 14 show the upper part of the flybrid module 500 arranged around the axis of rotation d along different section lines. Torsional vibration isolation device 530 contains a combination of torsional vibration damper 531 and the centrifugal pendulum 553, which are arranged axially side by side within the installation space of the electric machine 501 and radially between the rotor sleeve 508 and the separating clutch 517. The centrifugal pendulum 553 is here arranged axially in line with the separating clutch 517 and the torsional vibration damper 531 axially spaced from this.

Another difference compared to the torsional vibration isolation device 430 of Figures 9 to 11 is the connection of the centrifugal pendulum 553. This is assigned to the input part 532 with the disk parts 536, 537 of the torsional vibration damper 531 fastened to the rotor sleeve 508 of the rotor carrier 507 and thus to the rotor carrier 507 on the primary side.

The structure and arrangement of the torsional vibration damper 531 essentially corresponds to the torsional vibration damper 231 of FIGS. 3 to 5. The disc parts 577, 578 forming the pendulum mass carrier 557 are connected to one another at an axial distance by means of the spacer buffers 560 on receiving spacer bolts and take between them the pendulum masses 562 distributed over the circumference. The pendulum masses 562 are suspended by means of the pendulum bearing 568 in an oscillating manner on the disc parts 577, 578 of the pendulum mass carrier 557.

The torque present at the rotor carrier 507 is transmitted with damping from the disk parts 536, 537 via the spring device 533 with the arc springs 543, 547, the output part 534 with the flange part 542 to the output sleeve 535 connected to it by means of the rivet 580. The centrifugal pendulum-type pendulum 553 supports the damping effect of the torsional vibration damper 531 by means of speed-adaptive torsional vibration damping on the input part 532. Reference character list

100 hybrid module

101 electric machine

102 stator

103 support part

104 bearing flange

105 storage

106 angular contact ball bearings

107 rotor carrier

108 rotor sleeve

109 rotors

110 storage

111 shaft section

112 deep groove ball bearings

113 connection flange

114 camp

115 transmission input shaft

116 shaft sockets

117 disconnect clutch

118 actuator

119 ramp

120 ramp

121 pressing part

122 recess

123 friction lining

124 friction lining

125 pistons

126 rotary joint

127 rotary joint

128 pressure chamber

129 pressure chamber

130 torsional vibration isolation device torsional vibration damper

132 input part

133 spring device

134 output part

135 output sleeve

136 disk part

137 disk part

138 attachment section

139 attachment section

140 mounting flange

141 screw

142 flange part

143 helical compression spring

144 support area

145 support area

180 rivet

200 flybrid module

207 rotor carrier

208 rotor sleeve

230 torsional vibration isolation device

231 torsional vibration damper

232 input part

233 spring device

234 output part

235 output sleeve

236 disk part

237 disk part

241 screw

242 flange part

243 bow spring

246 restraint device

247 bow spring

248 impression

249 impression 250 flange wings

251 friction device

252 disk spring 280 rivet

300 hybrid module

301 electric machine

307 rotor carrier

308 rotor sleeve 317 disconnect clutch

330 torsional vibration isolation device

335 output sleeve

336 disk part

337 disk part

340 mounting flange

341 screw

353 centrifugal pendulum

354 centrifugal pendulum

355 driven pulley

356 pendulum mass carrier

357 pendulum mass carrier

358 disk part

359 interstice

360 space

361 pendulum mass

362 pendulum mass

363 standoffs

364 standoffs

365 bump stops

366 bump stops

367 self-aligning bearings

368 self-aligning bearings

369 recess

370 recess

371 recess 372 recess

373 recess

374 recess

375 pendulum roller

376 spherical roller 380 rivet

400 hybrid module

401 electric machine

407 rotor carrier

408 rotor sleeve 417 disconnect clutch

430 torsional vibration isolation device

431 torsional vibration damper

432 input part

433 spring device

434 output part

435 output sleeve

436 disk part

437 disk part

440 mounting flange

442 flange part

443 bow spring

446 restraint device

447 arc spring 454 centrifugal pendulum 457 pendulum mass carrier 462 pendulum mass

466 bump stop 468 self-aligning bearing

475 approach

476 recess

477 disk part

478 disc part 480 rivet 500 hybrid module

501 electric machine

507 rotor carrier

508 rotor sleeve 517 disconnect clutch

530 torsional vibration isolation device

531 torsional vibration damper

532 input part

533 spring device

534 output part

535 output sleeve

536 disk part

537 disk part

542 flange part

543 arc spring 547 arc spring 553 centrifugal pendulum 557 pendulum mass carrier 560 bump stop

562 pendulum mass 568 pendulum bearing

577 disk part

578 disk part

579 rivet

580 rivet d axis of rotation

Claims

patent claims

1. Hybrid module (100, 200, 300, 400, 500) for a hybrid drive train of a motor vehicle with an electric machine (101, 301, 401, 501) arranged between an internal combustion engine and a gearbox, the stator (102) of the electric machine (101 , 301, 401, 501) is fixed and has a radially inwardly directed support part (103) on which a rotatably driven by the internal combustion engine shaft portion (111) and a rotor carrier (107, 207, 307, 407, 507) with a Rotor (109) are each separately rotatable and axially fixed and with a separating clutch (117, 317, 417, 517) and a torsional vibration isolation device (130, 230, 330, 430,

530). , 430, 530) radially outside the separating clutch (117, 317, 417, 517) and within an installation space of the electric machine (101, 301, 401, 501).

2. Hybrid module (100, 200, 300, 400, 500) according to claim 1, characterized in that the separating clutch (117, 317, 417, 517) is designed as a cone clutch.

3. Hybrid module (100, 200, 400, 500) according to claim 1 or 2, characterized in that the torsional vibration isolation device (130, 230, 430, 530) at least one by means of an input part (132, 232, 432, 532) with the Rotor (109) effectively connected and provided by means of an output part (134, 234, 434, 534) for the non-rotatable connection to a downstream drive train device torsional vibration damper (131, 231, 431, 531), wherein between the input part (132, 232, 432, 532) and the output part (134, 234, 434, 534) a spring device (133, 233, 433, 533) acting in the circumferential direction is provided.

4. Hybrid module (300, 400, 500) according to one of claims 1 to 3, characterized in that the torsional vibration isolation device (330, 430, 530) has at least one centrifugal pendulum (353, 354, 454, 553) with a rotor connected pendulum mass carrier (356, 357, 457, 557) and pendulum masses (361, 362, 462, 562) arranged on this by means of pendulum bearings (367, 368, 468, 568) and distributed over the circumference in an oscillating manner.

5. Hybrid module (300) according to claim 4, characterized in that the torsional vibration isolation device (330) contains two centrifugal pendulums (353, 354) arranged next to one another, one centrifugal pendulum (353) being axially at the same height as the separating clutch (317) and the other Centrifugal pendulum (354) is arranged axially spaced from this.

6. Hybrid module (400, 500) according to any one of claims 1 to 5, characterized in that a torsional vibration damper (431, 531) and a centrifugal pen del (454, 553) are arranged axially side by side.

7. Hybrid module (500) according to claim 6, characterized in that the torsional vibration damper (531) contains an input part (532) formed from two axially spaced disc parts (536, 537), between which disc parts there is a flange part (542) of the output part (534) is arranged, wherein the pendulum mass carrier (557) of the centrifugal pendulum (553) is connected to one of the disc parts (536).

8. Hybrid module (500) according to claim 7, characterized in that the centrifugal pendulum (553) is arranged axially at the same height as the separating clutch (517) and the torsional vibration damper (531) axially spaced from the separating clutch (517).

9. Hybrid module (400) according to claim 6 or 7, characterized in that the torsional vibration damper (431) is arranged axially at the same height as the separating clutch (417) and the centrifugal pendulum (454) is axially spaced from the separating clutch (417).

10. Hybrid module (400) according to any one of claims 6, 8 or 9, characterized in that the pendulum mass carrier (457) of the centrifugal pendulum (454) is connected to the output part (434) of the torsional vibration damper (431).