DE102011121868A1 - Turbine e.g. radial turbine, for turbocharger of e.g. Otto engine of passenger car, has control device variably adjusting flow cross-section that is independent of fluidic connection and separation of vents, which supply gas to wheel - Google Patents

Abstract

The turbine (10) has two vents (22, 24) supplying exhaust gas to a turbine wheel (16). A control device (32) is displaced between separation and connection positions, and adjusts two flow cross-sections. The flow cross-sections fluidically connect the vents with each other in the connection position, and fluidically separate the vents from each other in the separation position. The control device variably adjusts a third flow cross-section, which is independent of the fluidic connection and separation of the vents, where the exhaust gas flows through the third flow cross-section.

Description

The invention relates to a turbine for an exhaust gas turbocharger specified in the preamble of claim 1. Art.

The current and probably future development of internal combustion engines leads to charge the internal combustion engines by means of respective exhaust gas turbocharger. This applies to both gasoline engines and diesel engines. In order to keep the fuel consumption and thus the CO ₂ emissions particularly low, the internal combustion engines are designed according to the so-called downsizing principle. In this case, the internal combustion engines only a relatively small engine volume, but can provide very high power and torque. Due to the resulting high specific performance, the requirements for charging devices for charging the internal combustion engines are growing steadily. Here, the conflict of objectives between the resulting from the downsizing, high Aufladegraden and a desired instationärverhalten to represent acceptable driving behavior of the internal combustion engines to meet.

Turbines for exhaust gas turbochargers comprising a turbine housing are known from the general state of the art. The turbine housing has a receiving space for a turbine wheel of the turbine and at least two floods through which exhaust gas can flow. The exhaust gas can be supplied to the turbine wheel via the floods so that the exhaust gas can drive the turbine wheel.

Furthermore, it is known that the turbine of an exhaust gas turbocharger comprises an adjusting element, which is adjustable between a disconnected position and at least one connecting position. By means of the adjusting element, the floods are fluidically separated from each other at least in a partial area in the separating position and are fluidically connected to one another in the connecting position, at least in a partial area.

If such a turbine is used, for example, in a four-cylinder internal combustion engine, two of the cylinders are respectively fluidly connected to only one of the turbine's flows, whereby the exhaust gas from the respective two cylinders is brought together. This has the advantage that volumes and flow cross sections of exhaust valves of the internal combustion engine are very small up to the entry of the turbine. Thus, the kinetic energy of the exhaust gas can be used very efficiently with regard to an impact charge.

On the other hand, this so-called cylinder summary, wherein the exhaust gas of the merged cylinder does not influence each other, to the fact that residual gas can be very advantageously flushed out of the cylinders.

A disadvantage of multi-flow turbines, however, is that the small volumes and the very small flow cross sections, which can still have a positive effect on the provision of high torques and the instationary behavior in the range of low speeds of the internal combustion engine, at high speeds and / or benefits of Internal combustion engine are usually too small. This results in high exhaust back pressures and high specific fuel consumption. To counteract this problem, the adjusting element is provided, by means of which the floods can be fluidly connected to each other. However, these known turbines have a further improvement in operability.

It is an object of the present invention, a turbine for an exhaust gas turbocharger of the type mentioned in such a way that the turbine is particularly efficient operable.

This object is achieved by a turbine for an exhaust gas turbocharger having the features of patent claim 1. Advantageous embodiments with expedient and non-trivial developments of the invention are specified in the remaining claims.

Such a turbine for an exhaust gas turbocharger comprises a turbine housing. The turbine housing has a receiving space in which a turbine wheel of the turbine is received at least partially. The turbine housing further has at least two floods, via which exhaust gas for driving the turbine wheel can be fed to the turbine wheel.

The turbine comprises at least one adjusting device adjustable between a disconnected position and at least one connecting position, by means of which at least one first flow cross-section is fluidically separable from one another and fluidically interconnecting in the connecting position.

According to the invention, by means of the adjusting device, a further flow cross-section of the turbine through which the exhaust gas can flow and which is independent of the fluidic connection and separation of the flows can be variably set. The adjustable, further flow cross section is also referred to as the effective flow cross section of the turbine.

The turbine according to the invention has, on the one hand, the advantage that it permits the representation of particularly small volumes and flow cross sections from an outlet of at least one combustion chamber, in particular of a cylinder, an internal combustion engine until the turbine wheel inlet allows when the actuator is in its release position. Thus, the kinetic energy of the exhaust gas can be efficiently utilized for driving the turbine wheel, so that the internal combustion engine is efficiently and effectively rechargeable. In particular, this makes it possible to design the associated internal combustion engine particularly pronounced according to the described downsizing principle. This leads to a particularly low weight of the internal combustion engine. Nevertheless, the internal combustion engine can provide particularly high power and torque, since it can be heavily charged by means of the exhaust gas turbocharger with the turbine according to the invention. For this purpose, the exhaust gas turbocharger also comprises a compressor with a compressor wheel which can be driven by the turbine wheel of the turbine according to the invention.

The fluidic separation of the floods of the turbine according to the invention thus enables the representation of a so-called surge charging, in which exhaust gas pulses or exhaust gas pulses are used for efficient and effective driving of the turbine.

If the internal combustion engine has a plurality of cylinders, then at least two first cylinders can be fluidly connected to a first one of the turbine passages, while at least two further cylinders of the internal combustion engine can be fluidically connected to the second turbine of the turbine according to the invention. The exhaust gas from the respective, merged cylinders does not influence each other, in particular due to an exhaust valve overlap. As a result, in particular residual gas can be flushed out of the cylinders particularly efficiently and effectively, which leads to a low tendency for the internal combustion engine to knock.

In addition, the flow separation of the turbine according to the invention in the disconnected position advantageous operating strategies are possible, such as a targeted flushing of the cylinder with fresh air (the so-called scavenging method). These operating strategies lead to an advantageous operating behavior of the internal combustion engine, so that the internal combustion engine can provide relatively high torques even at low speeds. This leads to low fuel consumption and low CO ₂ emissions.

A further advantage of the relatively small volumes and flow cross sections is that this makes possible a very advantageous instationary behavior of the turbine. This benefits a very good drivability of the internal combustion engine. In other words, thereby a very good run-up behavior of the turbine is realized, for example in vehicle accelerations, wherein the so-called turbo lag can be at least substantially avoided. In this case, the turbine according to the invention has high efficiencies even at relatively low exhaust gas flow rates.

However, the turbine according to the invention can also be operated efficiently and therefore with low efficiency, even if the exhaust gas flow rates are high, since the floods in the connection position are fluidically connected to one another by means of the adjusting device.

By adjusting the actuator of the thrust charging enabling separation position in the connection position is a congestion charging operation of the turbine and thus the exhaust gas turbocharger allows. Due to the fluidic connection of the floods, larger flow cross sections and volumes for the exhaust gas are available with respect to the separating position, which keeps the pressure upstream of the turbine wheel or the turbine and thus the exhaust backpressure low. As a result, the problems of the at least twin-flow turbine mentioned at the outset, which can lead to an undesirably high exhaust gas counterpressure and thus to undesirably high fuel consumption at relatively high exhaust gas flow rates, can be avoided. In other words, the adjusting device is adjusted in operating ranges of low speeds and / or powers of the internal combustion engine in its disconnected position, so that the floods are fluidly separated from each other. As a result, the advantages of a twin-flow turbine are effective, which allows the representation of very high torque at low speeds and has an advantageous transient behavior.

In contrast, higher speeds and / or performance of the internal combustion engine adjusting device is adjusted to its connection position, so that at high exhaust gas flow rates and thus at high exhaust gas mass flows flowing through the turbine undesirably high exhaust back pressures and thus undesirable high fuel consumption can be avoided.

The turbine according to the invention thus has a very high throughput spread, which is advantageous in particular in a gasoline engine as an internal combustion engine. In particular, in a gasoline engine there is a high spread of the exhaust gas mass flows, to which the turbine according to the invention can be adapted as needed and efficiently.

The turbine according to the invention has a particularly high throughput spread, as well as the effective flow cross-section by means of the adjusting device as needed and at least substantially optimally adjustable and so to different Exhaust gas mass flows can be adjusted. Thus, the effective flow cross-section is adjustable to a particularly low value as well as to a particularly large value, so that the turbine according to the invention can be efficiently flowed through and driven both by very high exhaust gas mass flows and by very low exhaust gas mass flows.

The turbine according to the invention is preferably designed as a radial turbine, in which the turbine wheel is at least substantially flowed radially from the exhaust gas. The turbine can also be designed as a mixed-flow turbine, in which the turbine wheel is flowed obliquely to the axial direction and obliquely to the radial direction of the exhaust gas.

For adjusting the first flow cross section and the further flow cross section, the adjusting device may comprise respective adjusting elements. Preferably, both the first flow cross section and the further flow cross section can be adjusted by means of only a single actuating element of the adjusting device. This keeps the number of parts and the space required low.

In an advantageous embodiment, at least one guide element is provided upstream of the turbine wheel, by means of which the exhaust gas flowing to the receiving space can be diverted. As a result, the turbine wheel can be streamlined against the exhaust gas, which is accompanied by an efficient and efficient operation of the turbine according to the invention.

Advantageously, a plurality of guide elements, in particular guide vanes, are provided, which are arranged distributed in the circumferential direction of the turbine wheel over its circumference at least substantially uniformly. As a result, the turbine wheel can be flowed over the circumference thereof in a particularly efficient and streamlined manner by the exhaust gas.

In an advantageous embodiment of the invention, the adjusting device comprises at least one adjusting element, by means of which for adjusting the further flow cross-section, the guide element in the flow direction of the exhaust gas only at least partially coverable on one side of the guide element. In this case, the guide element is preferably at least partially coverable on a side facing away from the turbine wheel by means of the first control element. As a result of the only one-sided overlap of the guide element by means of the adjusting device or its actuator so-called secondary flow losses can be avoided or kept very low. This benefits the efficient operation of the turbine according to the invention.

The adjusting element is preferably a so-called axial slide of the adjusting device, which is displaceable in the axial direction of the turbine relative to the turbine housing. The axial slide has a relatively simple structure. This leads to a high degree of robustness, in particular with regard to the application of high temperatures, resulting in a high functional reliability of the turbine and thus of the exhaust gas turbocharger.

The axial slide is also particularly robust against pressure pulsations of the exhaust gas, which occur especially in the impact charge. Furthermore, thereby the space requirement and the cost of the turbine according to the invention can be kept in a particularly small scope.

In a further advantageous embodiment of the invention, the adjusting device is adjustable between a fluidically maximally narrowing the further flow cross-blocking position and at least one further flow cross-section releasing release position, wherein the adjusting device is moved to its release position when the actuator is also adjusted in its blocking position. In other words, the floods are at least fluidically separated from one another in the subregion, even if the further flow cross section of the turbine is maximally constricted. The exhaust gas can thus not flow over between the floods. The turbine according to the invention then has particularly small volumes and flow cross sections, which leads to a very good operation with low exhaust gas mass flows at low speeds and / or powers of the internal combustion engine.

If, starting from an operating point at which relatively low exhaust gas mass flows are present, a change in the operating point of the internal combustion engine to higher exhaust gas mass flows, the turbine according to the invention has a particularly advantageous run-up behavior and thus a very good transient behavior, whereby the so-called turbo lag can be avoided , In other words, the turbine according to the invention or its turbine wheel can be accelerated very well.

It is preferably provided that the fluidic connection of the floods, d. H. starting from the disconnected position in the direction of the connection position, with a release of the flow cross-section, d. H. is accompanied by a successive enlargement of the further flow cross-section.

Advantageously, the adjusting device is adjustable in at least a first intermediate position between the locking position and the release position. In the first intermediate position is the first flow cross section fluidly released, but is narrowed relative to the blocking position. Advantageously, the adjusting device is at least substantially continuously adjustable in a plurality of first intermediate positions.

Preferably, the adjusting device is adjustable in at least one second intermediate position between the separating position and the connecting position, wherein the first flow cross-section is narrowed in the second intermediate position relative to the connecting position and enlarged relative to the separating position. The adjusting device is preferably at least substantially continuously adjustable in a plurality of second intermediate positions.

It is preferably provided that with a reduction of the further flow cross-section also a reduction of the first flow cross section is accompanied and vice versa.

In a further advantageous embodiment, the turbine, in particular the turbine housing, at least one arranged upstream of the turbine wheel additional space in which exhaust gas from the floods can be introduced and which can be released for introducing exhaust gas into the additional space by means of the actuator and to prevent the introduction of exhaust gas the additional space is fluidically shut off by means of the adjusting device. As a result of the release of the additional space, so that exhaust gas from both floods can flow into the additional space, the turbine has particularly large volumes (flow volumes), which is particularly advantageous at high exhaust gas mass flows. As a result, the exhaust backpressure can be kept low, resulting in low fuel consumption and thus low CO ₂ emissions of the internal combustion engine.

Preferably, the adjusting device is received in at least partially the additional space. Thus, the already existing additional space is used both for receiving one of the actuators and for displaying particularly large flow volumes of the turbine according to the invention. This is beneficial to the low space requirement of the turbine according to the invention. The additional space can also be used as a pulsation damper, which dampens exhaust fumes.

Further advantages, features and details of the invention will become apparent from the following description of preferred embodiments 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 serve 1 and two for explaining the background of the invention.

The drawing shows in:

1 a schematic longitudinal sectional view of a turbine for an exhaust gas turbocharger,

2 Partially a schematic cross-sectional view of the turbine according to 1 ;

3 a schematic longitudinal sectional view of another embodiment of the turbine according to the 1 and 2 which comprises an adjusting device, by means of which a very high throughput spread of the turbine is made possible and by means of which the turbine can be adapted efficiently and as needed to different exhaust gas mass flows;

4 a schematic cross-sectional view of the turbine according to 3 ;

5 a further schematic longitudinal sectional view of the turbine according to the 3 and 4 ;

6 a schematic cross-sectional view of the turbine according to 5 ;

7 a diagram illustrating the function of the adjusting device of the turbine according to the 1 to 6 ; and

8th a schematic longitudinal sectional view of another embodiment of the turbine according to the 1 to 7 ,

The 1 and 2 show a turbine 10 for an exhaust gas turbocharger of an internal combustion engine. The internal combustion engine is designed for example as a reciprocating internal combustion engine and comprises a plurality of combustion chambers in the form of cylinders. The internal combustion engine can be used in passenger car and Nutrkraftwagenanwendungen and in other applications and formed, for example, as gasoline engine, diesel engine, Diesottomotor or other internal combustion engine.

The turbine 10 includes a turbine housing 12 , The turbine housing 12 has a recording room 14 on which a turbine wheel 16 the turbine 10 at least partially included. The turbine wheel 16 is about a rotation axis 18 relative to the turbine housing 12 rotatable and with a while 20 rotatably connected. In this case, the turbine wheel 16 with the wave 20 be formed integrally.

The exhaust gas turbocharger also includes a compressor with a compressor wheel which also rotatably with the shaft 20 connected is. This allows the compressor wheel from the turbine wheel 16 are driven.

As in synopsis with the 2 can be seen, the turbine housing has 12 a first flood 22 as well as a second hat 24 on. Here is the turbine housing 12 designed in segmental design. The floods 22 . 24 are formed as spiral flow channels, which are each in the circumferential direction of the turbine wheel 16 extend over the circumference at least substantially helically and via which the turbine wheel 16 Exhaust gas of the internal combustion engine is supplied from the cylinders.

For example, if the internal combustion engine includes a first cylinder, a second cylinder, a third cylinder, and a fourth cylinder, the first cylinder and the fourth cylinder are fluid with the first flow 22 while the second cylinder and the third cylinder are fluidly connected to the second tide 24 are connected. The floods 22 . 24 extend over a respective wrap angle α of at least substantially 180 °. The floods 22 . 24 direct the exhaust gas to an inflow channel 25 over which the exhaust gas enters the receiving space 14 to the turbine wheel 16 flows.

Upstream of the turbine wheel 16 is a guide grid 26 with a plurality of vanes 28 arranged. The vanes 28 are at least partially in the inflow channel 25 arranged and relative to the turbine housing 12 fixed, ie immovable. The vanes 28 ensure a streamlined flow of the turbine wheel 16 from the exhaust.

How the particular 2 can be seen, are two of the vanes 28 designed and arranged to have a respective extension of tongues 30 of the turbine housing 12 represent. As a result, the flooding is - apart from any, minimal leakage 22 . 24 fluidly separated, so that the respective floods 22 . 24 flowing exhaust gas is not influenced by each other.

The turbine 10 according to the 1 and 2 also includes an adjusting device with a so-called axial slide 32 , by means of which an effective flow cross-section of the inflow channel 25 is variably adjustable. The 1 shows the axial slide 32 in its blocking position, in which the effective flow cross-section of the inflow channel 25 and thus with the turbine 10 maximum is narrowed. Again 1 it can be seen, the exhaust gas, the vanes 28 in the blocking position of the axial slide 32 only in a small area 34 stream and over the subarea 34 to the turbine wheel 16 stream.

Will be in the axial direction of the turbine 10 relative to the turbine housing 12 translationally displaceable axial slide 32 adjusted in its release position, the effective flow cross-section is increased. By this narrowing and on the other hand releasing the effective flow cross section, the turbine 10 can be adjusted variably, according to requirements and efficiently with regard to their damming behavior and adapted to different exhaust gas mass flows. This results in efficient operation of the turbine 10 ,

For adjusting the axial slide 32 is an adjustment mechanism 36 provided the adjusting device, which in a Verstellraum 38 of the turbine housing 12 is included.

The 3 to 6 show a way to the turbine 10 according to the 1 and 2 even more variable to adapt to different exhaust gas mass flows and thus to be able to operate even more efficiently. As in synopsis of 3 with the 4 to 6 is recognizable, are by means of the axial slide 32 also a first overflow cross section A1 and a second overflow cross section A2 variably adjustable. The overflow cross sections A1, A2 form a Gesamtüberströmquerschnitt.

The axial slide 32 is relative to the turbine housing 12 at least substantially continuously adjustable between a disconnected position and a connection position. In the release position, the total overflow cross-section is fluidly blocked, so that the floods 22 . 24 are fluidly separated from each other. This means that the floods 22 . 24 flowing exhaust gas not between the floods 22 . 24 can overflow.

In the connecting position are the floods 22 . 24 fluidly connected to each other, so that the exhaust gas from the floods 22 . 24 between the floods 22 . 24 can overflow. In the disconnected position, a surge charging operation of the exhaust gas turbocharger can thus be carried out, while in the connecting position a congestion charging operation of the exhaust gas turbocharger can be represented.

This means that in the connecting position an overflow of exhaust gas from the first flood 22 in the first tide 24 is made possible over the first overflow A1. Conversely, in the connection position, exhaust gas from the second flood 24 in the first tide 22 overflow over the second overflow cross section A2.

Here is the blocking position of the axial slide 32 set, even if its disconnected position is set or vice versa. Is the axial slide 32 set in its release position, it is also set in its connection position and vice versa.

The overflow cross sections A1, A2 are in the release position of the axial slide 32 , in which the effective flow cross-section of the turbine 10 is released to the maximum, laterally through an axial end face 46 the Leitgitters 26 as well as from a wall 48 of the turbine housing 12 between the floods 22 . 24 and the adjustment room 38 limited.

Between the displacement of the axial slide 32 and the overcurrent sections A1, A2 there is an at least substantially linear relationship. At maximum open axial slide 32 That is, when it is in its release position, the two overflow A1, A2 are maximally enabled, ie the largest. With closed turbine 10 ie when the axial slide 32 located in its blocking position and in the axial direction on end faces of the guide grid 26 is applied, the two overflow A1, A2 are closed, ie fluidly shut off at least substantially.

This means that by moving the axial slide 32 in the axial direction, both the effective flow area of the turbine 10 as well as the total cross-section of the turbine 10 between the floods 22 . 24 at least substantially continuously adjustable. Is doing by moving the axial slide 32 the effective flow cross-section increases, so also the Gesamtüberströmquerschnitt is increased and vice versa.

The axial slide 32 the turbine 10 according to the 3 to 8th can do the vanes 28 in the flow direction of the exhaust gas through the inflow channel 25 only on one side, on one turbine wheel 16 opposite side of the vanes 28 cover. As a result, secondary flow losses can be avoided or kept low.

The 7 shows a diagram 50 , on the abscissa 52 the adjustment or displacement of the axial slide 32 between his with 54 marked blocking position and its with 56 marked release position is applied. On the ordinate 58 the effective flow cross-section and the total cross-section are plotted. A first course 60 characterizes the effective flow area, while a second course 62 characterized the Gesamtüberströmquerschnitt.

Starting from the blocking position 54 of the axial slide 32 becomes with increasing way of the axial slide 32 , ie in its successive movement in the direction of the release position 56 , which increases effective flow area. This is accompanied by the enlargement of the total cross-section. In the release position, both the effective flow cross section and the Gesamtüberströmquerschnitt maximum.

The 8th shows a possibility of particularly large flow cross sections and flow volumes of the turbines 10 to realize. Such very large flow cross sections and flow volumes are particularly advantageous in operating ranges of high speeds and / or outputs with high exhaust gas mass flows in order to minimize and dampen pressure peaks and pressure pulsations and to avoid high exhaust back pressures and resulting high fuel consumption of the internal combustion engine.

For the representation of very large flow cross sections and flow volumes of the turbine 10 can at the turbine 10 according to 8th the adjustment room 38 be connected as an additional volume. As a result, pressure pulsations can be smoothed or damped, which leads to particularly low exhaust gas back pressures.

Is the axial slide 32 in its release position, so is an inflow section A3, which in the circumferential direction of the turbine wheel 16 is completely circumferential, between the axial slide 32 and the wall 48 maximally released. About the inflow section A3 can exhaust gas from both floods 22 . 24 in the adjustment room 38 inflow and so the adjustment room 38 use as additional flow volume or flow cross section. Will the axial slide 32 shifted at least substantially continuously starting from its release position into its blocking position, it is accompanied by an at least substantially continuous reduction or narrowing of the Einströmquerschnitts A3. Will the axial slide 32 at least substantially continuously moves in the direction of its release position, it is accompanied by the at least substantially continuous increase or release of the inflow A3. In the locked position of the axial slide 32 is preferably also the inflow section A3 fluidly blocked, so that the exhaust gas from the floods 22 . 24 not in the adjustment room 38 can flow in.

The relatively large volume of the adjustment chamber 38 can with correspondingly large inflow cross section A3, which depends on the movement of the axial slide 32 is to act as a pulsation damper and help reduce the pressure upstream of the turbine wheel 16 or the turbine 10 to keep low. As a result, the problems resulting from relatively small flow volumes and flow cross sections of conventional turbines with two or more passages can be avoided.

The turbine 10 also has the advantage that both the effective flow cross section and the Gesamtüberströmquerschnitt and the Einströmquerschnitt A3 only by means of an axial slide 32 can be set variably. This keeps the number of parts, the weight, the cost and the space requirement of the turbine 10 especially low.

Claims (7)

Turbine ( 10 ) for an exhaust gas turbocharger, with a turbine housing ( 12 ), which has a receiving space ( 14 ) for a turbine wheel ( 16 ) of the turbine ( 10 ) and at least two floods ( 22 . 24 ), via which the turbine wheel ( 16 ) Can be supplied, and with at least one adjustable between a disconnected position and at least one connection position adjusting device ( 32 ), by means of which at least one of the floods ( 22 . 24 ) in the separating position fluidically separated from each other and in the connecting position fluidly interconnecting, first flow cross-section (A1, A2) is adjustable, characterized in that by means of the adjusting device ( 32 ) also flows through the exhaust gas and from the fluidic connection and separation of the floods ( 22 . 24 ) independent, further flow cross-section of the turbine ( 10 ) is variably adjustable. Turbine ( 10 ) according to claim 1, characterized in that upstream of the turbine wheel ( 16 ) at least one guiding element ( 28 ) is provided, by means of which to the receiving space ( 14 ) flowing exhaust gas is derivable. Turbine ( 10 ) according to claim 2, characterized in that the adjusting device ( 32 ) at least one actuating element ( 32 ), by means of which, for adjusting the further flow cross-section, the guide element ( 28 ) in the flow direction of the exhaust gas on only one side of the guide element ( 28 ) is at least partially coverable. Turbine ( 10 ) according to one of the preceding claims, characterized in that the adjusting device ( 32 ) between a fluidically maximally narrowing the further flow cross-section blocking position ( 54 ) and at least one of the further flow cross-section on the other hand releasing release position ( 56 ) is adjustable, wherein the adjusting device ( 32 ) is adjusted to its release position when the actuator ( 32 ) in its locked position ( 54 ) is adjusted. Turbine ( 10 ) according to one of the preceding claims, characterized in that the fluidic connection of the floods ( 22 . 24 ) is accompanied by a release of the further flow cross-section. Turbine ( 10 ) according to one of the preceding claims, characterized in that the turbine ( 10 ), in particular the turbine housing ( 12 ), at least one upstream of the turbine wheel ( 16 ) arranged additional space ( 38 ), in which exhaust gas from the floods ( 22 . 24 ) and which for introducing exhaust gas into the additional space ( 38 ) by means of the adjusting device ( 32 ) and for preventing the introduction of exhaust gas into the additional space ( 38 ) by means of the adjusting device ( 32 ) is fluidically shut off. Turbine ( 10 ) according to claim 6, characterized in that the adjusting device ( 32 ) at least partially in the additional room ( 38 ) is recorded.

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