WO2010037663A2 - Hybrid drive system - Google Patents

Abstract

The invention relates to a hybrid drive system comprising an internal combustion engine having an input shaft (12), an electric machine (14) having a stator (16) and a rotor (20) which is or can be coupled with the input shaft (12) to rotate about a rotational axis (A), and an output shaft (26), preferably a transmission input shaft, which can be driven by the input shaft (12) and/or the rotor (20), further comprising a torsional vibration damper arrangement (28) having a first torsional vibration damper (30) comprising a primary side (43) and a secondary side (34) which can be rotated relative to the primary side (43) about the rotational axis against the effect of a damper fluid arrangement.

Description

 Hybrid drive system

description

The present invention relates to a hybrid lifting system for a vehicle, which comprises an internal combustion engine and an electric machine, which can selectively provide a driving torque for driving a vehicle either individually or in combination. Such a hybrid drive system has a drive shaft, generally the crankshaft of an internal combustion engine, via which the drive torque provided by the internal combustion engine is conducted to an output shaft, for example a transmission input shaft. The electric machine has a stator generally provided with a winding region and a rotor constructed generally with permanent magnets.

In order to reduce the rotational nonuniformities occurring in a drive train in such hybrid drive systems, it is known, for example, to integrate steel spring torsional vibration dampers into the torque transmission path or to generate slippage by defined activation of a disconnect clutch. The decoupling quality provided by steel spring torsional vibration dampers is often insufficient for rotational irregularities occurring in a drivetrain. Generating a slip in the drive train leads to increased energy consumption and thus also increased pollutant emissions. Furthermore, slip control systems are difficult to realize due to the required dynamics.

It is the object of the present invention to provide a hybrid drive system with improved vibration damping functionality.

According to the invention this object is achieved by a hybrid drive A system comprising an internal combustion engine having a drive shaft, an electric machine having a stator and a rotor coupled or rotatable with the drive shaft for rotation about a rotation axis and an output shaft drivable by the drive shaft and / or the rotor, preferably transmission input shaft, further comprising a torsional vibration damper assembly with a first torsional vibration damper with a primary side and a against the Wrikung a damper fluid assembly about the axis of rotation with respect to the primary side rotatable secondary side.

By providing a torsional vibration damper arrangement with a torsional vibration damper operating under the effect of a damper fluid assembly, a significantly improved vibration damping characteristic can be achieved, in particular even if the vibration damping characteristic of a torsional vibration damper arrangement constructed in this way can be adapted to different driving conditions by influencing the fluid pressure in the damper fluid arrangement.

In order to improve the vibration damping behavior even further, the invention further proposes that a second torsional vibration damper is provided with a primary side and against the action of a damper spring assembly about the axis of rotation relative to the primary side rotatable secondary side, wherein it can be provided that the secondary side of the second torsional vibration damper Substantially forms an output region of the torsional vibration damper assembly and the secondary side of the first torsional vibration damper is rotatably connected to the primary side of the second torsional vibration damper.

In the torsional vibration damper arrangement according to the invention, it can be provided that the damper fluid arrangement has at least one Fluid pressure accumulator arrangement and a conveyor arrangement comprises, by which in relative rotation of the primary side relative to the secondary side of the fluid storage pressure in at least one fluid pressure accumulator arrangement can be increased. By increasing the fluid storage pressure in a fluid pressure storage arrangement, a gentle energy reduction or energy storage is realized, whereby the occurrence of excessive torque fluctuations can be effectively counteracted.

In this case, it may be provided, for example, that the at least one fluid pressure accumulator arrangement comprises at least one fluid pressure accumulator unit with fluid which can be conveyed by the conveyor arrangement, preferably substantially incompressible first fluid and an energy store which can be loaded by the first fluid.

In a structurally very simple to implement embodiment, it can be provided that the at least one energy store comprises compressible second fluid.

Depending on the required Schwingungsämpfungscharaktehstik can be further provided that the at least one fluid pressure accumulator unit is provided on the primary side or the secondary side of the first Torsionsschwingungs- damper, wherein in one case the total mass on the primary side is increased, in other cases, the total mass on the secondary side is increased ,

In order to be able to provide equally optimal vibration damping properties via both possible directions of relative rotation between the primary side and the secondary side of the first torsional vibration damper, ie the type of gas spring torsional vibration damper, it is further proposed that two fluid pressure storage arrangements be provided and that upon relative rotation of the primary side with respect to the secondary side in a first direction of relative rotation - A -

the conveyor arrangement increases the fluid storage pressure in a first of the fluid pressure accumulator arrangements, and increases the fluid storage pressure in a second one of the fluid pressure accumulator arrangements in the case of relative rotation of the primary side relative to the secondary side in a second relative direction of rotation opposite to the first relative direction of rotation.

For this purpose, it can be provided, for example, that the conveying arrangement comprises at least one pressure chamber formed between the primary side and the secondary side, the volume of which is variable with relative rotation of the primary side with respect to the secondary side, and at least one connecting volume, via which at least one first fluid displaced at least one pressure chamber charged an energy storage.

In an alternative embodiment, it can be provided that the delivery arrangement comprises a pump arrangement that can be driven by relative rotation of the primary side with respect to the secondary side, which conveys first fluid from one of the fluid pressure accumulator arrangements to the other fluid pressure accumulator arrangement as a function of the relative direction of rotation. In this case, therefore, the conveyor arrangement can be constructed or operate, for example, in the manner of a gear pump with a substantially unlimited range of relative rotation angles between the primary side and the secondary side.

In order to be able to influence the pressure conditions in the first torsional vibration damper in a defined manner in the construction of a hybrid drive system according to the invention, it is further proposed that the first fluid can be supplied via the output shaft to the at least one fluid pressure reservoir arrangement. Alternatively it can be provided that the at least one fluid pressure accumulator arrangement first fluid via a preferably not provided for torque transmission between the drive shaft and the output shaft intermediate shaft can be fed. In order to be able to produce the fluid connection either via the output shaft or the intermediate shaft in a reliable manner, it is further proposed that the drive shaft or intermediate shaft is or can be brought into fluid communication with a source of pressurized fluid via a first rotary feedthrough region and in fluid communication with the at least one via a second rotary feedthrough region Fluid pressure accumulator assembly is.

In this case, the first rotary leadthrough region can be arranged on the internal combustion engine side for fluid intake / fluid delivery. This means that a stator region of the first rotary feedthrough region is positioned so that it can be connected to a continuing line system in the region of or in the direction of the internal combustion engine.

Alternatively it can be provided that the first rotary feedthrough region is arranged on the transmission side for fluid intake / fluid delivery. In this case, therefore, the stator region of the first rotary feedthrough region is open on the transmission side or, if appropriate, arranged in a transmission.

In a further alternative embodiment variant, it can be provided that the first rotary feedthrough region is arranged between the electric machine and the torsional vibration damper arrangement for fluid intake / fluid delivery.

In order to selectively provide a drive torque by the internal combustion engine in the hybrid drive system according to the invention or to provide the internal combustion engine by the electric motor, but not to drive the internal combustion engine, it is further proposed that a disconnect clutch assembly for producing / - interrupting a torque transmission connection between the drive shaft and the Rotor is provided. It can then continue be provided that the Torsionsschwingungsdämpferanordnung is provided in the torque flow from the drive shaft to the output shaft before or after the separation clutch assembly.

The hybrid drive system according to the invention can in principle be constructed such that the torsional vibration damper arrangement is arranged in the torque flow from the drive shaft to the output shaft before or after the electric machine. This means that, depending on which of the various drive system assemblies are arranged on the primary side or the secondary side with respect to the torsional vibration damper arrangement, the respective mass moment of inertia on the primary side and the secondary side is increased and thus defines the vibration damping ratios are influenced.

It can further be provided that the output shaft receives a torque from the drive shaft via a starting assembly, preferably a hydrodynamic coupling device or a wet-running coupling device.

The present invention will be described below in detail with reference to the accompanying drawings. It shows:

Fig. 1 is a principle partial longitudinal sectional view of a hybrid drive system;

FIG. 2 is a cross-sectional view of a gas spring torsional vibration damper; FIG.

FIG. 3 shows a representation corresponding to FIG. 2 of an alternative embodiment of a gas spring torsional vibration damper; FIG.

Fig. 4 is a representation corresponding to FIG. 1 of an alternative designed hybrid drive system;

Fig. 5 is a representation corresponding to Figure 1 of an alternative designed hybrid drive system.

Fig. 6 is a representation corresponding to Figure 1 of an alternative designed hybrid drive system.

7 shows a representation corresponding to FIG. 1 of an alternatively configured hybrid drive system;

Fig. 8 is a representation corresponding to Figure 1 of an alternative designed hybrid drive system.

FIG. 9 is a representation corresponding to FIG. 1 of an alternatively configured hybrid drive system; FIG.

FIG. 10 is a representation corresponding to FIG. 1 of an alternative hybrid drive system; FIG.

Fig. 1 1 is a representation corresponding to Figure 1 of an alternative designed hybrid drive system.

FIG. 12 is a representation corresponding to FIG. 1 of an alternative hybrid drive system; FIG.

Fig. 13 is a representation corresponding to Figure 1 of an alternative designed hybrid drive system.

Fig. 14 is a representation corresponding to FIG. 1 of an alternative designed hybrid drive system. 1 shows a first embodiment of a hybrid drive system 10. This system comprises as essential system areas an unillustrated internal combustion engine with a drive shaft 12 designed as a crankshaft, an electric machine 14 with a stator 16 having a winding area 18, and a rotor 20, the permanent magnets 22 for interaction with the winding region 18 has. As a starting element, the hybrid drive system 10 further comprises a hydrodynamic torque converter 24, via which a torque is transmitted to an output shaft 26 formed, for example, by a transmission input shaft.

In the hydrodynamic torque converter 24, there is provided a torsional vibration damper assembly 28 having a first torsional vibration damper 30 formed like a gas spring torsional vibration damper and a second torsional vibration damper 32 formed like a conventional steel spring torsional vibration damper.

Before the interaction of the various system areas of the hybrid drive system 10 is explained in detail, the structure and functionality of the first torsional vibration damper 30 designed as a gas spring torsional vibration damper will be explained below with reference to FIGS. 2 and 3.

The first torsional vibration damper 30 has, as a secondary side 34, a first housing part 42 formed with side parts 36, 38 and a peripheral part 40. As the primary side 43, the first torsional vibration damper 30 has a second housing part 44 formed substantially radially inside the first housing part 42. As shown in FIG. 2 shows this, the second housing part 44 at an angular distance of 180 ° two radially outwardly extending projections 46, 46 'on. Accordingly, the peripheral part 40 of the first housing part 42 has two radially inwardly extending projections 48, 48 'on. In the circumferential direction, a total of four pressure chambers 50 and 50 'and 52 or 52' are formed between these four projections 46, 48, 46 ', 48'. These pressure chambers 50, 50 ', 52, 52' are combined opposite one another in pairs and bounded in the axial direction by the two side parts 36, 38. The pressure chambers 50, 52, 50 ', 52' are in damper operation with a substantially incompressible first fluid, so for example oil, filled.

Each pressure chamber 50, 50 ', 52, 52' is further associated with a connecting chamber 54, 54 'and 56, 56'. In relative rotation between the primary side 34 and the secondary side 43, for example, the volume of the two pressure chambers 50, 50 'is reduced, while the volume of the two pressure chambers 52, 52' increases. The pressure chambers 50, 50 'which are reduced in their volume displace the first fluid contained therein via openings (not shown) into the respective associated connection chambers 54, 54', so that the fluid pressure correspondingly increases there. In this case, the two connecting chambers 54, 54 'associated fluid pressure accumulator units 58 and the contained therein in the form of a compressible second fluid energy storage 60 are charged. The fluid pressure storage units 58 thus form gas springs, in which the gas acting as an energy store 60 is separated from the first fluid by a respective piston element 62 or possibly a membrane or the like.

It can be seen in FIG. 2 that in each case four such fluid pressure storage units 58 are associated with each connecting chamber 54 or 54 ', while each such fluid pressure storage unit 58 is associated with each connecting chamber 56, 56'. For this purpose, separating elements 63 are provided between the connecting chambers 54, 56, 54 ', 56', which are consecutive in the circumferential direction. Depending on the positioning of these separating elements 63, it is thus possible for the pressure chambers 50, 50 ', 52, 52', which cooperate in pairs, to have a required or desired number of fluid pressure for the pulling operation on the one hand and the pushing operation on the other hand. to allocate memory units 58.

In this embodiment variant shown in Fig. 2 forms each pair of

Pressure chambers 50, 50 'and 52, 52' in conjunction with the respectively associated connection chambers 54, 54 'and 56, 56' and the respective fluid pressure storage units 58 which can be activated thereby each have a fluid pressure storage arrangement 64 or 64 '. During relative rotation between the primary side 43 and the secondary side 34, the fluid storage pressure in each case one of

Fluid pressure accumulator assemblies 64 and 64 'increases, while it decreases in the other ren.

The two pairs of pressure chambers 50, 50 'and 52, 52' form, in conjunction with the respectively associated connection chambers 54, 54 'and 56, 56', a fluid conveying arrangement 65. This ensures that, depending on the relative rotation between the primary side 34 and the secondary side 43 of the first torsional vibration damper 30, the fluid pressure in the two accumulator assemblies 64, 64 'is varied and thus each one of the primary side 34 and the secondary side 43 in the direction of neutral relative rotational position restoring force is generated.

An alternative embodiment of this is shown in Fig. 3. Here, only one fluid pressure accumulator arrangement 64 is provided, for example in association with the two pressure chambers 50, 50 'which are effective in traction mode. There is a single connection chamber 54 which combines these two pressure chambers 50, 50 'with all fluid pressure storage units 58. The two other pressure chambers 52, 52 'are held substantially without pressure, so for example in conjunction with the environment, so that here a damping effect is achieved only in a torque transmission direction, so for example in traction, while reducing the volumes of the two pressure chambers 52, 52 'is opposed to substantially no force due to lack of cooperation with any of the fluid pressure storage units 58. It should be pointed out here that, of course, in the first torsional vibration damper 30, a pump, for example a gear pump, which is effective without rotational angle limitation can also be provided, so that an essentially unlimited relative rotation can take place between the primary side 43 and the secondary side.

In the hybrid drive system 10 shown in FIG. 1, the stator 16 is supported, for example, on an engine block or other stationary assembly. The rotor 20 is connected to the drive shaft 12 via a first connecting plate 70 constructed, for example, of sheet material, with intermediate positioning of an intermediate ring 72. This intermediate ring 72 may be screwed together with the first connecting plate 70 by bolts 74 to the drive shaft 12. The first connecting disc 70 may be connected in its radially outer region with the rotor 20 by riveting.

A second connecting plate 76, which is also constructed of sheet metal, for example, establishes a connection between the rotor 20 and a housing 78 of the hydrodynamic torque converter 24. This connection can be made both with respect to the rotor 20 and with respect to the housing 78 by screwing, riveting or axially elastic elements, both the first connecting disc 70 and the second connecting disc 76 itself due to their elasticity a certain Axialrelativbewegbarkeit between the hydrodynamic torque converter Allow 24 and the drive shaft 12.

The hydrodynamic torque converter 24 is basically of conventional construction and has an impeller 80 on the housing 78. in the

Inside the housing 78, a turbine wheel 82 is arranged. A lock-up clutch 84 provides either over the torsional vibration damper Arrangement 28 a direct mechanical torque transmission connection between the housing 78 and the output shaft 26 ago. For this purpose, an output element 86 of the lock-up clutch 84 is fixedly connected to the primary side 43 of the first torsional vibration damper 30, ie the second housing part 44. The first housing part 42, in particular its side part 38, is fixedly connected to the primary side 88 of the second torsional vibration damper 32 or itself constitutes a region thereof. A secondary side 90 of the second torsional vibration damper 32, which is basically designed as a low-load damper z. B. can be formed for the idle range is formed as a central disk member 92 which has radially inside an output hub 94 and is fixedly connected thereto, which in turn is in torque transmitting engagement with the output shaft 26. For example, the turbine wheel 82 of the hydrodynamic torque converter 24 may be connected to the primary side 88 of the second torsional vibration damper 32 such that the second torsional vibration damper 32 operates not only with the lock-up clutch 84 engaged, but also in torque conversion operation when torque is applied across the turbine wheel 82 is to be guided in the direction of the output shaft.

It should be noted for the sake of completeness that the hydrodynamic torque converter 24 also has a generally designated 96 stator, which is supported via a freewheel assembly on a support hollow shaft, not shown.

In order to supply the pressure chambers 50, 50 ', 52, 52' described above with pressure fluid or to remove pressure fluid therefrom, a rotary feedthrough arrangement, generally designated 94, is provided. This comprises a first rotary feed-through region 96, via which a connection between a pressure fluid source or else a fluid reservoir and an intermediate shaft 98 can be established. A second rotary feedthrough region 100 provides a fluid connection between the intermediate shaft 98 and the second housing part 44 and thus the pressure chambers 50, 50 ', 52, 52 'ago. The intermediate shaft 98 serves to produce the fluid connection, but is not provided to transmit a torque between the drive shaft 12 and the output shaft 26.

The first rotary feedthrough region 96 comprises a stator 102 which, for example, together with the stator 16 of the electric machine 14, can be carried on an engine block or other stationary assembly and is open on the engine side or open for connection to the pressure fluid source or a fluid reservoir. It can be seen that the intermediate ring 72 connected fluid-tight due to its rotatability with the drive shaft 12 by corresponding dynamic seals with respect to the stator 102 and also with respect to the intermediate shaft 98 is.

In the intermediate shaft 98 are formed by the insertion of a sleeve-like insert 104, two coaxial flow channels, one of which establishes the connection to the two pressure chambers 50, 50 'and the other, which is fluid-tight with respect to the former, a connection to the pressure chambers 52, 52 ^' produces. Correspondingly, two channel sections leading to the two coaxial channels in the intermediate shaft 98 are also formed in the stator 102 and the intermediate ring 72, as well as in the second housing part 44 or a sleeve-like component 106 of the second rotary leadthrough region 100 firmly connected thereto this sleeve-like component 106 and the intermediate shaft 98 are provided by dynamic sealing elements for a fluid-tight connection. Since this transition is located in the interior of the housing 78, in the region of the second rotary leadthrough region 100, pressurized fluid exiting, which may be, for example, the same fluid or oil as in the transducer 24, which emerges as a leakage flow through these seals, can be recycled through the converter circuit. The intermediate shaft 98 is mounted with respect to the sleeve-like component 106 and the second housing part 44 via bearings 108, 110, which may for example be designed as rolling element bearings. About an example e- benfalls designed as Wälzkörperlager bearing 1 12, the intermediate shaft 98 is mounted with respect to the output shaft 26. It should be noted that, of course, the two housing parts 42, 44 in particular in the region of the two side parts 36, 38 are supported by appropriate bearings together or are sealed fluid-tight with respect to each other.

In the structure of a hybrid drive system 10 shown in FIG. 1, there is a permanent connection between the rotor 20 of the electric machine 14 and the drive shaft 12. This means that here preferably the electric machine 14 is operated as a support or as an auxiliary in maneuvering a vehicle or also for starting the internal combustion engine can be used. A torque transmission interruption in the drive train can take place in the region of the hydrodynamic torque converter 24 or also in a gear following the torque flow, preferably an automatic transmission.

4, a hybrid drive system 10 is shown, in which a designed in the manner of a conventional dry-running friction clutch separating clutch 120 is provided, through which either a torque connection between the drive shaft not shown here and the rotor 20 of the electric machine 14 can be made or can be interrupted. A trained in the manner of a clutch disc coupling assembly 122 is connected radially inwardly to the intermediate ring 72 and via this in fixed connection with the drive shaft. The rotor 20 of the electric machine 14 forms, with a housing 124 connected to the housing 78 of the hydrodynamic torque converter 24, a clutch housing in which a pressure plate 126 is under the bias of an energy accumulator which is designed, for example, as a diaphragm spring 128 is pressed against the coupling assembly 122. A release mechanism 130 disposed in the radially inner region of the electric machine 14 can actuate the force accumulator 128 against its own bias by pressurizing fluid so that it releases the pressure plate 126 and thereby releases the torque transmission connection between the rotor 20 and the coupling assembly 122. In this state, the torque coupling of the drive shaft to the output shaft 26 is canceled, so that a drive torque can then be supplied exclusively by the electric machine 14. When the disconnect clutch 120 is engaged, the torque transmission connection between the drive shaft and the housing 78 of the hydrodynamic torque converter 24 is established, so that a drive torque can be supplied by the internal combustion engine, possibly assisted by the electric machine 14.

The rotary feedthrough arrangement 94 again comprises the two rotary leadthrough regions 96, 100. The rotary leadthrough region 96 feeds the fluid supplied to the motor side or via the intermediate ring 72 to or from the output shaft 26 replacing the intermediate shaft with its axial end region. The output shaft 26 is formed in its axial end portion as a hollow shaft and has the insert part 104, so that here in the axial end portion of the output shaft 26, the two a connection between the two rotary lead-through areas 96, 100 producing coaxial channels are realized.

With regard to the structure of the torsional vibration damper assembly 28, the embodiment shown in Fig. 4 corresponds to the above-described, so that reference can be made to the relevant embodiments.

In Fig. 5, a hybrid drive system 10 is shown in which by a designed as a wet-running multi-disc clutch clutch 120 optionally a torque transmission connection between the rotor 20 of the here designed as an internal rotor electric machine 14 and the drive shaft, not shown, can be realized. A housing 140 of the disconnect clutch 120 is fixedly connected via a connecting plate 142 and a flex plate, not shown, for rotation with the crankshaft or drive shaft. An output element 144 of the separating clutch 120, which is non-rotatably coupled to an inner disk carrier, is fixedly connected both to the rotor 20 of the electric machine 14 and to the primary side 43 of the first torsional vibration damper 30. Here, the primary side 43 of the first torsional vibration damper 30 now comprises the first housing part 42, while the secondary side 34 comprises the second housing part 44. With this, the primary side 88 of the second torsional vibration damper 32, which may comprise, for example, two cover disk elements here, firmly connected, for example by using a Hirth toothing. A housing 146, which surrounds the second torsional vibration damper 30, is rotatably connected to the first housing part 42 and forms with a housing hub 148 a pump hub which can drive a pressure fluid pump engaging in a transmission or the like. It is thus ensured that regardless of whether a torque is introduced via the internal combustion engine or the electric machine 14, through the housing hub 148, a fluid pump can be permanently driven.

The pressurized fluid supply of the first torsional vibration damper 30 takes place again via the rotary feedthrough arrangement 94 with its first rotary feedthrough region 96 arranged on the motor side with the stator 102, the intermediate shaft 98 and the second rotary feedthrough region 100 lying in the region of the first torsional vibration damper 30.

FIG. 6 shows a hybrid drive system which, with regard to the structural design, largely corresponds to that illustrated in FIG. Reference should therefore be made to the above statements in this regard. One

However, there is a difference in the design of the rotary feedthrough The first rotary feedthrough region 96 is not arranged on the motor side or provided on the motor side for connection to a Fludidruckwelle, but lies axially between the hydrodynamic torque converter 24 and the electric machine 14. The stator 102 of this first rotary leadthrough range, for example, on a transmission bell 150 firmly and establishes fluid communication with the intermediate shaft 98. This in turn establishes a fluid connection with the second housing part 44 of the first torsional vibration damper 30 or the pressure chambers formed therein.

It can be seen in FIG. 6 that here the intermediate shaft 98 is switched into the torque flux. The second connecting disc 76 is connected in its radially inner region to the axial end of the intermediate shaft 98, as well as the radially inner portion of a housing shell 152 of the housing 78 of the hydrodynamic torque converter 24. It is understood that in both rotary lead-through areas 96, 100 sealing elements are provided which ensure that a substantially fluid-tight connection of the various with respect to each other about the rotation axis A rotating assemblies is possible.

FIG. 7 shows an embodiment of a hybrid drive system 10 in which the torque delivered or relayed via the rotor 20 of the electric machine 14 is delivered directly to the primary side 43 of the torsional vibration damper arrangement 28, which here only includes the first torsional vibration damper 30 becomes. Via the secondary side 34 or the second housing part 44, which is here formed with an axial or wave-like extension 160, the torque is forwarded to any starting element 162. This may be a hydrodynamic torque converter, a wet-running clutch arrangement, a fluid coupling or the like include.

The rotary feedthrough assembly 94 includes only a single rotary diameter guiding region with a stator 164, which is arranged surrounding the shaft-like extension region of the second housing part 44. This shaft-like extension portion 160 thus forms the rotor of the rotary leadthrough assembly 94. This rotary leadthrough assembly 94 is formed with double seals, which consist of pressure seals and volumetric flow seals, and is thus oil-tight. This embodiment is thus particularly suitable in connection with manual transmissions that have no oil supply.

In Fig. 8, an embodiment is shown, which essentially establishes a connection between the embodiment shown in Fig. 7 and the embodiment shown in Fig. 4. Here, a dry-running friction clutch incorporated in the torque flow is provided as the separating clutch 120. A torque coupling of the intermediate ring 72 and thus of the drive shaft to the rotor 20 of the electric machine 14 or also the primary side 43 of the first torsional vibration damper or the torsional vibration damper arrangement 28 can optionally be realized via these.

With regard to the structure of the separating clutch 120 and also of the first torsional vibration damper 30, reference is made to the above statements.

In all of the previously explained embodiments of a hybrid drive system, it is provided that the torsional vibration damper arrangement 28 is positioned in the torque flow between the drive shaft 12 and the output shaft 26 after the electric machine 14. FIG. 9 shows a hybrid drive system 10 in which the torsional vibration damper arrangement 28 with its first torsional vibration damper 30 is positioned in torque flow in front of the electric machine 14.

The primary side 43 here comprises the first housing part 42 with its two Side parts 36, 38 and the fluid pressure storage units 58 carried thereon. For example, via these fluid pressure storage units 58 and a connecting arrangement 170 fixed thereto, a connection to the drive shaft (not shown) can be realized via a flexible plate or the like. The second housing part 44, which provides the secondary side 34, is connected with its wave-like extension 160 and, for example, the two connecting disks 70, 76 to the input area 172 of a separating clutch 120 designed as a wet-running multi-plate clutch. This entrance area 172 may comprise an inner disc carrier with the lamellae carried thereon. The exit region 174 forms a housing with outer disks carried thereon. This housing also simultaneously forms the rotor 20 of the electric machine 14 with the permanent magnets 22 carried thereon, which are surrounded by the winding area 18 of the stator 16. The output shaft 26 is coupled to the output region 174 of the separating clutch 120 and thus also the rotor 20 of the electric machine 24.

The rotary feedthrough assembly 94 may again be formed as previously explained with reference to FIG. 7. Their stator 164 may also be formed as part of a transmission housing, for example.

The pressurized fluid supply to the disconnect clutch 120 may be from a transmission or also from the engine side. Of course, it is also possible to design the input area 172 as a housing and to use the inner disk carrier for forwarding the torque to the output shaft 26.

In Fig. 10, an embodiment of a hybrid drive system 10 is shown, which largely corresponds to that shown in Fig. 1. One difference, however, is that the supply of the first torsional vibration damper 30 with pressurized fluid takes place via the output shaft 26. This is designed as a hollow shaft with the sleeve-like insert part 98 and thus provides two channels over which the two pairs of pressure chambers can be supplied. The first rotary leadthrough region, which is not recognizable in FIG. 10, then lies, for example, within an automatic transmission, where the pressure fluid can be introduced into the output shaft 26 or fluid can be released therefrom.

In this embodiment, since the torsional vibration damper 30 having the second rotary leadthrough portion 100 is entirely within the housing 78 of the hydrodynamic torque converter 74, there is no problem in the occurrence of fluid leakage as it can be dissipated through the circuit constructed for the hydrodynamic torque converter 24.

It should be noted that in the embodiment shown in Fig. 10, of course, in the embodiment of Fig. 1 or similarly designed variants, the second torsional vibration damper 32 can be omitted and thus only the first torsional vibration damper 30 be effective in the manner of a dual mass flywheel can. In this case, the turbine wheel 82 can also be connected to the primary side of the first torsional vibration damper 30 in order to be able to provide vibration damping functionality even in torque conversion operation.

In the embodiment of a hybrid drive system shown in FIG. 11, the torque commanded or relayed via the rotor 20 of the electric machine 14 is conducted again to the first housing part 42 of the first torsional vibration damper 30, which housing part 42 is essentially the primary side 43 of the first Torsionsschwingungsdämpfers 30 provides. The second housing part 44 transmits the torque further to a wet-running multi-plate clutch used here as starting element 162. This is accommodated in a housing 146 provided on the primary side 43 of the first torsional vibration damper 30, which, as rangehend already explained with reference to FIG. 5, with a housing hub 148 can drive a arranged in a transmission fluid pump.

An outer disk carrier 182 of the wet-running multi-plate clutch is connected to the second housing part 44, that is to say the secondary side 34 of the first torsional vibration damper 30, for example via Hirtzahnnung or the like. An inner disk carrier 184 is connected via the second torsional vibration damper 32 to an output hub 94, which realizes the rotationally fixed coupling to the output shaft 26. In this embodiment, too, the supply of the first torsional vibration damper 30 with pressurized fluid takes place via this output shaft 26, as has been explained above with reference to FIG. 10. The fluid supply of the wet-running multi-plate clutch for cooling the slats on the one hand and for actuation on the other hand via fluid passages formed radially outside the output shaft 26.

The embodiment of a hybrid drive system shown in FIG. 12 represents a connection between the structure described above with reference to FIG. 11 with a wet-running multi-disc clutch as a starting element 162 following the torque flow to the first torsional vibration damper 30 and that explained with reference to FIG. 4 Embodiment in which a separating clutch 120 can selectively realize a connection between the rotor 20 of the electric machine 14 and the drive shaft, which is not shown here. The via this separating clutch 120, which is designed here as a dry-running friction clutch, forwarded torque reaches the primary side 43 of the first torsional vibration damper 30, which is formed here again with the first housing part 42. The fluid supply of the first torsional vibration damper 30 via the output shaft 26, as previously explained several times.

The embodiment shown in FIG. 13 represents a constructive connection. The rotor 20 of the electric machine 14 can be selectively brought by actuation of the separating clutch 120 in connection with the drive shaft. The guided through the separating clutch 120 to the primary side 43 of the first torsional vibration damper 30 torque is passed through the secondary side 34, here formed with the second housing part 44, on the primary side 88 of the second torsional vibration damper 32. This is again arranged in the housing 146, which is rotatably coupled to the primary side 43 of the first torsional vibration damper 30 and thus provides for a drive possibility for a fluid pump.

The first torsional vibration damper 30 is supplied with pressure fluid via the output shaft 26 in order to be able to influence the vibration damping characteristic by adjusting the pressure conditions in the various pressure chambers.

As a starting element, an integrated example in a transmission clutch can be used, which is used in the design of the transmission as an automatic transmission also for activating or deactivating one or more Gangstu- fen.

5, it is possible to provide additional mass parts 190, 192 on the primary side 88 of the second torsional vibration damper 30, of which, for example, the mass part 192 also implements the connection to the secondary side 34 of the first torsional vibration damper 30 can, in order to influence the vibration damping behavior in this way.

FIG. 14 shows an embodiment based largely on the embodiment shown in FIG. 9 and described with reference to FIG. 9. However, it can be seen here that the input area 172 of the as wet-running multi-plate clutch formed separating clutch 120, for example, via the two connecting discs 70, 76 connected to the second housing part 44, comprising a housing of the wet-running multi-plate clutch. The output region 174 includes the inner disk carrier, which is fixedly connected to a driven hub member 94. At this output hub member 94, with which the output shaft, not shown, can be brought into rotationally fixed engagement, and the rotor 20 of the here designed as an internal rotor electric machine 14 is firmly worn. This means that, similarly as in the embodiment according to FIG. 9, when the separating clutch 120 is disengaged, the electric machine 14 is coupled to the further drive train without vibration damping functionality. That is, the Torsionsschwingungsdämpferanordnung 28 can here only be effective vibration damping with their first torsional vibration damper 30 when the separating clutch 120 is engaged, in principle so the internal combustion engine, the drive shaft is coupled to the first torsional vibration damper 30, is in operation.

Previously, various embodiments of hybrid drive systems have been explained in which a Torsionsschwingungsdämpferan- order is integrated with a gas spring torsional vibration damper. This results in a variety of advantages in the drive state. Thus, for example, due to the very high moments of inertia provided by the electric machine, in particular when this is designed as an external rotor, in conjunction with the comparatively low rigidity of a gas spring torsional vibration damper, an excellent vibration decoupling can be achieved.

In embodiments in which a separating clutch is provided for selectively coupling and uncoupling the internal combustion engine, an additional rotary feedthrough region can provide the advantage that the gas spring torsional vibration damper can be arranged at any axial positioning. Also, if necessary, for the gas spring Torsionsschwingungsdämpfer be shared with a hydraulic supply used for the separating clutch. Likewise, a leakage return provided for the gas spring torsional vibration damper can also be used for the separating clutch.

Since a higher voltage level can be achieved in hybrid drive systems due to the provision of the electric machine, it is also possible to provide an on-demand electrically driven oil pump for supplying the gas spring torsional vibration damper. This means that it is not necessary to access the oil pump, which is present for example in an automatic transmission. With such an additional or external pressurized fluid supply, it is furthermore possible to construct a hybrid drive system with any type of separating clutch for manual transmissions, where a fluid supply does not take place or can take place via a transmission input shaft, but via an additional rotary feedthrough.

The space available within an electric machine, for example, the space available inside the electric machine stator, can be used, for example, for positioning a rotary feedthrough area. Since this electric machine stator is generally cooled by water cooling, the seals of the rotary feedthrough area can be thermally relieved. The existing in the electric machine bearings can equally be used for the arranged in their range rotary feedthrough area, so that created by the common seal and lubrication a further space advantage especially by axial space minimization.

In the starting state, as well as in the driving state, the gas spring Torsionsschwingungsdämpfer can be effective at least briefly to provide a damping function or elasticity, which reduces the control effort when turning the electric machine. This is because that the torque increase of the electric machine can be passed through the gas spring torsional vibration damper on the drive train, so that when switching from electric to internal combustion engine drive or vice versa torque shocks can be avoided or can be influenced to achieve a defined goal of the powertrain. Of course, such damping also has an effect on the coupling behavior of a separating clutch, so that the clutch picking can be suppressed.

Claims

claims A hybrid drive system comprising an internal combustion engine having a drive shaft (12), an electric machine (14) having a stator (16) and a rotor (20) coupled to or coupled to the drive shaft (12) for rotation about an axis of rotation (A) driven by the drive shaft (12) and / or the rotor (20) driven output shaft (26), preferably transmission input shaft, further comprising a Torsionsschwingungsdämpferanordnung (28) with a first Torsi- onsschwingungsdämpfer (30) with a primary side (43) and against the effect a damper fluid arrangement about the axis of rotation with respect to the primary side (43) rotatable secondary side (34). 2. Hybrid drive system according to claim 1, characterized in that the Torsionsschwingungsdämpferan- Regulation (28) comprises a second torsional vibration damper (30) comprising a primary side (88) and against the action of a damper spring assembly about the axis of rotation (A) with respect to the primary side (88) rotatable secondary side (90). 3. Hybrid drive system according to claim 2, characterized in that the secondary side (90) of the second torsional vibration damper (32) essentially forms an output region of the torsional vibration damper arrangement (28) and the secondary side (34) of the first torsional vibration damper (30) with the primary side (FIG. 88) of the second torsional vibration damper (32) is rotatably connected. 4. hybrid drive system according to one of claims 1 to 3, characterized in that the damper fluid arrangement at least one fluid pressure accumulator assembly (64, 64 ') and a För- deranordnung (65), by which during relative rotation of the primary side (43) with respect to the secondary side (34) of the fluid storage pressure in at least one fluid pressure accumulator assembly (64, 64 ') can be increased. 5. Hybrid drive system according to claim 4, characterized in that the at least one fluid pressure accumulator assembly (64, 64 ') at least one fluid pressure accumulator unit (58) by the conveyor assembly (65) conveyable, preferably substantially incompressible first fluid and a loadable by the first fluid energy storage (60). 6. Hybrid drive system according to claim 5, characterized in that the at least one energy store (60) comprises compressible second fluid. 7. Hybrid drive system according to claim 5 or 6, characterized in that the at least one fluid pressure storage unit (58) on the primary side (43) or the secondary side (34) of the first torsional vibration damper (30) is provided. 8. Hybrid drive system according to one of claims 4 to 7, characterized in that two fluid pressure accumulator assemblies (64, 64 ') are provided and that upon relative rotation of the primary side (43) with respect to the secondary side (34) in a first relative direction of rotation, the conveyor assembly, the fluid storage pressure (65) increases in a first of the fluid pressure accumulator arrangements (64, 64 ') and upon relative rotation of the primary side (43) with respect to the secondary side (34) in a second relative direction of rotation opposite to the first relative direction of rotation increases the fluid storage pressure in a second one of Fluid pressure accumulator assemblies (64, 64 ') increases. 9. hybrid drive system according to one of claims 4 to 8, characterized in that the conveying arrangement (65) at least one between the primary side (43) and the secondary side (34) formed pressure chamber (50, 50 ', 52, 52'), whose Volume with relative rotation of the primary side (43) with respect to the secondary side (34) is variable, and at least one connecting volume (54, 54 ', 56, 56') comprises, via which from the at least one pressure chamber (50, 50 ', 52 , 52 ') displaced first fluid at least one energy store (60) loaded. 10. Hybrid drive system according to claim 8, characterized in that the conveying arrangement (65) comprises a by relative rotation of the primary side (43) with respect to the secondary side (34) drivable pump arrangement which, depending on the relative rotational direction first fluid from one of Fluiddruckspeichera- arrangements to the other Fluid pressure accumulator arrangement promotes. 1 1. Hybrid drive system according to one of claims 4 to 10, characterized in that the at least one Fluiddruckspei- cheranordnung (64, 64 ') first fluid via the output shaft (26) can be fed. 12. Hybrid drive system according to one of claims 4 to 10, characterized in that the at least one Fluiddruckspei- cheranordnung (64, 64 ') first fluid via a preferably not to Torque transmission between the drive shaft (12) and the output shaft (26) provided intermediate shaft (98) can be fed. 13. Hybrid drive system according to claim 1 1 or 12, characterized in that the drive shaft (12) or intermediate shaft (98) via a first rotary feedthrough region (96) is in fluid communication with a source of pressurized fluid or can be brought and over a second rotary feedthrough region (100) is in fluid communication with the at least one fluid pressure accumulator assembly (64, 64 '). 14. Hybrid drive system according to claim 13, characterized in that the first rotary feedthrough area (96) is arranged on the internal combustion engine for fluid intake / fluid delivery. 15. Hybrid drive system according to claim 13, characterized in that the first rotary feedthrough area (96) is arranged on the transmission side for fluid intake / fluid delivery. 16. Hybrid drive system according to claim 13, characterized in that the first rotary feedthrough region (96) is arranged between the electric machine (14) and the torsional vibration damper arrangement (28) for fluid intake / fluid delivery. A hybrid drive system according to any one of claims 1 to 16, characterized in that a disconnect clutch assembly (120) is provided for establishing / interrupting a torque transmitting connection between the drive shaft (12) and the rotor (20). 18. Hybrid drive system according to claim 17, characterized in that the Torsionsschwingungs- damper assembly (28) in the torque flow from the drive shaft (12) to the output shaft (26) in front of the separating clutch assembly (120) is provided. 19. Hybrid drive system according to claim 17, characterized in that the torsional vibration Damper assembly (28) is provided in the torque flow from the drive shaft (12) to the output shaft (26) after the disconnect clutch assembly (120). 20. Hybrid drive system according to one of claims 1 to 19, characterized in that the Torsionsschwingungs- damper assembly (28) in the torque flow from the drive shaft (12) to the output shaft (26) in front of the electric machine (14) is arranged. 21. Hybrid drive system according to one of claims 1 to 19, characterized in that the Torsionsschwingungs- damper assembly (28) in the torque flow from the drive shaft (12) to the output shaft (26) after the electric machine (14) is arranged. 22. Hybrid drive system according to one of claims 1 to 21, characterized in that the output shaft (26) receives a torque from the drive shaft (12) via a starting assembly (162), preferably hydrodynamic coupling device (24) or wet-running coupling device.