阅读说明：本技术 用于机动车的减振装置和驱动系统 (Vibration damping device and drive system for a motor vehicle ) 是由 克里斯蒂安·丁格 大卫·施奈德尔巴赫 斯蒂芬·梅恩沙因 凯·申克 托尔斯滕·克劳斯 本杰明 于 2021-06-10 设计创作，主要内容包括：本发明涉及一种减振装置和一种驱动系统,其中,减振装置具有包括可与内燃机连接的输入侧的第一法兰部件、扭转减振器和可围绕转动轴线转动地支承的输出侧,其中,扭转减振器具有防护罩、至少一个储能件、第二法兰部件,其中,第一法兰部件克服储能件的作用可相对于第二法兰部件围绕转动轴线转动。第一法兰部件在第一端侧上与防护罩连接并且第一法兰部件和防护罩共同地限定布置在防护罩的径向内侧的油室,其中,储能件至少局部地布置在油室中并且第二法兰部件构造成将可经由输出侧输入的油引入油室中。(The invention relates to a vibration damping device and a drive system, wherein the vibration damping device comprises a first flange part having an input side that can be connected to an internal combustion engine, a torsional vibration damper and an output side that is mounted rotatably about a rotational axis, wherein the torsional vibration damper comprises a protective cover, at least one energy storage element, a second flange part, wherein the first flange part can be rotated about the rotational axis relative to the second flange part counter to the action of the energy storage element. The first flange part is connected to the protective hood on the first end side and the first flange part and the protective hood jointly delimit an oil chamber arranged radially inside the protective hood, wherein the energy storage element is arranged at least partially in the oil chamber and the second flange part is configured to introduce oil that can be fed via the output side into the oil chamber.)

1. A vibration damping device (15) for a drive system (10) of a motor vehicle,

has the advantages of

-a first flange part (55), the first flange part (55) comprising an input side (40) connectable with an internal combustion engine (20),

-a torsional vibration damper (60) and

an output side (45) mounted rotatably about a rotational axis (16),

-wherein the torsional vibration damper (60) has a shield (70), at least one energy storage member (75), a second flange part (65),

-wherein the first flange part (55) is rotatable relative to the second flange part (65) about an axis of rotation (16) against the action of the energy storage member (75),

it is characterized in that the preparation method is characterized in that,

-the first flange part (55) is connected with the protective cover (70) on a first end side (85), and the first flange part (55) and the protective cover (70) jointly define an oil chamber (220) arranged radially inside on the protective cover (70),

-wherein the energy storage element (75) is arranged in one subsection (245) in the oil chamber (220), and the second flange part (65) is configured to introduce oil (170) which can be input via the output side (45) into the oil chamber (220).

2. The vibration damping device (15) according to claim 1,

-wherein the first flange part (55) at least partially defines a collecting space (230) on a second end side (105) facing away from the oil chamber (220),

-wherein at least one axially extending through hole (225) is arranged in the first flange part (55),

-wherein the through hole (225) opens into the collecting space (230),

-wherein the through hole (225) is arranged radially inside an inner circumferential side (185) of the shield (70).

3. The vibration damping device (15) according to any one of the preceding claims,

-wherein the energy storage element (75) bears with the sub-section (245) against a first inner circumferential side (185) of the protective cover (70) and forms a frictional contact with the first inner circumferential side (185),

-wherein the sub-section (245) is arranged completely in the oil chamber (220).

4. The vibration damping device (15) according to any one of the preceding claims,

-wherein the torsional vibration damper (60) has a third flange part (76) comprising oil guiding vanes (237) and ribs (200),

-wherein the third flange part (76) is connected torque-transmitting with the input side (40),

-wherein the rib (200) is coupled with the energy storage member (75) and is designed to operate the energy storage member (75),

-wherein the oil guiding vane (237) is arranged radially inside the energy storage (75) and is designed to guide oil (170) onto the energy storage (75).

5. The vibration damping device (15) according to any one of the preceding claims,

-wherein the protective cover (70) is designed to be uninterrupted, preferably bell-shaped, and defines the oil chamber (220) radially inside.

6. The vibration damping device (15) according to any one of the preceding claims,

-having a flywheel mass part (50) which is connected in a torque-transmitting, preferably non-rotatable manner, to an internal combustion engine (20) of the drive system (10),

-wherein the flywheel mass (50) is arranged radially outside the first flange part (55) and is connected with the first flange part (55),

-wherein the flywheel mass (50) and the first flange part (55) are preferably constructed in one piece and of identical material.

7. A drive system (10) for a motor vehicle,

-an internal combustion engine (20) having a vibration damping device (15) according to any one of the preceding claims and comprising a motor output side (90) and a motor housing (110),

-wherein the input side (40) of the vibration damping device (15) is connected to the motor output side (90) in a torque-transmitting, preferably rotationally fixed manner.

8. The drive system (10) of claim 7 and claim 2,

-wherein the motor housing (110) is arranged axially opposite the second end side (105) and spaced apart from the second end side (105),

-wherein the motor housing (110) defines the collecting space (230) together with the second end side (105).

9. The drive system (10) of claim 7 or 8,

-wherein the internal combustion engine (20) has an oil circuit (250),

-wherein the oil circuit (250) is fluidly separated from the collecting space (230).

10. The drive system (10) of any of claims 7 to 9,

-having an electric motor (25),

-wherein the electric motor (25) is arranged on a side of the first flange part (55) facing the first end side (85),

-wherein the electric machine (25) is connected in a torque-transmitting manner to an output side (45) of the vibration damping device (15).

Technical Field

The present invention relates to a vibration damping device according to claim 1 and a drive system according to claim 7.

Background

DE 10035522C 1 discloses a dual mass flywheel for a motor vehicle. The dual-mass flywheel is fixedly connected with a crankshaft of the internal combustion engine. The dual mass flywheel has a helical compression spring that slides along a pad at a radially outer portion. Wear occurs due to the helical compression spring sliding along the pad. Furthermore, the sliding characteristics between the helical compression spring and the spacer change over the life of the dual mass flywheel.

Disclosure of Invention

The object of the present invention is to provide an improved vibration damping device and an improved drive system for a motor vehicle.

This object is achieved by means of a vibration damping device according to claim 1 and a drive system according to claim 7. Advantageous embodiments are given in the dependent claims.

It is known to provide an improved vibration damping device for a drive train of a motor vehicle, in that the vibration damping device has a first flange part having an input side which can be connected to an internal combustion engine, a torsional vibration damper and an output side which is mounted so as to be rotatable about a rotational axis. The torsional vibration damper has a shield, at least one energy storage member and a second flange member. The first flange part is rotatable relative to the second flange part about an axis of rotation against the action of the energy storage means. The first flange part is connected to the protective hood on the first end side. The first flange part and the shield jointly define an oil chamber arranged radially inside the shield. The energy storage element is arranged in a subsection in the oil chamber and the second flange part is designed to introduce oil which can be fed in via the output side into the oil chamber.

This embodiment has the advantage that the wear between the energy storage element and the protective hood is reduced, as a result of which the vibration damping device has a particularly long service life. Furthermore, wear particles which are produced when the energy storage element rubs against the protective hood are transported away by the oil. Furthermore, the friction characteristics are made substantially constant over the service life of the damping device.

In a further embodiment, the first flange part at least partially delimits the collecting space on the second end side facing away from the oil chamber. At least one axially extending through-hole is arranged in the first flange part. The through hole opens into the collecting space. The through hole is arranged radially inside the inner circumferential side of the shield. The oil level of the oil chamber and the maximum extension are defined by the through-opening, wherein excess oil passes from the oil chamber into the collecting space via the through-opening.

In a further embodiment, the energy storage element in the partial section rests against the first inner circumferential side of the protective hood and forms a frictional contact with the first inner circumferential side. The sub-section is arranged completely in the oil chamber. Dry friction between the energy storage means and the protective hood can thereby be avoided, so that the friction and wear between the energy storage means and the protective hood are low.

In a further embodiment, the torsional vibration damper has a third flange part with oil-guiding vanes and a rib, wherein the third flange part is connected to the input side in a torque-transmitting manner, wherein the rib is coupled to the energy storage means and is designed to operate the energy storage means, wherein the oil-guiding vanes are arranged radially inside the energy storage means and are designed to guide oil to the energy storage means. This ensures that the oil flows optimally through the oil guide vane in the direction of the oil chamber and the energy storage element, so that the oil is ensured to flush the energy storage element in this path in the direction of the oil chamber.

It is particularly advantageous if the protective hood is designed without interruption, preferably in the shape of a bell, and delimits the oil chamber on the radial inside. Thereby avoiding an undesired outflow of oil from the oil chamber.

In a further embodiment, the vibration damping device has a flywheel mass part which is connected to the internal combustion engine of the drive system in a torque-transmitting, preferably rotationally fixed manner. The flywheel mass is arranged radially outside the first flange part and is connected to the first flange part. The flywheel mass part and the first flange part are preferably formed in one piece and of identical material. The arrangement of the flywheel mass on the motor side makes it possible to adapt the damping device particularly well to rotational irregularities to be damped which are provided by the internal combustion engine. Furthermore, the improved quality allows rotational irregularities to be introduced into the torsional vibration damper at least in part in a reduced manner, so that the vibration damper arrangement has particularly good damper properties.

A drive system for a motor vehicle has the above-described vibration damping device and an internal combustion engine including a motor output side and a motor housing. The input side of the vibration damping device is connected to the output side of the motor in a torque-transmitting, preferably rotationally fixed manner. This embodiment has the advantage that rotational irregularities from the internal combustion engine are at least partially damped, so that the drive system is particularly quiet and the user of the motor vehicle is particularly comfortable.

In a further embodiment, the motor housing is arranged axially opposite and spaced apart from the second end side. The motor housing defines a collection space with the second end side. This embodiment has the advantage that the number of components of the drive system is particularly low and no further components are required to define the collecting space.

In a further embodiment, the internal combustion engine has an oil circuit, wherein the oil circuit is fluidically separated from the collecting space. This embodiment has the advantage that wear particles, which are produced by frictional contact between the protective hood and the energy storage element, are prevented from entering the oil circuit. Furthermore, the motor oil circulating in the oil circuit can be optimally matched to the internal combustion engine, without additional compromises being made for the lubrication of the frictional contact between the energy store and the protective hood.

In another embodiment, the drive system has an electric motor. The electric motor is arranged on a side of the first flange part facing the first end side. The electric machine is connected to the output side of the vibration damping device in a torque-transmitting manner. This embodiment has the advantage that the electric machine can be operated as a generator and the drive torque is applied to the electric machine with low rotational irregularities, so that the electric machine can be operated particularly uniformly.

Drawings

The invention is explained in detail below with reference to the drawings. In which is shown:

fig. 1 shows a detail of a longitudinal section of a half of a drive system for a motor vehicle;

FIG. 2 illustrates a portion A, labeled in FIG. 1, of a vibration damping device of the drive system illustrated in FIG. 1;

FIG. 3 shows a schematic view of a torsional vibration damper; and

fig. 4 shows a perspective view of a third flange part of the drive system shown in fig. 1.

Detailed Description

Fig. 1 shows a schematic half-section of a drive system 10 for a motor vehicle.

The drive system 10 has a vibration damping device 15 mounted so as to be rotatable about a rotational axis 16, an internal combustion engine 20 and a first electric machine 25. Additionally, the drive system 10 may have another motor 26. The drive system 10 may also be referred to as a hybrid drive.

The electric motor 25 can be designed in particular as a brushless direct current motor. In fig. 1, the electric machine 25 is operated as a generator. The electric machine 25 can also be used as a drive motor for a motor vehicle. In fig. 1, for example, the electric motor 25 is designed as an inner rotor. In this embodiment, the motor 25 has, for example, a rotor 30 and a stator 35. The rotor 30 has, for example, permanent magnet assemblies, while the stator 35 is provided with coils.

The vibration damping device 15 has an input side 40, an output side 45, a flywheel mass 50, a first flange part 55, a housing 155 and a torsional vibration damper 60. The torsional vibration damper 60 is disposed in the housing interior space 160 of the housing 150. Torsional vibration damper 60 can be configured, for example, as a simple torsional vibration damper, a tandem vibration damper, or a dual vibration damper. Other designs of torsional vibration damper 60 are also conceivable. In addition to torsional vibration damper 60, damping device 15 may also have a rotational speed adaptive damper, which is not shown in fig. 1. The rotational speed adaptive vibration damper can be arranged radially outside the torsional vibration damper 60 in the housing interior 160, for example.

The torsional vibration damper 60 has a second flange part 65, a protective cover 70, at least one energy storage element 75 and a third flange part 76. The energy storage member 75 may have at least one compression spring and/or an arc spring. The energy storage element 75 can also have, for example, a plurality of compression springs embedded in one another. Other designs of the energy storage means 75 are also conceivable. The clutch is arranged in a transmission 131, which is connected to the output side 45 of the vibration damping device.

The shield 70 is connected to the first flange part 55, for example by means of a first connection 80, for example a rivet connection. In this case, the protective cap 70 rests against the first end 85 of the first flange part 55. The first flange part 55 is disk-shaped and extends substantially in a plane of rotation perpendicular to the axis of rotation 16. Radially outward of the first connection 80, the first flange part 55 is connected to the flywheel mass 50. In this embodiment, for example, the flywheel mass 50 and the first flange part 55 are formed in one piece and are of identical material. A two-part design of the first flange part 55 and the flywheel mass 50 is also possible. The first flange part 55 has an input side 40 on the radially inner side.

The input side 40 is connected to a motor output side 90 of the internal combustion engine 20 in a torque-transmitting, preferably rotationally fixed manner. The motor output 90 can be formed, for example, by a crankshaft flange 91 of a crankshaft 95 of the internal combustion engine 20. In this embodiment, for example, the first flange part 55 is connected to the motor output side 90 in a rotationally fixed manner by means of a second connecting element 100, which is designed, for example, as a screw connection. Additionally, the third flange part 76 may be connected with the first flange part 55 radially inside with respect to the first connection 80 via the second connection 100. Here, the first flange part 55 is arranged axially between the crankshaft flange 91 and the third flange part 76. The motor output side 90 rests with a first end side 85 in the axial direction with respect to the rotational axis 16 on a second end side 105 of the first flange part 55. The first flange part 55 projects beyond the motor output side 90 in the radial direction.

The internal combustion engine 20 has a motor housing 110. The motor housing 110 can be configured, for example, as a crankshaft housing from which the motor output side 90 projects in the radial direction on the side facing the vibration damping device 15. A stepped portion 120 is formed on a third end side 115 of the motor housing 110 disposed axially opposite the second end side 105. As the radial distance from the axis of rotation 16 increases, the distance between the second end side 105 and the third end side 115 decreases due to the step 120. The step portion 120 has, for example, a radial overlap with the first connector 80. A radial overlap is understood here to mean that, when two components, for example the first connection element 80 and the step 120, are projected in the axial direction into a projection plane in which the two components, for example the first connection element 80 and the step 120, coincide, the projection plane extending in a rotation plane perpendicular to the rotation axis 16.

The output side 45 is arranged axially opposite the input side 40. The output side 45 may be part of the second flange member 65. The output side 45 is connected in a rotationally fixed manner via a third connection 125 to a transmission input shaft 130 of a transmission 131. The third connector 125 may be configured as a rivet connector, for example. Other embodiments of third connecting element 125 are also possible, for example as a shaft/sleeve connection. The transmission input shaft 130 is rotatably supported about the rotational axis 16 via a bearing assembly 135.

The transmission input shaft 130 has a rotor carrier 150, wherein the rotor carrier 150 carries the rotor 30 of the electric machine 25 radially on the outside. The rotor carrier 150 is arranged, for example, in a partially extended manner in the plane of rotation about the axis of rotation 16. The rotor holder 150 is arranged axially opposite the third end side 115. A third link 125 is disposed radially inward of the rotor holder 150.

The transmission input shaft 130 has an input passage 140 on the radially inner side. The supply channel 140 is fluidically connected on one side to a delivery pump (not shown in fig. 1), for example a gear 131. The inlet channel 140 opens into the housing interior 160 at a passage 145 on a radially inner side relative to the outlet side 45. In operation of drive system 10, oil 170 is delivered by the delivery pump via inlet channel 140 and port 145 into housing interior 160. The oil 170 is substantially not subjected to a pressure of more than 0.3 bar.

Furthermore, not shown in fig. 1, the housing 155 can have an oil sump from which the oil 170 is drawn off by a feed pump after flowing through the torsional vibration damper 60.

Fig. 2 shows a detail a, marked in fig. 1, of the damping device 15 of the drive system 10 shown in fig. 1.

The shield 70 defines a positioning space 175 with a first inner circumferential side 185 on the radially inner side, wherein the energy storage member 75 is arranged in the positioning space 175. The second flange part 65 is partially arranged radially inside the energy storage member 75.

The second flange part 65 is configured in a pot-like manner and has, radially on the outside, an actuating element 180 (shown in dashed lines in fig. 2), a radial section 181 and a first connecting section 182. The radial section 181 extends in a plane of rotation and forms the output side 45. The radial portion 181 bears against the transmission input shaft 130. The radial section 181 is connected radially on the outside to a first connecting section 182 of hollow-cylindrical design. The first connecting section 182 is connected to the actuating element 180 on the side axially opposite the radial section 181 facing the first end side 85, the actuating element extending substantially radially outward. Preferably, a plurality of operating elements 180 arranged offset from one another in the circumferential direction are arranged on the first connection section 182. The operating element 180 has an overlap with the energy storage member 75 in the circumferential direction. Here, the actuating element 180 engages into the positioning space 175.

The third flange part 76 has a second connecting section 195 and a rib 200. The second connecting section 195 extends substantially in a plane of rotation perpendicular to the axis of rotation and bears against the first end side 85 of the first flange part 55. The second connection section 195 may be fixed with the second connector 100. The fixed end 205 of the rib 200 is connected with the radially outer end of the second connecting section 195. The ribs 200 project into the positioning space 175 in the axial direction. Here, the rib 200 extends substantially obliquely to the axis of rotation 15. The free ends 210 of the ribs 200 are at a greater radial distance from the axis of rotation 16 than the fixed ends 205. The rib 200 is arranged offset from the operating element 180 in the circumferential direction. Here, the rib 200 is coupled to one side of the energy storage member 75, and preferably, the rib 200 abuts against one side of the energy storage member 75. The actuating element 180 bears against a second side of the energy storage means 75 opposite in the circumferential direction.

The protective hood 70 is configured in a hood-like manner, in particular in a bell-like manner, and has walls without discontinuities. The shield 70 defines an oil chamber 220 in the positioning space 175 and in the housing inner space with a first inner circumferential side 185 in the circumferential direction. The oil chamber 220 is a part of the positioning space 175. The oil chamber 220 is defined in the axial direction by the first flange part 55 on the axial side facing the internal combustion engine 20 and by the end 215 of the protective cover 70 on the side facing the transmission 131.

At least one through-hole 225 is arranged in the first flange part 55. The through-hole 225 extends in the axial direction. The through-hole 225 may be configured as a bore or slot in the first flange part 55. A collection chamber 230 is defined in the housing interior 160 between the second end side 105 and the third end side 115 (see fig. 1). The collection chamber 230 is fluidly connected to the positioning space 175 and the oil chamber 220 via the through-hole 225.

Fig. 3 shows a schematic view of torsional vibration damper 60.

The shield 70 is configured to be uninterrupted. Here, uninterrupted is understood to mean that no through-openings are provided in the first inner circumferential side 185 of the protective hood 70, so that the oil 170 passes radially outward through the protective hood 70. By means of the housing-like, preferably bell-shaped design of the protective hood 70, the radially inner end 215 of the protective hood 70 is arranged, on the one hand, offset in the axial direction from the first flange part 55, and, on the other hand, the end 215 is arranged, on the inside, offset in the radial direction from the first connection 80. The end 215 of the boot 70 defines a lead-through 235, wherein the lead-through 235 is engaged through the second flange part 65 (not shown in fig. 3). The lead 235 may have a circular cross-section.

Fig. 4 shows a perspective view of third flange part 76 of torsional vibration damper 60 shown in fig. 1 to 3.

The third flange part 76 has at least one oil deflector 237 and an opening 236 offset in the circumferential direction from the rib 200. The opening 236 and the oil deflector 237 extend from the first end side 85 in the axial direction of the energy storage element 75. The opening 236 is arranged radially outside the oil deflector 237 and has a radial overlap with the lead-through 235 in the mounted state.

In this embodiment, the opening 236 extends annularly about the axis of rotation 16. The third flange part 76 is produced from a sheet metal in a press bending process, wherein the oil deflector 237 is bent out of the opening 236 during production. The oil guide vane 237 is arranged radially inside the energy storage member 75 and has an axial overlap with the energy storage member 75. The axial overlap is understood here to mean that, when two components, for example the energy store 75 and the oil guide vane 237, are projected in the radial direction into a further projection plane, in which the axis of rotation 16 extends, the two components coincide.

The operation of the drive system 10 in operation is explained below with reference to fig. 1 to 4.

The drive system 10 has a plurality of operating states due to its design of the hybrid drive system 10. In the first operating state, a first torque M1 is provided by the internal combustion engine 20 on the motor output side 90 via the crankshaft 95. The first torque M1 is introduced into the vibration damping device 15 via the input side 40. During operation of the internal combustion engine 20, the first torque M1 is subjected to rotational irregularities, in particular rotational vibrations. The rotational irregularities cause rumbling and vibrations and are perceived as disturbing by the vehicle user. The flywheel mass 50 attenuates the first component of rotational irregularities by its mass. The first torque M1 is introduced into the damping device 15 via the second connection 100. The first flange part 55 drives the flywheel mass 50 and the third flange part 76. The rib 200 acts on the first end of the energy storage member 75 with a first torque M1. The energy storage element 75 is acted on by the first torque M1 and acts on the actuating element 180 of the second flange part 65 at a second rib arranged offset from the rib 200 in the circumferential direction. The first torque M1 is transmitted to the output side 45 via the second flange part 65 and into the transmission input shaft 130 via the third connection 125. Additionally, the electric machine 25 can be driven via the rotor carrier 150, which can be switched on to operate in the form of a generator, thereby charging the electrical power supply of the motor vehicle.

In a second operating state, which can also be described as an electric-only operating state of drive system 10, further electric machine 26 provides a second torque M2, which second torque M2 acts about rotational axis 16. The second torque M2 is introduced into the transmission input shaft 130. In purely electric operation, torsional vibration damper 60 is therefore inactive.

In a third operating state, the internal combustion engine 20 and at least one of the two electric machines 25, 26 are activated and the first torque M1 and the second torque M2 are added to form the total torque MG in the transmission input shaft 130.

If, during operation of the drive system 10, the damping device 15 rotates about the axis of rotation 16, the energy storage element 75 presses radially outward on the first inner circumferential side 185 (see fig. 2). In this case, the protective hood 70 ensures the radial position of the energy store 75. Furthermore, the axial position of the energy storage means 75 is also determined in a defined manner by the bell-shaped geometric design of the connecting section 195 and the protective hood 70. If the first torque M1 is provided by the internal combustion engine 20 in the first and third operating states, the energy storage element 75 bears against the first inner circumferential side 185 with a partial section 245 of the outer circumferential side 241. By loading the energy storage element 75 and the movement of the protective hood 70 relative to the energy storage element 75, the outer circumferential side 241 rubs against the first inner circumferential side 185 in the subsection 245.

In order to keep the wear on the first inner circumferential side 185 and on the outer circumferential side 241 of the first energy storing element 75 low, the oil 170 is introduced into the housing interior 160 via the passage 145. The oil 170 (symbolically shown by arrows in fig. 1 and 2) flows radially outward based on centrifugal force acting on the oil 170. Here, the oil is guided in the axial direction substantially into the positioning space 175 by the oil ring flow second flange part 65 and via the first connecting section 182. Oil 170 is sprayed radially outward from the second flange member 65 onto the energy storage member 75. The oil 170 which is sprayed on the left, for example from the second flange part 65 or the second connection 100 in the direction of the first end side 85, can be collected by the oil guiding vane 237. The second inner circumferential side 240 of the oil deflector 237 deflects the oil 170 in the direction of the center position of the energy store 75.

The shield 70 collects the outwardly flowing or squirted oil 170 and intercepts the oil 170 in a radial direction in the oil chamber 220. In this case, the partial section 245 is advantageously arranged at least partially, advantageously completely, in the oil chamber 220.

In operation of drive system 10, the interception of oil 170 causes oil level 242 to form in oil chamber 220. The maximum oil level 242 in the oil chamber 220 is defined by the radially outer edge 246 of the through-opening 225. Maximum oil level 242 is shown by the dashed line in fig. 2. The maximum oil level 242 defines a radially inner end portion of the oil chamber 220. In other words, the oil chamber 220 is determined by the positioning of the through-hole 225 in the radial direction.

The frictional contact friction between the outer circumferential side 241 and the first inner circumferential side 185 is particularly small and the wear is particularly low by the oil 170 intercepted in the oil chamber 220, since in the frictional contact friction is minimized by the oil 170 due to the intercepted oil 170. The excess oil 170 enters the collection space 230 via the through-hole 225. The oil 170 flows radially outward along the second end side 105 and is sprayed from there onto the housing 160. The oil 170 flows radially inward on the motor housing 110 and, for example, flows into an oil pan of the vibration damping device 15. From there, the oil (not shown in the drawing) is sucked up and filtered, returned again into the transmission 131 and from there conveyed into the feed channel 140.

The above-described design of the drive system 10 has the advantage that wear between the energy storage element 75 and the protective hood 70 is minimized. Furthermore, the erosion of protective hood 70 and/or energy storage element 75 occurring in the frictional contact is dissipated via oil 170 and carried away from torsional vibration damper 60. This has the advantage that the friction properties of the energy store 75 on the protective cap 70 can be kept constant over the service life of the vibration damping device 15 and in particular increased friction due to wear particles can be avoided.

In this embodiment, the internal combustion engine 20 has an oil circuit 250. Motor oil 255 circulates in oil loop 250 and has different properties than oil 170, such as high temperature inertness and/or lubrication characteristics. By separating the oil circuit 250 of the internal combustion engine 20 from the housing interior 160, it is avoided: the wear particles of the energy storage member 75 and the protective cover 70 enter the oil circuit 250 of the internal combustion engine 20. Furthermore, due to the fluid-separated configuration of the housing interior 160 from the oil circuit 250 of the internal combustion engine 20, the oil 170 can be optimally coordinated with respect to the vibration damping device 15 and the transmission 131. The load of the damper device 15 may be selected regardless of the motor oil 255.

List of reference numerals

10 drive system

15 damping device

16 axis of rotation

20 internal combustion engine

25 electric machine

26 Another electric machine

30 rotor

35 stator

40 input side

45 output side

50 flywheel mass

55 first flange part

60 torsional vibration damper

65 second flange part

70 positioning element

75 energy storage element

76 third flange part

80 first connecting piece

85 first end side

90 motor output side

91 crankshaft flange

95 crankshaft

100 second connecting piece

105 second end side

110 motor shell

115 third end side

120 step part

125 third connecting piece

130 variator input shaft

131 driving device

135 bearing assembly

140 input channel

145 port

150 rotor support

155 casing

160 inner space of the casing

170 oil

175 positioning space

180 operating element

185 first inner circumferential side

190 protective cover

195 connecting section

200 rib

205 fixed end of rib

210 free ends of the ribs

215 end of shield

220 oil chamber

225 via hole

230 collection chamber

235 threading part

236 opening

237 oil guide wing

240 (of the ribs) second inner circumferential side

241 outer circumferential side

242 oil level

246 edge

250 oil circuit of internal combustion engine

255 Motor oil