DE102008050054A1 - Hybrid drive system - Google Patents

Abstract

A hybrid propulsion system includes an internal combustion engine having a drive shaft (12), an electric machine (14) having a stator (16) and a rotor (20) coupled or coupleable to the drive shaft (12) for rotation about an axis of rotation (A) and one of Drive shaft (12) and / or the rotor (20) drivable output shaft (26), preferably transmission input shaft, further comprising a Torsionsschwingungsdämpferanordnung (28) with a first torsional vibration damper (30) having a primary side (43) and against the action of a damper fluid assembly to the Rotary axis with respect to the primary side (43) rotatable secondary side (34).

Description

The The present invention relates to a hybrid drive system for a vehicle, which comprises an internal combustion engine and an electric machine, which either individually or in combination a drive torque for Drive can provide a vehicle. Such a hybrid drive system has a drive shaft, generally the crankshaft of an internal combustion engine, up, over which is the drive torque provided by the internal combustion engine to an output shaft, for example a transmission input shaft, is directed. The electric machine generally has one a winding area provided stature and one in general built with permanent magnets rotor.

Around in such hybrid propulsion systems that in a drive train occurring rotational irregularities to reduce, for example, it is known, steel spring torsional vibration in the torque transmission einzugliedern, or by defined control of a separating clutch to create a slip. The decoupling quality provided by steel spring torsional vibration dampers is for the in Driveline occurring rotational irregularities often insufficient. Generating a slip in the drive train leads to increased energy consumption and thus also an elevated one Emissions. Furthermore, slip control systems are due to the required Dynamics difficult to realize.

It The object of the present invention is a hybrid propulsion system with improved vibration damping functionality.

According to the invention this Task solved by a hybrid drive system comprising an internal combustion engine with a drive shaft, an electric machine with a stator and a coupled to the drive shaft for rotation about a rotation axis or coupling rotor and one of the drive shaft and / or the rotor drivable output shaft, preferably transmission input shaft, further comprising a torsional vibration damper assembly having a first torsional vibration damper with a primary page and one against the action of a damper fluid assembly around the Rotary axis with respect the primary side rotatable secondary side.

By providing a Torsionsschwingungsdämpferanordnung with an under the effect of a damper fluid attachment working torsional vibration damper a significantly improved vibration damping characteristic is achieved, In particular, even if the vibration damping characteristic of a constructed torsional vibration damper arrangement by influencing the fluid pressure in the damper fluid assembly to different driving conditions can be adjusted.

Around the vibration damping behavior yet is to be further improved, the invention further proposes that a second torsional vibration damper is provided with a primary side and one against the action of a damper spring assembly around the Rotary axis with respect the primary side rotatable secondary side, wherein it can be provided that the secondary side of the second torsional vibration damper in Essentially an output range of the torsional vibration damper assembly forms and the secondary side of the first torsional vibration damper with the primary side of the second torsional vibration damper rotatably connected is.

at the torsional vibration damper assembly according to the invention it can be provided that the damper fluid arrangement at least one fluid pressure accumulator arrangement and a conveyor arrangement comprising, by relative rotation of the primary side relative to the secondary side the fluid storage pressure in at least one fluid pressure accumulator arrangement can be increased is. By the increase the fluid storage pressure in a fluid pressure accumulator arrangement realized a gentle energy reduction or energy storage, thereby avoiding excessive torque fluctuations can be effectively counteracted.

there For example, it may be provided that the at least one fluid pressure accumulator arrangement at least one fluid pressure storage unit having through the conveyor assembly of recoverable, preferably substantially incompressible first fluid and a comprises energy storage loadable by the first fluid.

at a structurally very simple to implement embodiment can be provided that the at least one energy storage compressible second fluid.

ever according to required vibration damping characteristic can be further provided that the at least one fluid pressure accumulator unit the primary side or the secondary side of the first torsional vibration damper is provided, in which case the total mass on the primary side is increased, in other cases, the total mass on the secondary side is increased.

To use both possible relative directions of rotation between the primary side and the secondary Side of the first torsional vibration damper, so the built-up like a gas spring Torsionsschwingungsdämpfers equally provide optimal vibration damping properties, it is further proposed that two fluid pressure accumulator arrangements are provided and that upon relative rotation of the primary side relative to the secondary side in a first relative direction of rotation, the conveyor assembly fluid pressure in a first of the fluid pressure accumulator assemblies increases and upon relative rotation of the primary side relative to the secondary side in a first relative rotational direction opposite second relative rotational direction increases the fluid storage pressure in a second of the fluid pressure accumulator assemblies.

For this For example, it can be provided that the conveyor arrangement has at least one between the primary page and the secondary side formed pressure chamber whose volume during relative rotation the primary side in terms of the secondary side variable is, as well as at least one connection volume comprises, over which at least one of the at least one pressure chamber displaced first fluid charged an energy storage.

at an alternative embodiment may be provided that the conveyor assembly a by relative rotation of the primary side regarding the secondary side drivable pumping arrangement comprises, which depending on the relative direction of rotation first fluid from one of the fluid pressure accumulator assemblies to the other Fluid pressure accumulator arrangement promotes. So here is the conveyor assembly for example, in the manner of a gear pump with essentially unlimited Relative rotation angle range between the primary side and the secondary side constructed to be or work.

Around in the structure according to the invention a hybrid drive system that defines the pressure ratios defined in the first torsional vibration damper to be able to It is further proposed that the at least one fluid pressure accumulator arrangement first fluid over the output shaft is fed. Alternatively it can be provided that the at least one fluid pressure accumulator arrangement first fluid over a preferably not for torque transmission between the drive shaft and the output shaft provided intermediate shaft can be fed.

Around the fluid connection either over the output shaft or the intermediate shaft in a reliable manner to be able to produce is further proposed that the drive shaft or intermediate shaft via a first rotary feedthrough area is in fluid communication with a source of pressurized fluid or can be brought is and about a second rotating passage area in fluid communication with the at least one fluid pressure accumulator assembly stands.

there may be the first rotary feedthrough area internal combustion engine side arranged for fluid intake / fluid delivery be. This means that a stator area of the first rotating passage area is positioned so that it is in the area of or towards the Internal combustion engine to be connected to a continuing line system can.

alternative can be provided that the first rotary feedthrough area gearbox side is arranged for fluid intake / fluid delivery. In this case is that is, the stator region of the first rotary feedthrough region on the transmission side for connection open or possibly arranged in a transmission.

at a further alternative embodiment variant can be provided be that the first rotary feedthrough area between the electric machine and the torsional vibration damper assembly is arranged for fluid intake / fluid delivery.

Around in the hybrid drive system according to the invention optionally to provide a drive torque by the internal combustion engine or when the internal combustion engine is deactivated by the electric machine to provide, but not drive the internal combustion engine with to have to, It is further proposed that a disconnect clutch assembly for Manufacture / -Unterbrechen a torque transmission connection is provided between the drive shaft and the rotor. It can then be further provided that the Torsionsschwingungsdämpferanordnung in the torque flow from the drive shaft to the output shaft before or is provided after the separating clutch arrangement.

The Hybrid drive system according to the invention can basically be constructed so that the torsional vibration damper assembly in the torque flow from the drive shaft to the output shaft before or after the electric machine is arranged. This means that, depending on which of the different ones Drive system modules on the primary side or secondary side in terms of the torsional vibration damper assembly are arranged, the respective mass moment of inertia on the primary side or the secondary side elevated and thus defines the vibration damping ratios are influenced.

Further can be provided that the output shaft has a torque of the drive shaft over a start-up assembly, preferably hydrodynamic coupling device or wet-running coupling device receives.

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

1 a schematic partial longitudinal sectional view of a hybrid drive system;

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

3 one of the 2 corresponding representation of an alternative embodiment of a gas spring torsional vibration damper;

4 one of the 1 corresponding representation of an alternative designed hybrid drive system;

5 one of the 1 corresponding representation of an alternative designed hybrid drive system;

6 one of the 1 corresponding representation of an alternative designed hybrid drive system;

7 one of the 1 corresponding representation of an alternative designed hybrid drive system;

8th one of the 1 corresponding representation of an alternative designed hybrid drive system;

9 one of the 1 corresponding representation of an alternative designed hybrid drive system;

10 one of the 1 corresponding representation of an alternative designed hybrid drive system;

11 one of the 1 corresponding representation of an alternative designed hybrid drive system;

12 one of the 1 corresponding representation of an alternative designed hybrid drive system;

13 one of the 1 corresponding representation of an alternative designed hybrid drive system;

14 one of the 1 corresponding representation of an alternative designed hybrid drive system.

The 1 shows a first embodiment of a hybrid drive system 10 , This comprises as essential system areas an internal combustion engine, not shown, with a drive shaft designed as a crankshaft 12 , an electric machine 14 with a stator 16 that has a winding area 18 and a rotor 20 , the permanent magnets 22 for interaction with the winding area 18 having. As a starting element, the hybrid drive system 10 a hydrodynamic torque converter 24 on, via the torque on an example formed by a transmission input shaft output shaft 26 is transmitted.

In the hydrodynamic torque converter 24 is a torsional vibration damper assembly 28 with a first torsional vibration damper designed in the manner of a gas-spring torsional vibration damper 30 and a second torsional vibration damper formed like a conventional steel spring torsional vibration damper 32 intended.

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

The first torsional vibration damper 30 indicates as secondary side 34 one with side parts 36 . 38 and a peripheral part 40 trained first housing part 42 on. As a primary page 43 has the first torsional vibration damper 30 a substantially radially inward of the first housing part 42 trained second housing part 44 on. As the 2 this shows, 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 two radially inwardly extending projections 48 . 48 ' on. In the circumferential direction are between these four projections 46 . 48 . 46 ' . 48 ' a total of four pressure chambers 50 respectively. 50 ' and 52 respectively. 52 educated. These pressure chambers 50 . 50 . 52 . 52 ' are lying opposite each other in pairs and in the axial direction through the two side parts 36 . 38 limited. The pressure chambers 50 . 52 . 50 ' . 52 ' are in damper operation with a substantially incompressible first fluid, so for example oil, filled.

Every pressure chamber 50 . 50 ' . 52 . 52 ' is still a connection chamber 54 . 54 ' respectively. 56 . 56 ' assigned. With relative rotation between the primary side 34 and the secondary side 43 For example, the volume of the two pressure chambers 50 . 50 ' decreases while the volume of the two pressure chambers 52 . 52 ' increases. The reduced in their volume pressure chambers 50 . 50 ' displace that in it contained first fluid via openings not shown in the respective associated connection chambers 54 . 54 ' , so that there correspondingly increases the fluid pressure. In this case, the two connecting chambers 54 . 54 ' associated fluid pressure storage units 58 or the energy store formed therein in the form of a compressible second fluid 60 loaded. The fluid pressure storage units 58 So form gas springs, in which as energy storage 60 effective gas from the first fluid through a respective piston element 62 or optionally a membrane or the like is separated.

One recognizes in the 2 that every connection chamber 54 respectively. 54 ' four such fluid pressure storage units, respectively 58 are assigned during each connection chamber 56 . 56 ' each such fluid pressure storage unit 58 assigned. For this purpose, between the circumferentially successive connecting chambers 54 . 56 . 54 ' . 56 ' separators 63 intended. Depending on the positioning of these separators 63 So it is possible, the pairwise cooperating pressure chambers 50 . 50 ' . 52 . 52 ' a required for the train operation on the one hand or the overrun operation on the other hand or desired number of fluid pressure storage units 58 assigned.

At this in 2 shown embodiment variant forms each pair of pressure chambers 50 . 50 ' respectively. 52 . 52 ' in conjunction with the respective associated connection chambers 54 . 54 ' respectively. 56 . 56 ' and thereby each activatable fluid pressure storage units 58 each a fluid pressure accumulator assembly 64 respectively. 64 ' , With relative rotation between the primary side 43 and the secondary side 34 the fluid storage pressure in each one of the fluid pressure accumulator assemblies 64 respectively. 64 ' increases while decreasing in the other.

The two pairs of pressure chambers 50 . 50 ' and 52 . 52 ' form in conjunction with the respective associated connection chambers 54 . 54 ' respectively. 56 . 56 ' a fluid conveying arrangement 65 , This ensures that, depending on the relative rotation between the primary side 34 and 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 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 in 3 shown. Here is only a fluid pressure accumulator arrangement 64 for example, in association with the two effective in train pressure chambers 50 . 50 ' intended. There is a single connection chamber 54 which these two pressure chambers 50 . 50 ' with all fluid pressure storage units 58 combined. The other two pressure chambers 52 . 52 ' are held substantially unpressurized, so for example in conjunction with the environment, so that here a damping effect is achieved only in a torque transmission direction, ie for example in train operation, while reducing the volumes of the two pressure chambers 52 . 52 ' in the absence of interaction with any of the fluid pressure storage units 58 essentially no force is opposed.

It should be noted here that, of course, in the first torsional vibration damper 30 as a fluid conveying arrangement 65 It is also possible to provide a pump which is effective without an angle of rotation limitation, for example a gear pump, so that it can be provided between the primary side 43 and the secondary side 34 a substantially unlimited relative rotation can take place.

In the in the 1 shown hybrid drive system 10 is the stator 16 For example, worn on an engine block or other stationary assembly. The rotor 20 is about an example of sheet metal constructed first connecting disc 70 with intermediate positioning of an intermediate ring 72 to the drive shaft 12 tethered. This intermediate ring 72 can work together with the first connecting disc 70 by bolt 74 to the drive shaft 12 can be screwed on. The first connection disc 70 can in its radially outer area with the rotor 20 be connected by riveting.

A second, for example, also made of sheet metal connecting disc 76 provides a connection between the rotor 20 and a housing 78 of the hydrodynamic torque converter 24 ago. This connection can both in terms of the rotor 20 as well as regarding the case 78 be done by screwing, riveting or axially elastic elements, wherein both the first connection disc 70 as well as the second connecting disc 76 even due to their elasticity, some axial relative movability between the hydrodynamic torque converter 24 and the drive shaft 12 allow.

The hydrodynamic torque converter 24 is basically of conventional construction and has the housing 78 a pump wheel 80 on. Inside the case 78 is a turbine wheel 82 arranged. A lockup clutch 84 provides optional arrangement on the torsional vibration damper 28 a direct mechanical torque transfer connection between the housing 78 and the output shaft 26 ago. For this purpose is an initial element 86 the lockup clutch 84 fixed to the primary side 43 of the first torsional vibration damper 30 So the second Ge casing part 44 connected. The first housing part 42 , in particular its side part 38 , is with the primary page 88 of the second torsional vibration damper 32 firmly connected or itself represents a range of the same. A secondary side 90 of the second torsional vibration damper 32 , the principle as a low-load damper z. B. may be formed for the idle area is as a central disk element 92 formed, the radially inner an output hub 94 has or is firmly connected, in turn, in torque transmitting engagement with the output shaft 26 stands. The turbine wheel 82 of the hydrodynamic torque converter 24 for example, to the primary page 88 of the second torsional vibration damper 32 be tethered so that the second torsional vibration damper 32 not only when the lock-up clutch is engaged 84 is effective, but also in torque conversion mode when a torque across the turbine wheel 82 is to be led in the direction of the output shaft.

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

To the above-described pressure chambers 50 . 50 ' . 52 . 52 ' to supply with pressurized fluid or dissipate pressure fluid thereof is a generally with 94 designated rotary feedthrough arrangement provided. This comprises a first rotary feedthrough area 96 , via which a connection between a pressure fluid source or else a fluid reservoir and an intermediate shaft 98 can be produced. A second rotary feedthrough area 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 establish the fluid connection, but is not intended to be between the drive shaft 12 and the output shaft 26 to transmit a torque.

The first rotary feedthrough area 96 includes a stator 102 , for example, together with the stator 16 the electric machine 14 may be worn on an engine block or other stationary assembly and open on the motor side or for connection to the pressure fluid source or a fluid reservoir is open. The in the stator 102 formed fluid channels lead through the intermediate ring 72 continue to the intermediate shaft 98 , It can be seen that the intermediate ring 72 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 connected fluid-tight.

In the intermediate shaft 98 are by inserting a sleeve-like insert 104 formed two coaxial flow channels, one of which the connection to the two pressure chambers 50 . 50 ' produces and the other, which is fluid-tight with respect to the former, a connection to the pressure chambers 52 . 52 ' manufactures. Corresponding are also in the stator 102 and the intermediate ring 72 two to the two coaxial channels in the intermediate shaft 98 leading channel sections formed, as well as in the second housing part 44 or a sleeve-like component firmly connected thereto 106 of the second rotating passage area 100 , Also in the transition between this sleeve-like component 106 and the intermediate shaft 98 is provided by dynamic sealing elements for a fluid-tight connection. Because of this transition inside the case 78 can lie in the area of the second rotary feedthrough area 100 exiting pressure fluid, which may be, for example, the same fluid or oil, as in the converter 24 , which leaks as leakage current through these seals, are recycled through the converter circuit.

The intermediate shaft 98 is over camp 108 . 110 , which may be formed for example as a roller bearing, with respect to the sleeve-like component 106 or the second housing part 44 stored. By way of example, also designed as Wälzkörperlager bearing 112 is the intermediate shaft 98 with respect to the output shaft 26 stored. It should be noted that, of course, the two housing parts 42 . 44 especially in the area of the two side parts 36 . 38 are supported by respective bearings together or are sealed by sealing arrangements fluid-tight with respect to each other.

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

In the 4 is a hybrid drive system 10 shown in which a formed in the manner of a conventional dry-running friction clutch separating clutch 120 is provided, by which optionally a torque connection between the drive shaft, not shown here and the rotor 20 the electric machine 14 can be made or can be interrupted. A formed in the manner of a clutch disc coupling assembly 122 is radially inward to the intermediate ring 72 Tied and above this in firm connection with the drive shaft. The rotor 20 the electric machine 14 forms with one to the housing 78 of the hydrodynamic torque converter 24 connected housing 124 a clutch housing in which a pressure plate 126 under the bias of an example designed as a diaphragm spring force accumulator 128 against the coupling assembly 122 pressed. A in the radially inner region of the electric machine 14 arranged release mechanism 130 can by Druckfluidbeaufschlagung the energy storage 128 operate against its own bias, so that this the pressure plate 126 releases and thereby the torque transmission connection between the rotor 20 and the coupling assembly 122 will be annulled. In this state, the torque coupling of the drive shaft to the output shaft is 26 lifted, so that a drive torque is then exclusively from the electric machine 14 can be delivered. When the disconnect clutch is engaged 120 is the torque transmission connection between the drive shaft and the housing 78 of the hydrodynamic torque converter 24 made, so that a driving torque by the internal combustion engine, possibly supported by the electric machine 14 , can be delivered.

The rotary union arrangement 94 includes here again the two rotary feedthrough areas 96 . 100 , The rotary feedthrough area 96 leads the motor side supplied or discharged fluid over the intermediate ring 72 to or from the here with its axial end portion of the intermediate shaft replacing the output shaft 26 , The output shaft 26 is formed in its axial end portion as a hollow shaft and has the insert part 104 on, so here in the axial end region of the output shaft 26 the two a connection between the two rotary feedthrough areas 96 . 100 are realized producing coaxial channels.

With regard to the construction of the torsional vibration damper assembly 28 corresponds to the in 4 shown embodiment of the foregoing, so that reference may be made to the relevant embodiments.

In 5 is a hybrid drive system 10 shown in which by a trained as a wet-running multi-plate clutch clutch 120 optionally a torque transmission connection between the rotor 20 the here designed as an internal rotor electric machine 14 and the drive shaft, not shown, can be realized. A housing 140 the separating clutch 120 is over a connecting disk 142 and a non-illustrated flex plate or the like for rotation with the crankshaft or drive shaft fixedly connected. An output element 144 the separating clutch 120 , which is rotatably coupled with an inner disk carrier, is both with the rotor 20 the electric machine 14 , as well as the primary page 43 of the first torsional vibration damper 30 firmly connected. Here includes the primary page 43 of the first torsional vibration damper 30 now the first housing part 42 while the secondary side 34 the second housing part 44 includes. With this is the primary page 88 of the second torsional vibration damper 32 , which may comprise, for example, two cover disk elements, firmly connected, for example, using a Hirth toothing. With the first housing part 42 is rotatably a second torsional vibration damper 30 surrounding housing 146 connected, with a housing hub 148 forms a pump hub, which can drive in a gear or the like engaging a pressure fluid pump. It is thus ensured that regardless of whether a torque via the internal combustion engine or the electric machine 14 is introduced 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 assembly 94 with its motor-side arranged first rotary leadthrough area 96 with the stator 102 , the intermediate wave 98 and in the region of the first torsional vibration damper 30 lying second rotary leadthrough area 100 ,

The 6 shows a hybrid drive system, which in terms of structural design largely the in 1 Represented corresponds. Reference should therefore be made to the above statements in this regard. However, there is a difference in the design of the Drehdurchführungsan order 94 , Their first rotary feedthrough area 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 This first rotary feedthrough area is, for example, on a transmission bell 150 firmly supported and provides a fluid connection to the intermediate shaft 98 ago. This in turn provides a fluid connection with the second housing part 44 of the first torsional vibration damper 30 or the pressure chambers formed therein.

One recognizes in the 6 that here is the intermediate shaft 98 is turned on in the torque flow. The second connection disc 76 is in its radially inner region to the axial end of the intermediate shaft 98 connected, as well as the radially inner region of a housing shell 152 of the Ge häuses 78 of the hydrodynamic torque converter 24 , It goes without saying that in both rotary feedthrough 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.

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

The rotary union arrangement 94 includes only a single rotary feedthrough area with a stator 164 , which is the wave-like extension area of the second housing part 44 is arranged surrounding. This wavy extension area 160 thus forms the rotor of the rotary feedthrough assembly 94 , This rotary union arrangement 94 is designed with double seals consisting 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 8th is shown an embodiment, which is essentially a connection between the in 7 shown embodiment and in 4 produces shown embodiment. Here is a incorporated in the torque flow dry-running friction clutch as a disconnect clutch 120 intended. This can optionally be a torque coupling of the intermediate ring 72 and thus the drive shaft to the rotor 20 the electric machine 14 or also the primary side 43 the first torsional vibration damper or Torsionsschwingungsdämpferanordnung 28 will be realized.

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

In all of the above-described embodiments of a hybrid drive system, it is provided that the torsional vibration damper arrangement 28 in the torque flow between the drive shaft 12 and the output shaft 26 after the electric machine 14 is positioned. In 9 is a hybrid drive system 10 shown in which the Torsionsschwingungsdämpferanordnung 28 with their first torsional vibration damper 30 in the torque flow in front of the electric machine 14 is positioned.

The primary side 43 here includes the first housing part 42 with its two side parts 36 . 38 and the fluid pressure storage units carried thereon 58 , For example, about these fluid pressure storage units 58 and a connection arrangement fixed thereto 170 can be realized via a flex plate or the like, a connection to the drive shaft, not shown. That the secondary side 34 providing second housing part 44 is with its wavy extension 160 and for example the two connecting disks 70 . 76 to the entrance area 172 a trained as a wet-running multi-plate clutch disconnect clutch 120 tethered. This entrance area 172 may include an inner disc carrier with the lamellae carried thereon. The exit area 174 forms a housing with it worn outer plates. This housing also forms the rotor at the same time 20 the electric machine 14 with the permanent magnets carried thereon 22 coming from the winding area 18 of the stator 16 are surrounded. The output shaft 26 is at the exit area 174 the separating clutch 120 and thus also the rotor 20 the electric machine 24 coupled.

The rotary union arrangement 94 may again be formed as above with respect to the 7 explained. Their stator 164 may for example be formed as part of a transmission housing.

The pressurized fluid supply of the separating clutch 120 can be done by a gearbox or from the motor side. Of course it is also possible the entrance area 172 to design as a housing and the inner disk carrier for forwarding the torque to the output shaft 26 to use.

In 10 is an embodiment of a hybrid drive system 10 shown, which largely the in 1 Represented corresponds. One difference, however, is that the supply of the first torsional vibration damper 30 with pressurized fluid through the output shaft 26 he follows. This is as a hollow shaft with the sleeve-like insert 98 trained and thus provides two channels over which the two pairs of pressure chambers can be supplied. The Indian 10 unrecognizable first rotary feedthrough area is then, for example, within an automatic transmission, where the pressure fluid in the output shaft 26 introduced or fluid can be discharged from this.

As in this embodiment, the torsional vibration damper 30 with the second rotary feedthrough area 100 completely inside the case 78 of the hydrodynamic torque converter 74 There is no problem in the occurrence of fluid leaks, as this on the circuit, which for the hydrodynamic torque converter 24 is constructed, can be dissipated.

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

At the in 11 shown embodiment of a hybrid drive system that is about the rotor 20 the electric machine 14 ready or forwarded torque back to the first housing part 42 of the first torsional vibration damper 30 passed, which housing part 42 here essentially the primary side 43 of the first torsional vibration damper 30 provides. The second housing part 44 conducts the torque further to a starting element 162 Wet-running multi-plate clutch used here. This is in one on the primary side 43 of the first torsional vibration damper 30 provided housing 146 which, as far as referring to the 5 already explained, with a housing hub 148 can drive a arranged in a transmission fluid pump.

An outer disc carrier 182 the wet-running multi-plate clutch is, for example via Hirtverzahnung or the like to the second housing part 44 So the secondary side 34 of the first torsional vibration damper 30 tethered. An inner disc carrier 184 is about the second torsional vibration damper 32 with an output hub 94 connected, which the non-rotatable coupling to the output shaft 26 realized. About this output shaft 26 Also in this embodiment, the supply of the first torsional vibration damper 30 with pressurized fluid, as with respect to the 10 has been explained above. 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 radially outside the output shaft 26 formed fluid channels.

In the 12 1 shows a connection between the previously described with reference to the 11 described construction with a wet-running multi-plate clutch than in the torque flow to the first torsional vibration damper 30 following starting element 162 and with reference to the 4 explained embodiment in which a separating clutch 120 Optionally, a connection between the rotor 20 the electric machine 14 and the drive shaft, which is not shown here, can realize. The about 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 here again with the first housing part 42 is trained. The fluid supply of the first torsional vibration damper 30 via the output shaft 26 , as previously explained several times.

In the 13 The illustrated embodiment provides a constructive connec tion of the above with reference to the 2 and 5 variants described. The rotor 20 the electric machine 14 can optionally by operating the separating clutch 120 be brought in conjunction with the drive shaft. That through the separating clutch 120 on the primary side 43 of the first torsional vibration damper 30 guided torque is transmitted via its secondary side 34 , here formed with the second housing part 44 , on the primary side 88 of the second torsional vibration damper 32 directed. This is back in the case 146 arranged with the primary side 43 of the first torsional vibration damper 30 rotatably coupled and thus provides a drive option for a fluid pump.

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

When Starting element can be integrated, for example, in a transmission Be used in the design of the transmission as a coupling Automatic transmission also to activate or deactivate one or multiple gears is used.

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

The 14 shows an embodiment, which largely on the in 9 shown and with respect to the 9 described embodiment is based. One recognizes here, however, that the entrance area 172 designed as a wet-running multi-plate clutch disconnect clutch 120 , for example via the two connecting disks 70 . 76 to the second housing part 44 connected, comprising a housing of the wet-running multi-plate clutch. The exit area 174 includes the inner disk carrier which is connected to an output hub member 94 firmly attached. At this output hub element 94 with which the output shaft, not shown, can be brought into rotationally fixed engagement, is also the rotor 20 the here designed as an internal rotor electric machine 14 firmly worn. This means that, similarly as in the embodiment according to 9 , with disengaged disconnect clutch 120 the electric machine 14 without vibration damping functionality is coupled to the other drive train. That is, the torsional vibration damper assembly 28 can do here with their first torsional vibration damper 30 only be effective against vibration damping when the separating clutch 120 is engaged, in principle so the internal combustion engine whose drive shaft to the first torsional vibration damper 30 is docked, is in operation.

foregoing have been various embodiments of hybrid propulsion systems explains in which a Torsionsschwingungsdämpferanordnung integrated with a gas spring torsional vibration damper is. This results in a variety of advantages in the drive state. For example, due to the provided by the electric machine very high moments of inertia in particular when this is designed as an external rotor, in conjunction with the comparatively low rigidity of a gas spring torsional vibration damper a excellent vibration isolation can be achieved.

at Embodiments in which a separating clutch is optional Coupling and uncoupling of the internal combustion engine is provided, a additional Rotary feedthrough area provide the advantage that the gas spring torsional vibration damper on can be arranged arbitrary axial positioning. Also can possibly for the gas spring torsional vibration damper a for the Separation clutch used hydraulic supply be shared. Likewise one for the gas spring torsional vibration damper provided leakage return also for the Disconnect be shared.

There in hybrid propulsion systems due to the provision of the electric machine a higher voltage level can be reached, further for the supply of gas spring torsional vibration damper on demand electrically driven oil pump be provided. This means it does not necessarily have to accessed the existing example in an automatic transmission oil pump become. With such an additional or external pressure fluid supply, it is still possible, a Hybrid drive system with any type of disconnect clutch also for manual transmissions where a fluid supply does not have a transmission input shaft takes place or can take place, but via an additional Rotating union.

Of the space available within an electric machine, for example the existing inside the Elektromaschinenstators space can be for example, for positioning a rotary feedthrough area use. Since this electric machine stator is generally cooled by water cooling, can the seals of the rotary feedthrough area thermally relieved. The existing at the electric machine Storage can equally also for be used in the area arranged rotary feedthrough area, so that by the joint seal and lubrication another Space advantage especially by axial space minimization arises.

in the Starting state, as well as in the driving state, the gas spring torsional vibration damper at least briefly to provide a damping function or a elasticity be effective, which is the regular effort when turning the electric machine reduced. This is because the torque increase of the electric machine via the gas spring torsional vibration damper on the drive train can be routed so that when switching from electric to internal combustion engine drive or vice versa Torque surges avoided or to achieve a targeted drivetrain twisting can be influenced. Such damping of course also on the coupling behavior of a separating clutch, so that the Clutch picking suppressed can be.

Claims (22)

Hybrid drive system, comprising an internal combustion engine with a drive shaft ( 12 ), an electric machine ( 14 ) with a stator ( 16 ) and one with the drive shaft ( 12 ) for rotation about an axis of rotation (A) coupled or coupled rotor ( 20 ) and one of the drive shaft ( 12 ) and / or the rotor ( 20 ) drivable output shaft ( 26 ), preferably transmission input shaft, further comprising a Torsional vibration damper arrangement ( 28 ) with a first torsional vibration damper ( 30 ) with a primary page ( 43 ) and one against the action of a damper fluid arrangement about the axis of rotation with respect to the primary side ( 43 ) rotatable secondary side ( 34 ). Hybrid drive system according to claim 1, characterized in that the Torsionsschwingungsdämpferanordnung ( 28 ) a second torsional vibration damper ( 30 ) comprises a primary page ( 88 ) and one 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 ). Hybrid drive system according to claim 2, characterized in that the secondary side ( 90 ) of the second torsional vibration damper ( 32 ) substantially an output region of the Torsionsschwingungsdämpferanordnung ( 28 ) and the secondary side ( 34 ) of the first torsional vibration damper ( 30 ) with the primary side ( 88 ) of the second torsional vibration damper ( 32 ) is rotatably connected. Hybrid drive system according to one of claims 1 to 3, characterized in that the damper fluid arrangement at least one fluid pressure accumulator arrangement ( 64 . 64 ' ) and a För deranordnung ( 65 ), by which during relative rotation of the primary side ( 43 ) with respect to the secondary side ( 34 ) the fluid storage pressure in at least one fluid pressure accumulator arrangement ( 64 . 64 ' ) can be increased. Hybrid drive system according to claim 4, characterized in that the at least one fluid pressure accumulator arrangement ( 64 . 64 ' ) at least one fluid pressure storage unit ( 58 ) with the conveyor assembly ( 65 ) conveyable, preferably substantially incompressible first fluid and a loadable by the first fluid energy storage ( 60 ). Hybrid drive system according to claim 5, characterized in that the at least one energy store ( 60 ) comprises compressible second fluid. 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. Hybrid drive system according to one of claims 4 to 7, characterized in that two fluid pressure accumulator arrangements ( 64 . 64 ' ) are provided and that during relative rotation of the primary side ( 43 ) with respect to the secondary side ( 34 ) in a first relative direction of rotation, the conveyor arrangement the fluid storage pressure ( 65 ) in a first of the fluid pressure storage 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, the fluid storage pressure in a second of the fluid pressure storage arrangements ( 64 . 64 ' ) elevated. Hybrid drive system according to one of claims 4 to 8, characterized in that the conveyor arrangement ( 65 ) at least one between the primary side ( 43 ) and the secondary side ( 34 ) formed pressure chamber ( 50 . 50 ' . 52 . 52 ' ) whose volume during relative rotation of the primary side ( 43 ) with respect to the secondary side ( 34 ) is variable, and at least one connection volume ( 54 . 54 ' . 56 . 56 ' ), via which from the at least one pressure chamber ( 50 . 50 ' . 52 . 52 ' ) displaced first fluid at least one energy store ( 60 ) charged. Hybrid drive system according to claim 8, characterized in that the conveyor arrangement ( 65 ) one by relative rotation of the primary side ( 43 ) with respect to the secondary side ( 34 ) comprises drivable pumping arrangement, which promotes depending on the relative rotational direction of the first fluid from one of the fluid pressure accumulator assemblies to the other fluid pressure accumulator assembly. Hybrid drive system according to one of claims 4 to 10, characterized in that the at least one fluid pressure accumulator arrangement ( 64 . 64 ' ) first fluid via the output shaft ( 26 ) can be fed. Hybrid drive system according to one of claims 4 to 10, characterized in that the at least one fluid pressure accumulator arrangement ( 64 . 64 ' ) first fluid via a preferably not for torque transmission between the drive shaft ( 12 ) and the output shaft ( 26 ) provided intermediate shaft ( 98 ) can be fed. Hybrid drive system according to claim 11 or 12, characterized in that the drive shaft ( 12 ) or intermediate wave ( 98 ) over a first rotary feedthrough area ( 96 ) is or can be brought into fluid communication with a source of pressurized fluid and via a second rotary feedthrough area (FIG. 100 ) in fluid communication with the at least one fluid pressure accumulator arrangement ( 64 . 64 ' ) stands. Hybrid drive system according to claim 13, characterized in that the first rotary feedthrough area ( 96 ) is arranged on the engine side for fluid intake / fluid delivery. Hybrid drive system according to claim 13, since characterized in that the first rotary feedthrough area ( 96 ) is arranged on the transmission side for fluid intake / fluid delivery. Hybrid drive system according to claim 13, characterized in that the first rotary feedthrough area ( 96 ) between the electric machine ( 14 ) and the Torsionsschwingungsdämpferanordnung ( 28 ) is arranged for fluid intake / fluid delivery. Hybrid drive system according to one of claims 1 to 16, characterized in that a disconnect clutch arrangement ( 120 ) for establishing / interrupting a torque transmission connection between the drive shaft (10) 12 ) and the rotor ( 20 ) is provided. Hybrid drive system according to claim 17, characterized in that the torsional vibration damper arrangement ( 28 ) in the torque flow from the drive shaft ( 12 ) to the output shaft ( 26 ) in front of the disconnect clutch assembly ( 120 ) is provided. Hybrid drive system according to claim 17, characterized in that the torsional vibration damper arrangement ( 28 ) in the torque flow from the drive shaft ( 12 ) to the output shaft ( 26 ) after the disconnect clutch assembly ( 120 ) is provided. Hybrid drive system according to one of claims 1 to 19, characterized in that the Torsionsschwingungsdämpferanordnung ( 28 ) in the torque flow from the drive shaft ( 12 ) to the output shaft ( 26 ) in front of the electric machine ( 14 ) is arranged. Hybrid drive system according to one of claims 1 to 19, characterized in that the Torsionsschwingungsdämpferanordnung ( 28 ) in the torque flow from the drive shaft ( 12 ) to the output shaft ( 26 ) after the electric machine ( 14 ) is arranged. Hybrid drive system according to one of claims 1 to 21, characterized in that the output shaft ( 26 ) a torque from the drive shaft ( 12 ) via a starting assembly ( 162 ), preferably hydrodynamic coupling device ( 24 ) or wet-running coupling device receives.