DE102014018069A1 - Turbine for an exhaust gas turbocharger, in particular an internal combustion engine - Google Patents

Abstract

The invention relates to a turbine (28) for an exhaust gas turbocharger (22), in particular an internal combustion engine (10), with at least one turbine housing (30) having a receiving space (36) for a turbine wheel (38), which at least two exhaust gas flows through and at least partially fluidly separated from each other floods (32, 34), and with an adjusting device (64) which at least one about a rotation axis (40) rotatable first Verperrkörper (66) for adjusting at least one of exhaust gas-flowable first flow cross-section of a first of the floods (32 , 34), at least one about the rotation axis (40) rotatable second Versperrkörper (68) for adjusting at least one exhaust flow-through second flow cross section of the second flood (34) and the Versperrkörpern (66, 68) common and about the axis of rotation (40) rotatable actuating element (70 (over which the Versperrkörper (66, 68) rotatably about the axis of rotation (40) sin d, wherein the actuating element (70) has at least one connecting channel (W) and between at least one connecting position, in which the floods (32, 34) via the connecting channel (W) at least one respective connection point (V) are fluidly interconnected, and at least one separation position, in which the floods (32, 34) at the respective connection point (V) by means of the actuating element (70) are fluidly separated from each other, about the axis of rotation (40) is rotatable.

Description

The invention relates to a turbine for an exhaust gas turbocharger, in particular an internal combustion engine, according to the preamble of patent claim 1.

Such a turbine for an exhaust gas turbocharger, in particular an internal combustion engine, for example, is already the DE 10 2008 039 085 A1 to be known as known. The turbine comprises at least one turbine housing, which has a receiving space for a turbine wheel. This means that in the receiving space, the turbine wheel about a rotational axis relative to the turbine housing is rotatably receivable. The turbine housing has at least two floods through which exhaust gas can flow and at least partially separated from one another by fluid. Furthermore, the turbine comprises an adjusting device, which has at least one rotatable about an axis of rotation first Verperrkörper for adjusting at least one of exhaust gas can flow through the first flow cross-section of a first of the floods. In other words, the first flow cross-section through which the exhaust gas can flow is variably adjustable by rotating the first locking body about the axis of rotation.

The adjusting device furthermore has at least one second locking body rotatable about the axis of rotation for adjusting at least one second flow cross section of the second flood through which exhaust gas can flow. In other words, the second flow cross-section of the second flood is variably adjustable by the second locking body is rotated about the axis of rotation. In addition, the adjusting device comprises a common to the Versperrkörpern and rotatable about the axis of rotation actuating element, via which the Versperrkörper are rotatable about the axis of rotation. The actuating element is, for example, a ring rotatable about the axis of rotation.

If the ring is rotated about the axis of rotation relative to the turbine housing, so the Versperrkörper be rotated, since the Versperrkörper example, connected to the actuating element or formed integrally with the actuating element. Due to the variable adjustability of the flow cross sections, the turbine can be adapted to different operating points of the internal combustion engine as needed. In particular, it is possible to adapt the turbine to different mass flows of the exhaust gas.

The Versperrkörper can be formed, for example in cross section in the manner of tongues, so that the adjustment is commonly referred to as a tongue slider. It has been shown that with a variable turbine according to the tongue slide principle, a large number of requirements for the charging system, such as high agility, favorable consumption behavior in the driving range, influencing possibilities for reducing emissions, for example via the exhaust gas recirculation, caused by an asymmetric segment design, mechanical Reliability of the simple adjustment device in the form of the tongue slider, acting on the increase of the engine braking performance, simple device for the thermal management of the internal combustion engine, use in two-stage supercharging system as a high-pressure turbine without bypassing the same, cost-effective production conditions, etc. can be satisfied.

A fundamental problem of turbines, in particular segmented turbines, in the turbocharger system is the large area requirement for the exhaust gas flow in the middle to upper rpm range of the internal combustion engine in conjunction with the pulsating application of the engine exhaust flow, which is accompanied by increased ventilation losses in the turbine wheel. This area requirement can probably be met largely by the variability of the tongue slider or by the throughput spread of the variable device of the turbine. Nevertheless, one wishes for efficiency reasons in the variable impact turbines and especially in the simple tongue slider turbine a simple device with which the shock effect can be damped and thus in particular a greater degree of utilization of Radschaufelkanäle at reduced ventilation by the large exhaust gas volume flow can be achieved.

The consequence of a shock-congestion switching is particularly evident in gasoline engines for passenger cars in a strong reduction in fuel consumption in the last engine speed quarter to the engine nominal point, which is also possible with a significant withdrawal of enrichment due to the lowered engine pressures and temperatures in the exit tract.

Object of the present invention is therefore to provide a turbine of the type mentioned, by means of which a particularly simple switchover can be realized, can be switched by a particularly simple way between a shock charging and a congestion charging.

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

In order to create a turbine of the type specified in the preamble of claim 1, by means of which a particularly simple switching possibility can be realized, can be switched by the between a supercharging and a static charge of the internal combustion engine, it is provided according to the invention that the actuating element has at least one connecting channel and is rotatable between at least one connection position and at least one separation position about the rotation axis. In the connection position, the floods are fluidically connected to one another via the connection channel at at least one respective connection point; in the separation position, the flows are fluidically separated from one another at the respective connection point by means of the actuation element. If the adjusting device or the actuating element is in the disconnected position, this, for example, sets a supercharging of the internal combustion engine. In the connection position, however, a congestion charging of the internal combustion engine is set, so that a particularly simple switchover is created by the adjustment, by means of which can be switched between the supercharging and the accumulation charge. As a result, the turbine according to the invention can be adapted in a particularly simple manner to different operating points of the internal combustion engine, so that a particularly efficient, that is fuel-efficient operation of the internal combustion engine with only low emissions can be realized.

At the same time, the turbine according to the invention has a high degree of robustness, since the adjusting device is a simple mechanical adjusting device, for example in the form of a tongue slide. Here, a particularly soft adjustment without discontinuities for an increasing gain of the dust operation or damping of the surge mode can be realized, whereby a particularly advantageous adjustability, in particular controllability or controllability, the turbine is displayed. In other words, it is possible to realize a shock-congestion switching with at least substantially steady behavior.

The floods are feed channels, by means of which the exhaust gas flowing through the floods is led to the receiving space. In the receiving space, a turbine wheel is receivable, which is rotatable about an axis of rotation relative to the turbine housing. The effluent from the floods and flowing into the receiving space exhaust gas flows to the turbine wheel, wherein the turbine wheel is driven by means of the exhaust gas. In the connection position, the supply channels are fluidically connected to each other at the respective connection point via the connecting channel of the actuating element. In the disconnected position, however, the supply channels are fluidly separated from each other by means of the actuating element at the respective connection points.

Preferably, it is provided that, in the connection position, a smallest flow cross-section, via which the flows are fluidically connected to one another, is limited at least partially by the actuating element. It can be provided that the actuating element is rotatable about the axis of rotation in a plurality of connecting positions, wherein by moving the actuating element into the respective connecting positions of the narrowest flow cross section, via which the floods are fluidly connected to each other, is adjustable. In other words, the respective connection positions correspond to respective values of the narrowest flow cross section, via which the flows are fluidically connected to one another. In the disconnected position, the value of the flow cross-section is zero, so that the floods are fluidically separated from one another at the respective connecting positions by means of the actuating element. The setting, that is, the control or regulation of the narrowest flow cross section, through which the floods are fluidly connected to each other in the connecting positions, via the connecting channel, which is formed for example as a Umblasewanne. This means, for example, that the channel is formed by a radially inwardly open and, for example, at least substantially trough-shaped recess of the actuating element.

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 description of the figures and / or in the figures alone can be used not only in the respectively specified combination but also in other combinations or in isolation, without the scope of To leave invention.

The drawing shows in:

1 a schematic representation of an internal combustion engine, with an exhaust gas turbocharger with a turbine, wherein an actuating element has at least one connecting channel and between at least one connecting channel and between at least one connecting position, in which floods of the turbine via the connecting channel at least one respective connection point are fluidly connected to each other, and at least one separation position in which the floods are fluidically separated from each other at the respective connection point by means of the actuating element, about a rotation axis is rotatable;

2 a fragmentary schematic longitudinal sectional view of the turbine;

3 a detail of a schematic plan view of the turbine;

4 a schematic sectional view of the turbine;

5 a diagram illustrating the function of the turbine;

6 Partially a schematic sectional view of the turbine.

In the figures, identical or functionally identical elements are provided with the same reference numerals.

1 shows in a schematic representation of a whole 10 designated internal combustion engine for driving a motor vehicle. The internal combustion engine 10 is presently designed as a reciprocating internal combustion engine and includes a cylinder housing 12 with six combustion chambers in the form of cylinders 14 and 16 , The internal combustion engine 10 includes an exhaust tract 18 , which of exhaust gas of the internal combustion engine 10 can be flowed through. Out 1 is recognizable that the exhaust tract 18 two floods 20 and 22 includes, which are at least partially separated from each other fluidly. By means of one in the exhaust tract 18 arranged exhaust manifold 24 are the cylinders 14 to the first flood 20 and the cylinders 16 to the second flood 22 summarized or merged.

In addition, the internal combustion engine includes 10 an exhaust gas turbocharger 26 with one in the exhaust tract 18 arranged turbine 28 , which is designed for example as a multi-segment turbine or twin-flow turbine. This means that the turbine 28 a turbine housing 30 with two at least partially fluidly separated floods 32 and 34 having.

In synopsis with 4 it can be seen that the turbine housing 30 a recording room 36 in which a turbine wheel 38 around a rotation axis 40 relative to the turbine housing 30 is received rotatably. The flood 32 is fluid with the tide 20 connected, the tide 34 fluidly with the tide 22 connected is. That the floods 20 and 22 flowing exhaust gas is by means of the floods 20 and 22 to the floods 32 and 34 directed, so that the exhaust gas from the floods 20 and 22 emanate and into the floods 32 and 34 can flow in. By means of the floods 32 and 34 the exhaust gas becomes the receiving space 36 led, so that the exhaust gas from the floods 32 and 34 pour out and into the recording room 36 can flow in. This turns the turbine wheel 38 driven by the exhaust gas. Out 4 it can be seen that the feed channels or floods 32 and 34 at least substantially helically in the direction of contact of the turbine wheel 38 extend over its circumference, leaving the floods 32 and 34 of the turbine housing 30 also referred to as spiral channels or spiral segments.

The internal combustion engine 10 also includes an intake system 42 over which the internal combustion engine 10 Air sucks during their operation. In the intake tract 42 is an air filter 44 arranged to filter the air. In addition, in the intake tract 42 a compressor 46 the exhaust gas turbocharger 26 arranged. The compressor 46 includes a compressor wheel disposed in the intake tract 48 which with a wave 50 the exhaust gas turbocharger 26 rotatably coupled. Also the turbine wheel 38 is with the wave 50 rotatably coupled, so that the compressor wheel 48 over the wave 50 from the turbine wheel 38 can be driven. By means of the compressor wheel 48 becomes the intake tract 42 compressed air is compressed by the compressor wheel 48 over the wave 50 from the turbine wheel 38 is driven. As a result, energy contained in the exhaust gas can be used to compress the air, so that a particularly efficient operation of the internal combustion engine 10 can be realized.

Through the through the compressor 46 caused compression of the air is heated. To represent a particularly high degree of supercharging, is in the intake 42 downstream of the compressor 46 a cooling device in the form of a charge air cooler 52 arranged, by means of which the compressed and thus heated air is cooled. Downstream of the intercooler 52 is in the intake tract 42 a charge air distributor 54 arranged, by means of which the compressed air to the cylinder 14 and 16 is distributed.

The internal combustion engine 10 also includes an exhaust gas recirculation device 56 with at least one exhaust gas recirculation line 58 , which on the one hand fluidly with the flood 20 and on the other hand with the intake tract 42 connected is. At a branch point A, at which the exhaust gas recirculation line 58 fluidly with the tide 20 connected, at least part of the tide 20 branched off exhaust gas and diverted into the exhaust gas recirculation line 58 be initiated. The exhaust gas recirculation line 58 is at a feed Z fluidly with the intake 42 connected, so that the exhaust gas recirculation line 58 flowing exhaust gas at the feed Z in the intake tract 42 is initiated. The feed Z is also referred to as a mixing point, since at the feed Z, the exhaust gas with the intake 42 flowing air mixes.

The exhaust gas recirculation device 56 includes a in the exhaust gas recirculation line 58 arranged exhaust gas recirculation valve 60 , By means of which the amount of the exhaust gas recirculation line 58 flowing exhaust gas is adjustable. In the flow direction of the exhaust gas through the exhaust gas recirculation line 58 is downstream of the exhaust gas recirculation valve 60 and upstream of the feed point Z, an exhaust gas recirculation cooler 62 arranged, by means of which the recirculated exhaust gas is cooled.

The floods 32 and 34 are symmetrical or asymmetrical. This means that the floods 32 and 34 have respective symmetrical cross sections through which the exhaust gas can flow, or asymmetrical cross sections. The flood 20 which the cylinders 14 is assigned, by design has the task of the exhaust gas recirculation demand of the internal combustion engine 10 in order to minimize raw nitrogen emissions (raw NO _x emissions). By means of the exhaust gas recirculation device 56 is a so-called exhaust gas recirculation (EGR) can be displayed, in whose frame exhaust gas from the exhaust system 18 to the intake tract 42 returned and in the intake 42 is initiated. The flood 20 is therefore also referred to as AGR flood. The flood 22 the turbine 28 should provide high levels of efficiency to the air supply of the internal combustion engine 10 that is the cylinder 14 and 16 throughout the operating area. In other words, the tide has 22 in particular the task, also referred to as λ fuel-air ratio in the respective cylinders 14 and 16 adjust, so that the tide 22 Also referred to as λ-flood.

Out 4 is recognizable that the tide 32 in the circumferential direction of the turbine wheel 38 extends over its circumference over a wrap angle φ _Ages . The wrap angle φ _{Ages of} the first tide 32 results from φ _AE -φ _A0 . Here, φ _{A0 is} an initial _angle at which a spiral _{inlet cross-section} A _{sA0 of} the first tide 32 is arranged. Further, φ _{AE is} an end angle at which an end of the first tide 32 is arranged. In this case, the wrap angle φ _{Ages of} the first flood 32 in the present case substantially 216 °. In other words, the first tide extends 32 for example, starting from an angle φ = φ _A0 = 0 ° to an angle φ = φ _AE = 216 °.

Accordingly, the second flood extends 34 in the circumferential direction of the turbine wheel 38 over its circumference over a wrap angle φ B _ges , which results from φ _BE -φ _B0 . In this case, φ _{B0 is} an initial _angle at which a spiral _{inlet cross-section} A _{sB0 of} the second tide 34 is arranged. Further, φ _{BE is} an end angle at which one end of the second tide 34 is arranged. In other words, the second tide extends 34 starting from an angle φ = φ _B0 = 216 ° up to an angle φ = φ _BE = 360 °. The wrap angle φ _Bges is thus 144 °.

The floods 32 and 34 are at least partially fluidly separated from each other and arranged in the direction of contact one behind the other, that is, connected in series. The turbine 28 is thus designed as a segment turbine or multi-segment turbine.

Alternatively, it is conceivable that the turbine 28 is designed as a twin-flow turbine. Here the floods open 32 and 34 not as in the segment turbine in the circumferential direction of the turbine wheel 38 one behind the other in the reception room 36 but in the axial direction of the turbine 28 side by side. Again, the floods 32 and 34 at least substantially spiral in the circumferential direction of the turbine wheel 38 extend over its circumference. Furthermore, the turbine includes 28 an adjusting device 64 in the form of a so-called tongue slider, which two Versperrkörper in the form of tongues 66 and 68 includes. The tongue 66 is the first flood 32 associated with the tongue 68 the second flood 34 assigned. The first tongue 66 serves for adjusting at least one first flow cross-section through which the exhaust gas can flow through 32 , where the second tongue 68 for adjusting a second flow cross-section of the second flow which can be flowed through by exhaust gas 34 serves. For example, the floods open 32 and 34 via respective flow cross sections in the receiving space 36 , These flow cross sections by means of the tongues 66 and 68 are adjustable. In other words, for example, the flow cross section, over which the hat 32 in the recording room 38 flows through the tongue 66 adjustable, wherein the flow cross section, over which the flood 34 in the recording room 38 flows through the tongue 68 is adjustable.

In addition, the adjustment comprises 64 a tongue 66 and 68 common actuator in the form of a ring 70 with which the tongues 66 and 68 are connected. The ring 70 is at least substantially concentric with the axis of rotation 40 arranged and around the axis of rotation 40 relative to the turbine housing 30 rotatable. Because the tongues 66 and 68 with the ring 70 connected, the tongues become 66 and 68 when turning the ring 70 around the axis of rotation 40 rotated, so that the respective flow cross sections of the floods 32 and 34 by turning the ring 70 and concomitant turning of the tongues 66 and 68 be set.

Downstream of the turbine 28 is one out 1 recognizable exhaust aftertreatment device 72 in the exhaust tract 18 arranged. Furthermore, it is off 1 a computing device 74 recognizable, by means of which the tongue slide (adjusting 64 ), that is controlled or preferably regulated.

In order to realize a switching possibility in a particularly simple way, by means of which between a through the exhaust gas turbocharger 26 caused bumping and congestion charge can be switched, the ring points 70 at least one connection channel W on, which - particularly good 2 can be seen - by a radially inwardly open and at least substantially trough-shaped recess of the ring 70 is formed and arranged in a ring slide area ZS_UM.

The ring 70 is between at least one in 1 to 3 shown connection position and at least one separation position about the axis of rotation 40 rotatable.

In the connecting position are the floods 32 and 34 the turbine 28 connected fluidically to each other via the connecting channel W at at least one respective connection point, so that, for example, exhaust gas from one of the floods 32 and 34 in the corresponding other flood 34 respectively 32 can overflow. This overflow is also referred to as blow-over, so that a Umblasevorrichtung is created by the tongue slider. In other words, the tongue slider not only includes the simultaneously displaceable tongues 66 and 68 for throughput and capacity control of the turbine 28 but also a Umblasevorrichtung, by means of which the possibility is created to switch between a shock charging or a Stoßaufladebetrieb and a congestion charging or a Stauaufladebetrieb.

In the release position of the tongue slider are the floods 32 and 34 at the respective connection point by means of the ring 70 fluidly separated from each other, so that, for example, in the disconnected position, the bump charge is set. In contrast, the congestion charge is set in the connection position.

Overall, it can be seen that a setting, that is, control or regulation of the narrowest flow cross-section, over which the floods 32 and 34 are fluidically connected to each other at the respective connection point, takes place via the formed as a Umblasewanne connection channel W, which is located on the annular valve area ZS_UM and by the rotational movement of the ring 70 determines the opening and closing of said narrowest flow cross-section. Depending on the need for flow surfaces and sensitivity or Umblaseverstellbereich results in the design of the Umblasewanne in conjunction with the dimensioning and orientation of 1 and very good 3 recognizable Umblasekanäle 76 and 78 located in the turbine housing 30 extend. In the connection position are the Umblasekanäle 76 and 78 fluidly connected to each other via the connecting channel W. The Umblasekanal 76 flows into the flood 32 , wherein the Umblasekanal 78 into the flood 34 empties. In the connecting position open both Umblasekanäle 76 and 78 in said recess and thus the connecting channel W. In the disconnected position are the Umblasekanäle 76 and 78 by means of the ring 70 fluidly obstructed and separated, so that the floods 32 and 34 to the respective, in 3 V connection points are fluidly separated from each other. In the connecting position, however, are the floods 32 and 34 at the respective connection positions V fluidly connected to each other and thereby short-circuited. It is conceivable that due to a large area requirement of the narrowest flow cross section, over which the floods 32 and 34 are interconnected in the connecting position and which is also referred to as Umblasequerschnitt, a parallel connection of several channels or Umblasewannen on the circumference of the ring 70 can be arranged. In other words, it is preferably provided that the ring 70 has at least one further connecting channel, wherein the floods 32 and 34 in the connection position also fluidly connected to each other via the further connection channel at at least one respective further connection point and in the disconnected position at the respective further connection point by means of the ring 70 are fluidly separated from each other.

Out 3 is the principle of said Umblasung and adjustment of the Umblasewanne (connecting channel W) to the Umblasekanälen 76 and 78 recognizable. Based on 3 It can be seen that the Umblasewanne in the conventional ring 70 , which is also referred to as an annular slide, is integrated and the separation and connection of the Umblasekanäle 76 and 78 accomplished to the turbine inlet area in front of the respective feed channels.

4 shows the turbine 28 in a section perpendicular to the axis of rotation 40 , Out 4 is the location of the Umblasekanäle 76 and 78 recognizable.

Out 4 is also one of the tides 32 assigned connection flange 80 recognizable over which the tide 32 with the tide 20 can be fluidly connected. Also the flood 34 is assigned a connecting flange, over which the flood 34 fluidly with the tide 22 can be connected. The flood 34 assigned connection flange is in 4 not recognizable because of the tide 34 associated connection flange with respect to the image plane of 4 behind the connecting flange 80 is arranged. In other words, the connection flanges are related to the image plane of 4 one above the other.

5 shows a graph showing the function of the turbine 28 is recognizable. Based on 5 the critical turbine flow rate _parameter Φ _crit is shown, which is on the ordinate 82 is applied. The tongue slider is adjustable in an adjustment, that is rotatable, so that respective rotational positions of the tongue slider can be adjusted by turning the tongue slider to respective adjustment. The displacement angle of the tongue slider is also denoted by ε and is in 5 plotted on the abscissa in the unit degrees. Out 5 shows that the adjustment of the tongue slider from an adjustment angle ε = 0 ° up to an adjustment angle ε = 60 °, so that the adjustment range is 60 °. From ε = 0 ° to ε = 40 ° extends a so-called Umblasebereich U, in which the floods 32 and 34 via the connecting channel W of the ring 70 fluidly connected to each other. From ε = 0 ° to ε = 20 ° extends a so-called blow-off area A, in which a blow-off of exhaust gas takes place. Out 5 the turbine-slump behavior is evident in critical and supercritical turbine pressure ratio. If the turbine stationary, that is, for example, applied to a component exhaust gas turbocharger test stand, results in a solid curve 86 , which is also called maximum line. With pulsating partial admission of the turbine 38 In engine operation, the ability to swallow is the turbine designed as an adjustable tongue-and-groove segment turbine 28 only about 50% to about 75% of the full application without being blown, which is essentially related to the specific design of the tongues 66 and 68 and their distance and any leakage currents and the Radaustrittsquerschnitt with the wheel-housing gap is. A course 88 illustrates the Teilbeaufschlagung the present symmetric segments (floods 32 and 34 ) in engine operation. With Amax the maximum increase through blowdown is illustrated. If the Umblasevorrichtung actuated, in the present case between ε = 40 ° and ε = 0 °, then results in an approximation of the two courses to the maximum opening case of the adjustment angle with appropriate design of the Umblasevorrichtung 86 and 88 the throughput capability until an overlap of the partial application with the full application in the opening case ε = 0 ° sets. For example, on the ring 70 also blow-off openings are activated or provided in an adjustment range of ε = 20 ° to ε = 0 ° for Radbypassierung. About such a blow-off, at least a portion of the exhaust gas, the turbine wheel 38 bypass. This is understood to mean that the exhaust gas flowing through the blow-off opening bypasses the turbine wheel and does not drive it, which is also referred to as bypassing.

6 shows prominent positions of the tongue slider or the tongues 66 and 68 , present on the example of the tongue 66 , between the maximum opening state at ε = 0 ° to the minimum turbine absorption capability at ε = 60 °. At ε = 0 °, a maximum tap cross-section results from A _{S, 0} + A _{blow-off, max} + A _{blow-by, max} . This means that at ε = 0 ° not only the floods 32 and 34 are fluidly connected to each other via the connecting channel W, but also a bypassing of the turbine wheel takes place. At ε = 20 °, the blow-off or bypassing is closed, that is ended, the floods 32 and 34 are still fluidly connected to each other via the connecting channel W. From ε = 40 ° to ε = 60 ° is an overlap, so that the Umblasekanäle 76 and 78 by means of the ring 70 are fluidly obstructed and separated from each other, so that the floods 32 and 34 at the respective connection points V by means of the ring 70 are completely separated from each other. At ε = 60 °, this results in a minimum tap cross-section A _{S, min} , since both the blowing and the blowing off are deactivated. In an adjustable range of 40 °, in this case from ε = 0 ° to ε = 40 °, the Umblasung hiss the floods 32 and 34 because these are fluidly connected to each other via the connecting channel W.

LIST OF REFERENCE NUMBERS

10

Internal combustion engine

12

cylinder housing

14

cylinder

16

cylinder

18

exhaust tract

20

flood

22

flood

24

exhaust manifold

26

turbocharger

28

turbine

30

turbine housing

32

first tide

34

second tide

36

accommodation space

38

turbine

40

axis of rotation

42

intake system

44

air filter

46

compressor

48

compressor

50

wave

52

Intercooler

54

Charge-air distributor

56

Exhaust gas recirculation device

58

Exhaust gas recirculation line

60

Exhaust gas recirculation valve

62

Exhaust gas recirculation cooler

64

adjustment

66

tongue

68

tongue

70

ring

72

exhaust treatment device

74

computing device

76

Umblasekanal

78

Umblasekanal

80

connecting flange

82

ordinate

84

abscissa

86

course

88

course

A

Blow off

Amax

maximum increase due to blow-off

U

Umblasebereich

W

connecting channel

ZS_UM

Annular slide area

ε

displacement

A _Ages

Wrap angle

φ _A0

Starting angle

φ _B0

Starting angle

φ _AE

end angle

φ _BE

end angle

A _SA0

Spiral inlet cross-section

A _SB0

Spiral inlet cross-section

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102008039085 A1 [0002]

Claims (4)

Turbine ( 28 ) for an exhaust gas turbocharger ( 22 ), in particular an internal combustion engine ( 10 ), with at least one a receiving space ( 36 ) for a turbine wheel ( 38 ) turbine housing ( 30 ), which comprises at least two floods through which exhaust gas can flow and at least partially separated from one another by fluid ( 32 . 34 ), and with an adjusting device ( 64 ), which at least one about a rotation axis ( 40 ) rotatable first locking body ( 66 ) for adjusting at least one exhaust flow-through first flow cross-section of a first of the floods ( 32 . 34 ), at least one about the axis of rotation ( 40 ) rotatable second locking body ( 68 ) for adjusting at least one second flow cross-section through which the exhaust gas can flow ( 34 ) as well as the locking bodies ( 66 . 68 ) and around the axis of rotation ( 40 ) rotatable actuator ( 70 ), over which the Versperrkörper ( 66 . 68 ) about the axis of rotation ( 40 ) are rotatable, characterized in that the actuating element ( 70 ) has at least one connecting channel (W) and between at least one connecting position, in which the floods ( 32 . 34 ) are fluidically connected to one another via the connecting channel (W) at at least one respective connecting point (V), and at least one separating position in which the floods ( 32 . 34 ) at the respective connection point (V) by means of the actuating element ( 70 ) are fluidly separated from each other about the axis of rotation ( 40 ) is rotatable. Turbine ( 28 ) according to claim 1, characterized in that the connecting channel (W) by a radially inwardly open recess of the actuating element ( 70 ) is formed. Turbine ( 28 ) according to claim 1 or 2, characterized in that the turbine ( 28 ) is designed as a multi-segment turbine or twin-flow turbine. Turbine ( 28 ) according to one of the preceding claims, characterized in that the actuating element ( 70 ) has at least one further connecting channel, the floods ( 32 . 34 ) in the connecting position via the further connecting channel to at least one respective further connection point fluidly connected to each other and in the disconnected position at the respective further connection point by means of the actuating element ( 70 ) are fluidly separated from each other.

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