DE102015008292A1 - Drive unit, including for a motor vehicle - Google Patents

Abstract

The invention relates to a drive unit (10), inter alia for a motor vehicle, having an internal combustion engine (12) having a plurality of combustion chambers (5, 6), with at least one exhaust gas turbocharger (24) which can drive one of exhaust gas of the internal combustion engine (12) Turbine (28) and one of the turbine (28) drivable compressor (34) for compressing the combustion chambers (5, 6) to be supplied air, and with at least one of an output shaft of the internal combustion engine (12) drivable and decoupled from the output shaft, mechanical or electrical supercharger (38) for compressing air to be supplied to the combustion chambers (5, 6), comprising: - at least one first exhaust gas path (40) through which exhaust gas from at least one of the combustion chambers (5, 6) can flow; The turbine (28), which can be driven by the exhaust gas flowing through the first exhaust gas path (40), and a bypass line (48) are arranged, via which the turbine (28) of FIG ndest a portion of the exhaust gas flowing through the first exhaust path (40) is to bypass, and - at least one of exhaust from at least one of the first combustion chamber (6) different, second of the combustion chambers (5, 6) can be flowed through second exhaust path (44) via which the first exhaust path (40) is to be bypassed by the exhaust gas flowing through the second exhaust path (44).

Description

The invention relates to a drive unit, inter alia for a motor vehicle, according to the preamble of patent claim 1.

Such a drive unit, inter alia for a motor vehicle such as a passenger car, is already well known from the general state of the art. The drive unit comprises an internal combustion engine which has a plurality of combustion chambers, in particular in the form of cylinders. The drive unit further comprises at least one exhaust gas turbocharger, which has a turbine which can be driven by exhaust gas of the internal combustion engine and a compressor drivable by the turbine for compressing air to be supplied to the combustion chambers. In other words, the exhaust gas turbocharger is used for charging the internal combustion engine, since charging is understood as meaning the supply of the compressed air to the combustion chambers.

The drive unit further comprises at least one of an output shaft of the internal combustion engine driven and decoupled from the output shaft, mechanical supercharger for compressing the combustion chambers to be supplied air. The mechanical supercharger is usually also referred to as a compressor and is a mechanically drivable loader, since it is not drivable by the exhaust gas of the internal combustion engine, but by the example designed as a crankshaft output shaft, that is mechanically driven. It would also be an electric drivability conceivable.

For coupling the mechanical supercharger with the output shaft and for decoupling the mechanical supercharger from the output shaft, a clutch is used, for example, which can be opened and closed. If the clutch is closed, the mechanical supercharger is coupled to the output shaft and can be driven by the output shaft, so that air is compressed by means of the mechanical supercharger. If the clutch is open, the mechanical loader is decoupled from the output shaft, so that the mechanical loader is not driven by the output shaft. By using the compressor and the mechanical supercharger, the internal combustion engine can be charged particularly well, so that, for example, an advantageous response of the internal combustion engine can be realized.

Object of the present invention is to develop a drive unit of the type mentioned in such a way that a particularly advantageous emission behavior of the internal combustion engine in conjunction with optimized residual gas behavior at high spec. Liter capacity and rated speed, is feasible.

This object is achieved by a drive unit having the features of patent claim 1. Advantageous embodiments with expedient developments of the invention are specified in the remaining claims.

In order to develop a drive unit specified in the preamble of claim 1 type such that an advantageous response and a particularly advantageous emission behavior of the internal combustion engine can be realized according to the invention provided at least one of exhaust from at least a first of the combustion chambers through-flow first exhaust path, in which arranged the turbine is. Thus, the turbine is driven by the exhaust gas flowing through the first exhaust path. In the first exhaust path, a bypass line is further arranged, via which the turbine is to be avoided by at least a portion of the exhaust gas flowing through the first exhaust path. By bypassing the turbine is meant a so-called bypassing of the turbine, since the exhaust gas flowing through the bypass line does not flow through the turbine and thus does not drive the turbine. In other words, the exhaust gas flowing through the bypass bypasses the turbine and thus does not drive the turbine.

In addition, at least one second exhaust gas path is provided, which can be flowed through by exhaust gas from at least one of the second combustion chamber, which is different from the first combustion chamber. The first exhaust gas path is to be bypassed by the exhaust gas flowing through the second exhaust gas path via the second exhaust gas path. This means that the exhaust gas flowing through the second exhaust path does not flow through the first exhaust path, but bypasses the first exhaust path. The exhaust gas flowing through the second exhaust gas path can thus also not flow through the turbine and drive it, but the exhaust gas flowing through the second exhaust gas path can for example be led directly to an exhaust aftertreatment device, in particular a catalytic converter, so that the exhaust gas aftertreatment device is heated particularly efficiently and effectively. can be heated.

The core idea of the invention is thus that the at least one first combustion chamber promotes its exhaust gas in the first exhaust path and not in the second exhaust path, wherein the at least one second combustion chamber promotes its exhaust gas in the second exhaust path and not in the first exhaust path. The at least one first combustion chamber speaks, so to speak, directly into the exhaust aftertreatment device, so that the so-called Katalysatorheizmoment can be kept low. This allows the Emissions of the internal combustion engine are kept to a particularly low level. In addition, a particularly advantageous response of the internal combustion engine can be represented in the drive unit according to the invention, since as the turbine as small as possible turbine can be used. As a result, a particularly agile response of the internal combustion engine can be realized.

The turbine is designed, for example, as a mono-scroll turbine, twin-scroll turbine, segment turbine and / or can have a variable turbine geometry. Alternatively or additionally, it is conceivable that the turbine or the exhaust gas turbocharger altogether an electric motor is assigned as a so-called e-booster, so that the turbine can be driven electrically by means of the electric motor. In addition, it is possible by means of the drive unit according to the invention to realize a particularly advantageous residual gas behavior, in particular at rated power of the internal combustion engine. Thus, it is conceivable to realize a particularly high compression, since a particularly good flushing of the combustion chambers can be displayed. As a result of the realization of this high compression, a particularly economical partial load operation can be realized.

In conventional turbocharged internal combustion engines, the supercharging of the internal combustion engine is usually a compromise between torque build-up and rated power representation. In the drive unit according to the invention, this compromise can be avoided by the combination of charging units in the form of the mechanical supercharger and the exhaust gas turbocharger. In addition, further advantages are to be expected, especially in certification cycles, since the drive unit can be used to produce a particularly advantageous downsizing with a particularly high liter output of, for example, more than 135 kilowatts per liter and with high compression of, for example, higher than 9.3.

Further advantages, features and details of the invention will become apparent from the following description of a preferred embodiment and from the drawing. The features and feature combinations mentioned above in the description as well as the features and feature combinations mentioned below in the figure description and / or alone in the single figure can be used not only in the respectively indicated combination but also in other combinations or alone, without the frame to leave the invention.

The drawing shows in the single FIGURE is a schematic representation of a drive unit, including for a motor vehicle, with two turbochargers and a mechanical supercharger.

The only Fig. Shows in a schematic representation of a whole 10 Designated drive unit, including for a motor vehicle such as a motor vehicle, especially passenger cars. The drive unit 10 is used to drive the motor vehicle and includes an internal combustion engine 12 , which is designed as a reciprocating internal combustion engine and has a plurality of combustion chambers present in the form of cylinders. In the present case, the internal combustion engine 12 eight cylinders, which in the Fig. Of 1 to 8th numbered consecutively and accordingly with 1 . 2 . 3 . 4 . 5 . 6 . 7 and 8th are designated. The internal combustion engine 12 is designed for example as a V-engine and includes two cylinder banks 14 and 16 , where the cylinder bank 14 the cylinders 1 . 2 . 3 . 4 and the cylinder bank 16 the cylinders 5 . 6 . 7 and 8th having. In the present case, the internal combustion engine 12 following ignition sequence on: 1 - 5 - 4 - 2 - 6 - 3 - 7 - 8th , However, the preceding and following embodiments are also readily applicable to other internal combustion engines with respect to eight larger or smaller number of cylinders and / or with a different firing order. For example, it is alternatively conceivable that the internal combustion engine 12 is designed as a series motor.

The internal combustion engine 12 has an output shaft, not shown in the figure, which is formed for example as a crankshaft. The output shaft is connected to a crankcase of the internal combustion engine not visible in the figure 12 rotatable about an axis of rotation relative to the crankcase. About the output shaft provides the internal combustion engine 12 Torques for driving the motor vehicle ready. The drive unit 10 has one of exhaust gas of the internal combustion engine 12 permeable exhaust tract 18 in which exhaust aftertreatment devices in the form of catalysts 20 and 22 are arranged. The drive unit 10 also has two exhaust gas turbochargers 24 and 26 on, which in each case one of exhaust gas of the internal combustion engine 12 drivable and in the exhaust tract 18 arranged turbine 28 respectively. 30 include.

The drive unit 10 further comprises an intake tract 32 , which can be traversed by air. By means of the intake tract 32 the air gets to the cylinders 1 . 2 . 3 . 4 . 5 . 6 . 7 and 8th fed. The turbocharger 24 . 26 each include one in the intake tract 32 arranged compressor 34 respectively. 36 , where the compressor 34 Part of the exhaust gas turbocharger 24 and consequently from the turbine 28 is drivable. The compressor 36 is part of the exhaust gas turbocharger 26 and consequently from the turbine 30 drivable. By driving the respective compressor 34 respectively. 36 can the the intake tract 32 be compressed by flowing air. Because the respective turbine 28 respectively. 30 of exhaust gas the Internal combustion engine 12 is driven, energy contained in the exhaust gas can be used to compress the air.

This includes the respective turbine 28 respectively. 30 For example, one of the exhaust gas driven turbine wheel, which is rotatably connected to a respective shaft. Furthermore, the respective compressor comprises 34 respectively. 36 For example, a compressor wheel for compressing the air, wherein the compressor wheel rotatably connected to the shaft and thus can be driven via the shaft of the respective turbine wheel. The cylinders 1 . 2 . 3 . 4 . 5 . 6 . 7 . 8th can be supplied with the compressed air, so even at a low displacement of the internal combustion engine 12 high specific torques and power can be displayed.

The drive unit 10 further comprises at least one mechanical loader 38 , which is also referred to as a compressor. The mechanical loader 38 is coupled to the crankshaft and thus can be driven by the crankshaft and decoupled from the crankshaft. For this purpose, for example, a clutch, not recognizable in the figure, is provided, which can be opened and closed. If the clutch is closed, then the mechanical loader 38 coupled with the crankshaft and is therefore driven by the crankshaft. If the clutch is open, then the mechanical loader 38 decoupled from the crankshaft and can not be driven by the crankshaft. By means of the mechanical loader 38 can the the intake tract 32 air flowing through are compressed so that the compressors 34 and 36 as well as the mechanical loader 38 can be used to compress the air. It can also be seen from the figure that per cylinder bank 14 respectively. 16 a first exhaust path 40 respectively. 42 and a second exhaust path 44 respectively. 46 are provided. Thus, the drive unit 10 two first exhaust paths 40 and 42 and two second exhaust paths 44 and 46 on. Here are the cylinders 7 and 8th to the exhaust path 40 merged, leaving the first exhaust path 40 exhaust from the cylinders 7 and 8th can be flowed through. The cylinders 5 and 6 are to the exhaust path 44 merged, leaving the second exhaust path 44 from the exhaust from the cylinders 5 and 7 is flowed through or is flowed through. In other words, the first exhaust path 40 exhaust from the cylinders 6 and 8th but not exhaust from the cylinders 5 and 7 permeable, wherein the second exhaust path 44 exhaust from the cylinders 5 and 7 but not exhaust from the cylinders 6 and 8th can be flowed through. The same applies to the cylinder bank 14 , Here are the cylinders 3 and 4 to the exhaust path 42 merged, leaving the first exhaust path 42 exhaust from the cylinders 3 and 4 but not exhaust from the cylinders 1 and 2 can be flowed through. The cylinders 1 and 2 however, are the exhaust path 46 merged, leaving the second exhaust path 46 exhaust from the cylinders 1 and 2 but not exhaust from the cylinders 3 and 4 can be flowed through.

In the respective, first exhaust path 40 respectively. 42 is the respective turbine 28 respectively. 30 arranged so that the respective turbine 28 respectively. 30 from the respective first exhaust path 40 respectively. 42 flowing exhaust gas is driven. Furthermore, in the respective first exhaust path 40 respectively. 42 at least one bypass line 48 respectively. 50 arranged over which the respective turbine 28 respectively. 30 from at least a part of the respective first exhaust path 40 respectively. 42 flowing through exhaust gas is to be avoided. Preferably, the entire, the respective first exhaust path 40 respectively. 42 exhaust gas flowing through the respective bypass line 48 respectively. 50 flow through, which is the respective bypass line 48 respectively. 50 exhaust gas flowing through the respective turbine 28 respectively. 30 does not flow through and thus the respective turbine 28 respectively. 30 does not drive. Based on the flow direction of the exhaust gas through the respective first exhaust path 40 respectively. 42 is the particular catalyst 20 respectively. 22 downstream of the respective turbine 28 respectively. 30 arranged so that the respective first exhaust path 40 respectively. 42 flowing exhaust gas to the respective turbine 28 respectively. 30 to the respective catalyst 20 respectively. 22 flows through or flows through it.

From the Fig. It is further seen that the respective first exhaust path 40 respectively. 42 over the respective second exhaust path 44 respectively. 46 to bypass exhaust gas. In other words, this bypasses the respective second exhaust path 44 respectively. 46 exhaust gas flowing through the respective first exhaust path 40 respectively. 42 , so that the respective second exhaust path 44 respectively. 46 exhaust gas flowing through not through the respective first exhaust path 40 respectively. 42 flows. The first exhaust paths 40 and 42 as well as the respective second exhaust paths 44 and 46 are fluid with the respective catalysts 20 and 22 connected, so that also the respective second exhaust path 44 respectively. 46 flowing exhaust gas to the respective catalyst 20 respectively. 22 flows and flows through them. The first exhaust paths 40 and 42 are thus exhaust strands with the turbines 28 and 30 , wherein the second exhaust paths 44 and 46 Exhaust pipes without turbine are. The cylinders 1 . 2 . 5 and 7 thus do not promote their exhaust gas through the turbines 28 and 30 but directly to the catalysts 20 and 22 so that they can be heated particularly effectively and efficiently.

Overall, it can be seen from the figure that per cylinder bank 14 respectively. 16 two of the respective cylinders are brought together in such a way that in each case two first of the cylinders their exhaust gas to the respective first exhaust path 40 respectively. 42 , and two of the first cylinders each other, second of the cylinders her Exhaust gas to the respective second exhaust path 44 respectively. 46 promote. The application-optimal admission of the exhaust gas paths 40 . 42 . 44 and 46 results, for example, from the respective firing order.

In the respective first exhaust path 40 respectively. 42 is a turbine valve device 52 respectively. 54 arranged, by means of which a bypass line 48 respectively. 50 flowing through amount of the exhaust gas is adjustable. In other words, it is by means of the respective turbine valve device 52 respectively. 54 possible, respective amounts of the respective bypass line 48 respectively. 50 and the respective turbine 28 respectively. 30 adjust exhaust gas flowing through, so that it is possible, for example, by means of the respective turbine valve device 52 respectively. 54 the bypass 48 respectively. 50 as well as the respective turbine 28 respectively. 30 to block or release. Is the respective bypass line 48 respectively. 50 For example, fluidly blocked, so is the respective turbine 28 respectively. 30 released, so that the respective first exhaust path 40 respectively. 42 flowing exhaust gas through the respective turbine 28 respectively. 30 and not by the respective bypass line 48 respectively. 50 flows. Is for example by means of the respective turbine valve device 52 respectively. 54 the respective turbine 28 respectively. 30 fluidly obstructed, so is the respective bypass line 48 respectively. 50 released, so that the respective first exhaust path 40 respectively. 42 flowing exhaust gas not through the respective turbine 28 respectively. 30 but by the respective bypass line 48 respectively. 50 flows. In this case, the turbines 28 and 30 deactivated on the exhaust side, as the turbines 28 and 30 not driven by the exhaust gas.

In the figure, a state is shown in which the turbine valve devices 52 and 54 the turbine 28 and 30 release and the bypass lines 48 and 50 obstruct, so that the exhaust does not pass through the bypass lines 48 and 50 but through the turbines 28 and 30 flows and the turbines 28 and 30 drives. This is the case for example in a first operating state, which is also referred to as exhaust gas turbocharger operation. In a second operating state, which is also referred to as a supercharger operation, obstruct the turbine valve devices 52 and 54 the turbines 28 and 30 and give the bypass lines 48 and 50 free, so that's the first exhaust paths 40 and 42 flowing exhaust gas through the bypass lines 48 and 50 not by the turbines 28 and 30 flows, so the turbines 28 and 30 then not be driven.

In the intake tract 32 are upstream of the mechanical loader 38 and upstream of the compressor 34 and 36 air filter 56 and 58 arranged, by means of which the air is filtered. In addition, each compressor is 34 respectively. 36 a compressed air flow through the compressor path 60 respectively. 62 provided in which the respective compressor 34 respectively. 36 is arranged. The compressor paths 60 and 62 are traversed by the air. Further, one is the compressors 34 and 36 common and air-permeable compressor bypass path 64 provided over which the compressor 34 and 36 from the compressor bypass path 64 to be bypassed by flowing air. This means that the the compressor bypass path 64 air flowing through not through the compressor 34 and 36 flows and thus not by means of the compressor 34 and 36 is compressed.

The drive unit 10 includes a compressor valve device 66 for example, with a compressor path 60 and the compressor bypass path 64 associated valve element 68 and one the compressor path 62 and the compressor bypass path 64 associated valve element 70 , By means of the compressor valve device 66 , in particular by means of the valve elements 68 and 70 , are respective, the respective compressor path 60 respectively. 62 and the compressor bypass path 64 adjustable amounts of air adjustable. For example, it is possible by means of the compressor valve device 66 the compressor paths 60 and 62 fluidly obstruct and the compressor bypass path 64 release, so that the air is not through the compressor paths 60 and 62 but through the compressor bypass path 64 flows or can flow. This is for example provided in the supercharger mode. Furthermore, it is possible that the compressor valve device 66 the compressor bypass duct 64 fluidly obstructed and the compressor paths 60 and 62 releases so that the air is not through the compressor bypass path 64 but through the compressor paths 60 and 62 flows or can flow. This is provided for example in the exhaust gas turbocharger operation, so that the air through the compressor 34 and 36 is compressed. Is the compressor bypass path 64 released and are the compressor paths 60 and 62 fluidly obstructed, so are the compressors 34 and 36 or the turbocharger 24 and 26 deactivated on the air side. This is intended, for example, in loader operation. In the figure, the exhaust gas turbocharger operation is illustrated by - as can be seen from the figure - the compressor valve device 66 the compressor paths 60 and 62 releases and the compressor bypass path 64 fluidly blocked or from the air filters 56 and 58 separates.

The drive unit 10 also has at least one air flow through the loader path 72 on, in which the mechanical loader 38 is arranged. In addition, each cylinder bank 14 respectively. 16 an airflowable loader bypass path 74 respectively. 76 provided so that a total of two loader bypass paths 74 and 76 are provided. The loader bypass paths 74 and 76 are traversed by air, whereby the loader bypass paths 74 and 76 air flowing through it is not the loader path 72 and thus the mechanical loader 38 flows through and therefore not by means of the mechanical charger 38 is compressed. In addition, a loader valve device 78 provided by means of which respective, the loader path 72 and the loader bypass paths 74 and 76 flowing through amounts of air are adjustable. The loader valve device 78 includes, for example, valve elements 80 . 82 and 84 wherein, for example, the loader bypass path 74 by means of the valve element 84 fluidly lockable, the loader bypass path 76 by means of the valve element 80 fluidic lockable and the loader path 72 by means of the valve element 82 is fluidic lockable.

Specifies the loader valve device 78 the loader bypass paths 74 and 76 free while the loader valve device 78 the loader path 72 fluidly obstructed, so the air can not pass through the loader 72 flow, but the air flows through the loader bypass paths 74 and 76 and is therefore not by means of the loader 38 compacted. This is provided for example in the exhaust gas turbocharger operation. Locks the loader valve device 78 the loader bypass paths 74 and 76 while the loader valve device 78 the loader path 72 releases the air does not flow through the loader bypass paths 74 and 76 but through the loader path 72 and thus the mechanical loader 38 , so that the air by means of the mechanical charger 38 can be compressed. This is intended, for example, in loader operation.

By the respective compression of the air, this is heated. To represent a particularly high degree of supercharging, are in the intake 32 Cooling devices in the form of intercoolers 86 and 88 arranged, by means of which by means of the mechanical supercharger 38 or through the compressors 34 and 36 compressed and thus heated air is cooled before the air enters the cylinders 1 . 2 . 3 . 4 . 5 . 6 . 7 and 8th flows. Overall, it can be seen from the figure that the intake tract 32 flowing through and for example by the compressor 34 and 36 or through the mechanical loader 38 compressed air the cylinder banks 14 and 16 or the combustion chambers can be fed. Since the turbocharger operation is illustrated in the figure, in the present case, the loader path 72 fluidly obstructed while the loader bypass paths 74 and 76 are released.

From the Fig. It can also be seen that the compressor paths 60 and 62 and the compressor bypass path 64 to a common air path 90 downstream of the compressor 34 and 36 and upstream of the mechanical loader 38 are merged. In the air path 90 is a throttle 92 arranged, by means of which a total of the combustion chambers to be supplied amount of air is adjustable or adjusted. The air path branches off 90 downstream of the throttle 92 in the loader path 72 and the loader bypass paths 74 and 76 on. Overall, it can be seen from the figure that in the exhaust-gas turbocharger operation the mechanical supercharger 38 (Compressor) is switched off both mechanically and on the air side, since the clutch is open and the loader path 72 is fluidly locked.

The turbines are exhausted 28 and 30 with exhaust from the cylinders 6 and 8th respectively. 3 and 4 acted upon, here by way of example (resulting from the firing order) cylinder 5 and 7 respectively. 1 and 2 their exhaust directly and bypassing the turbines 28 and 30 to the catalysts 20 and 22 promote. Air side promote the compressor 34 and 38 on the mechanical loader 38 pass directly into the intercooler 86 and 88 , For example, the exhaust gas turbocharger operation in low and medium speeds, for example in a range of 25 to 40 percent of the maximum speed of the internal combustion engine 12 set. Exceeds the speed of the internal combustion engine 12 this middle speed range, so there is a switch to the charger operation, which is also referred to as compressor operation.

As part of this switchover, the turbocharger 24 and 26 deactivated on the turbine side and compressor side as the turbines 28 and 30 from the exhaust gas via the bypass lines 48 and 50 and the compressors 34 and 36 from the air via the compressor bypass path 64 to be bypassed. This shutdown takes place by means of the turbine valve devices 52 and 54 and by means of the compressor valve device 66 and 70 , For example, the turbocharger 24 and 26 deactivated or bypassed by control valves, switching rollers and / or other elements. Because the turbines 28 and 30 be bypassed by exhaust gas, all the exhaust gas flows from the cylinders 1 . 2 . 3 . 4 . 5 . 6 . 7 and 8th not by turbines 28 and 30 but directly to and through the catalysts 20 and 22 ,

Finally, in turbocharger operation are the exhaust gas turbochargers 24 and 26 Deactivated on the air and exhaust side. Air side is at the mechanical loader 38 the loader valve device 78 and 80 switched so that the air through the mechanical charger 38 flows and is compacted by means of this. This is done for example by means of at least one recirculation damper, control valve and / or a valve. In exhaust gas turbocharger operation thus ensure the exhaust gas turbocharger 24 and 26 solely for charging, with the loader alone the mechanical loader 38 for the supercharging of the internal combustion engine 12 provides. By such operation of the power plant 10 can be a particularly advantageous response of the internal combustion engine 12 be realized so that it can provide high torques even at low speeds. At the same time, the emissions of the internal combustion engine 12 be kept low as the catalysts 20 and 22 can be heated particularly advantageous. Finally, a particularly advantageous residual gas behavior, in particular at rated power, can be represented.

LIST OF REFERENCE NUMBERS

10

power unit

12

Internal combustion engine

14

cylinder bank

16

cylinder bank

18

exhaust tract

20

catalyst

22

catalyst

24

turbocharger

26

turbocharger

28

turbine

30

turbine

32

intake system

34

compressor

36

compressor

38

mechanical loader

40

first exhaust path

42

first exhaust path

44

second exhaust path

46

second exhaust path

48

bypass line

50

bypass line

52

Turbine valve device

54

Turbine valve device

56

air filter

58

air filter

60

compressor path

62

compressor path

64

Compressor bypass path

66

Compressor valve means

68

valve element

70

valve element

72

loaders path

74

Supercharger bypass path

76

Supercharger bypass path

78

Loader valve means

80

valve element

82

valve element

84

valve element

86

Intercooler

88

Intercooler

90

air path

92

throttle

1

cylinder

2

cylinder

3

cylinder

4

cylinder

5

cylinder

6

cylinder

7

cylinder

8th

cylinder

Claims (7)

Drive unit ( 10 ), inter alia for a motor vehicle, having a plurality of combustion chambers ( 5 . 6 ) having internal combustion engine ( 12 ), with at least one exhaust gas turbocharger ( 24 ), which one of exhaust gas of the internal combustion engine ( 12 ) drivable turbine ( 28 ) and one of the turbine ( 28 ) drivable compressor ( 34 ) for compressing the combustion chambers ( 5 . 6 ) to be supplied with air, and at least one of an output shaft of the internal combustion engine ( 12 ) can be driven and decoupled from the output shaft, mechanical or electrical loader ( 38 ) for compressing the combustion chambers ( 5 . 6 ) supplied air, characterized by: - at least one of exhaust from at least a first of the combustion chambers ( 5 . 6 ) flow through the first exhaust path ( 40 ) in which the first exhaust path ( 40 ) through-flowing exhaust gas driven turbine ( 28 ) and a bypass ( 48 ) are arranged, over which the turbine ( 28 ) of at least part of the first exhaust path ( 40 ) bypassing the exhaust gas, and - at least one of exhaust gas from at least one of the first combustion chamber ( 6 ) different, second of the combustion chambers ( 5 . 6 ) can be flowed through the second exhaust path ( 44 ), over which the first exhaust path ( 40 ) of which the second exhaust path ( 44 ) to bypass the exhaust gas. Drive unit ( 10 ) according to claim 1, characterized by: - at least one air-flow compressor path ( 60 ), in which the compressor ( 34 ), - at least one air-bypassed compressor bypass path ( 64 ) over which the compressor ( 34 ) from the compressor bypass path (FIG. 64 ) to bypass the air, and - a compressor valve device ( 66 ), by means of which, the compressor path ( 60 ) and the compressor bypass path (FIG. 64 ) are adjustable by flowing amounts of air. Drive unit ( 10 ) according to claim 1 or 2, characterized by - at least one air-flow through the loader path ( 72 ), in which the mechanical loader ( 38 ), - at least one air-bypassable loader bypass path ( 76 ), over which the mechanical loader ( 38 ) from the loader bypass path ( 76 ) to be bypassed by air, and A loader valve device ( 78 ), by means of which, the loader path ( 72 ) and the loader bypass path ( 76 ) are adjustable by flowing amounts of air. Drive unit ( 10 ) according to claims 2 and 3, characterized in that the compressor path ( 60 ) and the compressor bypass path (FIG. 64 ) downstream of the compressor ( 34 ) and upstream of the mechanical supercharger ( 38 ) to an air path ( 90 ), in which a throttle valve ( 92 ), wherein the air path downstream of the throttle valve ( 92 ) and upstream of the mechanical supercharger ( 38 ) in the loader path ( 72 ) and the loader bypass path ( 76 ) branches off. Drive unit ( 10 ) according to one of the preceding claims, characterized in that in the first exhaust path ( 40 ) a turbine valve device ( 52 ) is arranged, by means of which a bypass line ( 48 ) flowing through amount of the exhaust gas is adjustable. Drive unit ( 10 ) according to claims 1 to 5, characterized in that a first operating state is provided, in which the mechanical loader ( 38 ) decoupled from the output shaft, the loader path ( 72 ) by means of the loader valve device ( 78 ) fluidly blocked, the loader bypass path ( 76 ), the compressor bypass path ( 64 ) by means of the compressor valve device ( 66 ) fluidly blocked, the compressor path ( 60 ) and the bypass ( 48 ) by means of the turbine valve device ( 52 ) is fluidly blocked. Drive unit according to claim 6, characterized in that a second operating state is provided, in which the mechanical loader ( 38 ) coupled with output shaft, the loader path ( 72 ), the loader bypass path ( 76 ) by means of the loader valve device ( 78 ) fluidly blocked, the compressor bypass path ( 64 ), the compressor path ( 60 ) by means of the compressor valve device ( 66 ) fluidly blocked and the bypass line ( 48 ) is released.

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