DE102022003030A1 - Turbine for an exhaust gas turbocharger for an internal combustion engine and internal combustion engine for a motor vehicle - Google Patents

Abstract

The invention relates to a turbine (10) for an exhaust gas turbocharger, with a turbine housing (12), which has flows (14, 16) through which exhaust gas can flow, with a turbine wheel, with a bypass channel (24), via which the turbine wheel is exposed to at least one blow-off mass flow forming part of the exhaust gas is to be bypassed, with at least one flow opening (32), via which the flows (14, 16) can be fluidly connected to one another, and with at least one valve element (26), which is located between the bypass channel (24) and the flow opening (32) which simultaneously closes the closed position and at least one open position which simultaneously at least partially releases the bypass channel (24) and the flow opening (32) can be moved relative to the turbine housing (12), wherein in the at least one open position a first surface area (38) of the valve element (26) and a second surface area (40) of the turbine housing (12) limit a first flow cross section (Q1) through which the blow-off mass flow can flow on its way from the respective flood (14, 16) to the bypass channel (24).

Description

The invention relates to a turbine for an exhaust gas turbocharger of an internal combustion engine according to the preamble of patent claim 1. The invention further relates to an internal combustion engine for a motor vehicle.

The DE 10 2013 002 894 B4 a turbine for an exhaust gas turbocharger can be seen as known, with a turbine housing which has at least two floods that are fluidly separated from one another at least in some areas and through which exhaust gas from an internal combustion engine can flow.

The object of the present invention is to create a turbine for an exhaust gas turbocharger of an internal combustion engine and an internal combustion engine with at least one such turbine, so that particularly efficient operation can be realized.

This object is achieved by a turbine with the features of patent claim 1 and by an internal combustion engine with the features of patent claim 10. Advantageous embodiments with useful developments of the invention are specified in the remaining claims.

A first aspect of the invention relates to a turbine for an exhaust gas turbocharger of an internal combustion engine. The turbine has a turbine housing which has at least two floods that are fluidly separated from one another at least in some areas and through which exhaust gas from the internal combustion engine can flow. The internal combustion engine, also referred to as an internal combustion engine or motor, has, for example, at least one or more combustion chambers. Combustion processes take place in the respective combustion chamber during fired operation of the internal combustion engine. During the respective combustion process, a fuel-air mixture, also known as a mixture, is burned, which results in the exhaust gas. The mixture includes air and a preferably liquid fuel. Furthermore, it is conceivable that the fuel is a gaseous fuel. The exhaust gas can flow out of the respective combustion chamber and flow through the turbine. In particular, the exhaust gas can flow through the floods, also known as exhaust gas floods. For example, the floods are separated by means of a partition wall arranged in particular between the floods, in particular at least in some areas and most particularly at least predominantly and thus at least more than half or completely.

The turbine has a turbine wheel arranged in the turbine wheel, in particular rotatably, which is accommodated in particular in a receiving area of the turbine housing. The turbine wheel can be driven by the exhaust gas flowing through the turbine housing and can therefore be rotated in particular about an axis of rotation relative to the turbine housing. In particular, the exhaust gas can be guided by means of the floods to the turbine wheel, in particular to and into the receiving area, so that, for example, the exhaust gas flowing through the floods can flow out of the floods and flow towards the turbine wheel and thereby drive the turbine wheel.

The turbine has at least one bypass channel, which is also referred to as a bypass or bypass channel. In particular, it is conceivable that the bypass channel extends at least partially, in particular at least predominantly and thus at least more than half or completely, in the turbine housing, in particular directly, is delimited by the turbine housing. Via the bypass channel, the turbine wheel can be bypassed by at least part of the exhaust gas flowing through the turbine housing. In other words, at least the said part of the exhaust gas can bypass the turbine wheel via the bypass channel. This means that the exhaust gas flowing through the bypass channel and thereby bypassing the turbine wheel does not drive the turbine wheel. This bypassing of the turbine wheel by the exhaust gas is also referred to as bypassing, blow-off or blow-off, so that the part of the exhaust gas flowing through the bypass channel and thus bypassing the turbine wheel forms or is a so-called blow-off mass flow. In other words, the exhaust gas flowing through the bypass channel and thus bypassing the turbine wheel is also referred to as blow-off mass flow or blow-off exhaust gas.

The turbine also has at least one flow opening through which the flows can be fluidly connected to one another. In particular, the flow opening is formed, for example, in the partition, in particular in such a way that the flow opening is completely circumferentially delimited along its circumferential direction by the partition, in particular directly. In particular, the partition is part of the turbine housing. The aforementioned feature that the flows can be completely separated from one another, in particular by means of the partition, is to be understood in particular as meaning that the flows can be completely separated from one another when the flow opening is closed, that is to say fluidically blocked. In particular, the flow opening is arranged at a connection point at which the floods flow fluidly via the flow opening are connectable to each other. Furthermore, it is preferably provided that the connection point is the only point in the turbine housing at which the flows can be fluidly connected to one another.

The turbine also has a valve element, which is preferably arranged in the turbine housing. The valve element is movable, in particular pivotable, between a closed position and at least one open position relative to the turbine housing. In the closed position, the bypass channel and the flow opening are simultaneously closed by means of the valve element, so that the floods are fluidly separated from one another at the connection point and so that no exhaust gas from the floods can flow into the bypass channel, and so that no exhaust gas from the floods can bypass the turbine wheel. In particular, it is provided that in the closed position of the valve element, the flow opening is blocked, in particular completely, by means of the valve element.

For example, the bypass channel has an inflow opening, which is delimited, for example, completely circumferentially along its circumferential direction by the turbine housing, in particular directly. It is conceivable that in the closed position the valve element closes the inflow opening, in particular completely. Thus, for example, in the closed position, the flow opening and the inflow opening are fluidically blocked at the same time by means of the valve element, and are therefore closed. In the at least one open position, the valve element simultaneously exposes the bypass channel and the flow opening in certain areas, in particular in such a way that in the at least one open position, the valve element at least partially exposes the flow opening and the inflow opening at the same time. Thus, in the open position, the bypass channel is released, and at the same time the flows are fluidly connected to one another at the connection point, since the flow opening is at least partially released. Thus, the aforementioned blow-off flow can flow from the floods into the bypass channel, for example by the blow-off mass flow flowing through the inflow opening, and as a result the blow-off mass flow can flow through the bypass channel and thus bypass the turbine wheel. In particular, it is conceivable that when the valve element is adjusted or moved, in particular relative to the turbine housing, from the closed position into the at least one open position, the valve element simultaneously exposes both the bypass channel, in particular the inflow opening, and the throughflow opening, so that, for example, there is no position of the valve element exists in which the valve element opens the bypass channel and blocks the flow opening, and preferably there is no position of the valve element in which the valve element blocks the bypass channel and opens the flow opening. This means that both a particularly advantageous flood connection and a particularly advantageous blow-off can be represented at the same time.

In order to be able to realize a particularly efficient operation of the turbine and thus of the internal combustion engine, it is provided according to the invention that in the at least one open position a first surface area of the valve element and a second surface area of the turbine housing limit a first flow cross section, in particular directly, which of the blow-off mass flow can flow through on its way from the respective flood to the bypass channel, in particular to the inflow opening. Furthermore, it is provided according to the invention that in the at least one open position, a third surface region of the valve element, spaced from the first surface region, and a fourth surface region of the turbine housing, spaced from the second surface region, delimit, in particular directly, a second flow cross section, which depends on the blow-off mass flow the path of which can be flowed through from the respective flood to the bypass channel, in particular the inflow opening. In the flow direction of the blow-off mass flow flowing in the at least one open position from the respective flood towards the bypass channel, in particular the inflow opening, the second flow cross section is arranged downstream of the first flow cross section, so that in the at least one open position the blow-off mass flow is on its way from the respective flood to the Bypass channel, in particular the inflow opening, first flows through the first flow cross section and then through the second flow cross section, which is spaced from the first flow cross section. The flow cross sections are therefore connected in series.

Furthermore, it is provided according to the invention that the first flow cross section and the second flow cross section are each smaller than all of the blow-off mass flow flowing in the at least one open position from the first flow cross section towards the second flow cross section between the first flow cross section and the second flow cross section, i.e. downstream of the first flow cross section and upstream of the second flow cross section, flow cross sections arranged and through which the blow-off mass flow can flow on its way from the first flow cross section to the second flow cross section. Therefore are or form the first Flow cross section and the second flow cross section respective constrictions through which the blow-off mass flow flows on its way from the respective flood to the bypass channel, in particular the inflow opening. The blow-off mass flow flows on its way from the respective flood to the bypass channel, in particular the inflow opening, through the constrictions and through the aforementioned flow cross-sections arranged between the narrow points, with all flow cross-sections arranged between the narrow points being from the blow-off mass flow on its way from the respective Flood flows through to the bypass canal, larger than the bottlenecks. The bottlenecks are or thus form two throttles connected in series, which bring about a particularly effective gap reduction and thus, in comparison to conventional solutions, enable functional areas that were previously available in conventional solutions in interaction with a surface of the flow opening, also known as a flute connection surface, the flute connection surface of which, for example, from the Exhaust gas on the way from one of the floods via the flow opening into the other of the floods could flow through, were inaccessible. In other words, since in the at least one open position the valve element releases the flow opening, in the at least one open position it is possible for at least part of the exhaust gas from or from one of the flows to flow through the at least partially released flow opening and thus flow into the other of the flows or vice versa. In the at least one open position, the floods are fluidly connected to one another via the flow opening, which is also referred to as a flood connection. In the closed position, the flow opening is fluidically blocked, so that the floods are fluidly separated from one another at least at the connection point, which is also referred to as flood separation. The invention is based in particular on the following findings and considerations: The bypass channel and the valve element are, for example, components of a blow-off device, since the previously described blow-off can be effected by means of the bypass channel and by means of the valve element. In particular, the valve element can be used to adjust the amount of exhaust gas flowing through the bypass channel and thus bypassing the turbine wheel. The design of such blow-off devices and in particular of twin-flow turbines usually involves a conflict of objectives between the flow connection, i.e. the fluidic connection of the flow via the flow opening, and the blowing off of the exhaust gas. The valve element is used as an actuator in order to switch, if necessary, between the flood separation and the flood connection and, if necessary, to release and block the bypass channel. The valve element is usually adapted to the respective requirements in terms of its geometry, i.e. geometrically, and in particular optimized, in particular with the aim of achieving high efficiency of the turbine. The valve element is or comprises a flow body that is moved to switch between the flood connection and the flood separation and to selectively open or close the bypass channel. This usually creates two functional surfaces. In particular, these always form the areas that are narrowest in terms of flow to form an environment. One of the surfaces is a flow connection surface, via which the flows are fluidly connected to one another, in particular in the at least one open position, and the other of the surfaces is a blow-off surface, via which, for example, the blow-off mass flow can flow through the inflow opening or flow into the bypass channel. It is desirable, in particular, to minimize the blow-off area, i.e. to keep it as small as possible, but at the same time to maintain minimal gaps for functional reasons in order to enable mechanical mobility of the valve element, in particular relative to the turbine housing. In order to address the conflict of objectives described above, the end points are provided in the invention. The blow-off mass flow must therefore, on its way from the respective flood to the bypass channel, in particular the inflow opening, first pass through the first flow cross section, which is, for example, a first gap or is formed by a first gap, and then through the second flow cross section, which is, for example, a second gap or is formed by a second gap. In this way, for example, the blow-off area can be advantageously kept small in the at least one open position and thus when the blow-off device or valve element is open, whereby the flood connection can be improved in comparison to conventional solutions. This means that particularly high turbine efficiencies can be achieved. Particularly in connection with double-flow, especially multi-flow, turbines, a conflict of objectives between boost pressure build-up in the range of low engine speeds and at the same time high boost pressure and efficiency at nominal speed can be resolved or improved. As a result, particularly low fuel consumption and therefore CO ₂ emissions operation of the internal combustion engine can be guaranteed.

In order to enable particularly efficient operation, it is provided in one embodiment of the invention that the first flow cross section and the second flow cross section are each smaller than all in the flow direction of the flow from the respective flood to the first flow Flow cross-section of the blow-off mass flow flowing upstream of the first flow cross-section and downstream of the respective flood, flow cross-sections which can be flowed through by the blow-off mass flow on its way from the respective flood to the first flow cross section.

A further embodiment is characterized in that the first flow cross section and the second flow cross section are each smaller, all in the flow direction of the blow-off mass flow flowing from the respective flood to the bypass channel, in particular the inflow opening, downstream of the second flow cross section and upstream of the bypass channel, in particular the inflow opening, arranged and through which the blow-off mass flow can flow on its way from the respective flood to the bypass channel, in particular the inflow opening. This allows the turbine to achieve a particularly high level of efficiency. A further embodiment is characterized in that the valve element has a first sealing surface, which rests against a corresponding, second sealing surface of the turbine housing, in particular directly, in order to block the bypass channel, in particular the inflow opening, and in the at least one open position at least partially from the second Sealing surface is spaced apart. As a result, the bypass channel can be blocked effectively and efficiently, so that particularly efficient operation can be achieved.

It has proven to be particularly advantageous if the third surface area is formed by the first sealing surface and the fourth surface area is formed by the second sealing surface. As a result, the second flow cross section can be designed particularly advantageously, so that particularly efficient operation can be achieved.

In a further, particularly advantageous embodiment of the invention, it is provided that the second surface area is formed by a bulge of the turbine housing, also known as a projection, the bulge of which faces a partial area of the turbine housing that adjoins the bypass channel, in particular the inflow opening, towards the bulge Turbine housing and in the at least one open position is raised towards the valve element. As a result, the first flow cross section can be advantageously made small, and in a particularly simple manner, whereby particularly efficient operation can be achieved.

In order to realize a particularly effective and efficient operation, it has proven to be particularly advantageous if the bulge is convex.

In order to be able to create particularly flow-favorable conditions and thus particularly efficient operation, it is provided in a further embodiment of the invention that the bulge has a radius or is formed by a radius.

Finally, it has proven to be particularly advantageous if the first surface area of the valve element is curved, in particular convex. As a result, particularly good flow conditions can be achieved, so that particularly efficient operation can be achieved.

A second aspect of the invention relates to an internal combustion engine for a motor vehicle, preferably designed as a reciprocating piston engine, wherein the internal combustion engine can be designed, for example, as a gasoline engine or as a diesel engine. The internal combustion engine according to the second aspect of the invention has at least one turbine according to the first aspect of the invention. Advantages and advantageous refinements of the first aspect of the invention are to be viewed as advantages and advantageous refinements of the second aspect of the invention and vice versa.

Further advantages, features and details of the invention result from the following description of a preferred exemplary embodiment and from the drawing. The features and combinations of features mentioned above in the description as well as the features and combinations of features mentioned below in the description of the figures and/or shown in the figures alone can be used not only in the combination specified in each case, but also in other combinations or on their own, without the scope of to abandon invention.

• 1 ausschnittsweise eine schematische Schnittansicht einer Turbine für einen Abgasturbolader einer Verbrennungskraftmaschine;
• 2 ausschnittsweise eine weitere schematische Längsschnittansicht der Turbine, wobei sich ein Ventilelement in seiner Schließstellung befindet;
• 3 ausschnittsweise eine schematische Perspektivansicht der Turbine gemäß 2;
• 4 ausschnittsweise eine schematische Schnittansicht der Turbine, wobei sich das Ventilelement in einer ersten Offenstellung befindet;
• 5 ausschnittsweise eine schematische Schnittansicht der Turbine, wobei sich das Ventilelement in einer zweiten Offenstellung befindet; und
• 6 ausschnittsweise eine schematische Perspektivansicht der Turbine gemäß 5.

The drawing shows in:

• 1 a detail of a schematic sectional view of a turbine for an exhaust gas turbocharger of an internal combustion engine;
• 2 a detail of a further schematic longitudinal sectional view of the turbine, with a valve element in its closed position;
• 3 a section of a schematic perspective view of the turbine according to 2 ;
• 4 a detail of a schematic sectional view of the turbine, with the valve element being in a first open position;
• 5 a detail of a schematic sectional view of the turbine, with the valve element being in a second open position; and
• 6 a section of a schematic perspective view of the turbine according to 5 .

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

1 shows a detail in a schematic sectional view of a turbine 10 for an exhaust gas turbocharger of an internal combustion engine not shown in the figures. The internal combustion engine is designed, for example, as a reciprocating piston engine and has a plurality of combustion chambers, the respective combustion chamber being at least partially delimited, for example, by a respective cylinder. During a fired operation of the internal combustion engine, the fired operation of which is also referred to as fired operation, combustion processes take place in the respective combustion chamber, from which exhaust gas from the internal combustion engine results. In particular, a motor vehicle, also simply referred to as a vehicle, can be equipped with the internal combustion engine and can be driven by means of the internal combustion engine. The motor vehicle is preferably a motor vehicle.

The turbine 10 has an in 1 Partially visible turbine housing 12 with an in 1 unrecognizable recording space. A turbine wheel of the turbine 10, which cannot be seen in the figures, is accommodated in the receiving space. The turbine wheel is rotatable about an axis of rotation relative to the turbine housing 12. The turbine housing 12 also has at least or exactly two flows 14 and 16 that are fluidly separated from one another at least in some areas. As illustrated by directional arrows 18 and 20, the exhaust gas from the internal combustion engine can flow through the floods 14 and 16. In 1 an intermediate wall 22 of the turbine housing 12, also referred to as a partition or partition or intermediate wall, can be seen. By means of the intermediate wall 22, the floods 14 and 16 are fluidically separated from one another.

A first part or a first group of combustion chambers is, for example, fluidly connected to the flood 14, so that the exhaust gas from the first group of combustion chambers is brought together to and into the flood 14. A second part or a second group of combustion chambers, which is different from the first part and is provided in addition to the first part, is fluidly connected to the flood 16, so that the exhaust gas from the second group is brought together to or into the flood 16. In other words, the exhaust gas from the combustion chambers belonging to the first group is supplied to the flood 14, with or while the exhaust gas from the combustion chambers belonging to the second group is supplied to the flood 16. Expressed again in other words, the combustion chambers belonging to the first group convey their exhaust gas to and into the flood 14, with the combustion chambers belonging to the second group conveying their exhaust gas to and into the flood 16.

If the floods 14 and 16 are fluidly separated from one another, this is also referred to as flood separation. This flow separation creates an overall reduction in exhaust gas-carrying volumes between the combustion chambers and the turbine wheel compared to the combustion chambers, which can lead to the effect of so-called shock charging. In other words, the exhaust gas turbocharger and thus the internal combustion engine can be operated by the flow separation in a surge charging operation, in which the internal combustion engine is charged by means of the surge charging, that is, supplied with compressed air.

The turbine 10 includes a bypass channel 24, which can extend at least partially into the turbine housing 12. The turbine wheel can be bypassed by at least part of the exhaust gas via the bypass channel 24. In other words, by means of the bypass channel 24, at least part of the exhaust gas can be diverted from the combustion chambers in the flow direction of the exhaust gas upstream of the turbine wheel and in particular can be introduced into the bypass channel 24, so that the branched off exhaust gas flowing through the bypass channel 24 bypasses the turbine wheel and therefore does not drive it. The exhaust gas flowing through the bypass channel 24 and thus bypassing the turbine wheel, and therefore the part of the exhaust gas flowing through the bypass channel 24 and thus bypassing the turbine wheel, is or forms a blow-off mass flow.

The turbine 10 also has a valve element 26, which is located between an in 1 closed position shown by solid line and at least one in 1 Open position shown by dashed lines is movable, in particular pivotable, relative to the turbine housing 12. The closed position is also in the 2 and 3 shown. 4 shows the at least one open position, which is also referred to as the first open position. 5 and 6 show a second open position of the valve element 26. In particular, it is conceivable that the closed position and the second open position are respective end positions of the valve element 26, so that the valve element 26 moves relative to the turbine housing 12 between the end positions and from end position to end position, however cannot be moved beyond the respective end position. On its way from one of the end positions to the other end position, the valve element 26 comes into the first open position, i.e. into the at least one open position. When we talk about the open position below, this is to be understood as meaning the at least one open position, i.e. the first open position, unless otherwise stated.

In order to be able to move and thus adjust the valve element 26 relative to the turbine housing 12, the valve element 26 in the exemplary embodiment shown in the figures is coupled to a pivot arm 28, which can be pivoted about a pivot axis 30 relative to the turbine housing 12. The valve element 26 can thus be pivoted between the closed position and the second open position and thus between the closed position and the first open position about the pivot axis 30 relative to the turbine housing 12.

In the closed position, the bypass channel 24 is fluidically blocked, that is, closed, by means of the valve element 26, so that no exhaust gas can flow from the floods 14 and 16 into the bypass channel 24 and flow through it. In the at least one open position and also in the second open position, the valve element 26 releases the bypass channel 24, so that the bypass channel 24 is released. By moving the valve element 26 from the closed position to the open position and thereby releasing the bypass channel 24, a boost pressure of the exhaust gas turbocharger can be set, in particular controlled or regulated. In particular, the boost pressure can be adjusted by adjusting, i.e. varying, the amount of exhaust gas flowing through the bypass channel 24 by moving the valve element 26 relative to the turbine housing 12.

The turbine 10 also has a flow opening 32 arranged upstream of the turbine wheel, which in the present case is formed in the intermediate wall 22. The flows 14 and 16 can be fluidly connected to one another via the flow opening 32, in particular at a connection point at which the flow opening 32 is arranged. How out 1 can be seen, a first branch channel 34 branches off from the flood 14, with a second branch channel 36 branching off from the flood 16. The branch channel 34 fluidically connected to the flood 14 can be fluidly connected to the branch channel 36 fluidly connected to the flood 16 via the flow opening 32.

How out 1 can be seen, the flow opening 32 is also fluidically blocked, that is closed, by means of the valve element 26 in the closed position of the valve element 26. If the valve element 26 is now moved from its closed position to the at least one open position, the flows 14 and 16 are fluidly connected to one another in that the valve element 26 at least partially opens the flow opening 32, and at the same time the valve element 26 provides the bypass channel 24, in particular an inflow opening of the bypass channel 24, at least partially free. The blow-off mass flow can flow from the floods 14 and 16 into the bypass channel 24 via the inflow opening, with the valve element 26, for example, fluidically blocking the inflow opening by means of the valve element 26 in the closed position. By at least partially opening the flow opening 32, the floods 14 and 16 are fluidly connected to one another, which is also referred to as a flood connection. By releasing the flow opening 32, that is to say by fluidly connecting the flows 14 and 16 to one another, it is possible, for example, to switch from shock charging to or into accumulation charging.

When the valve element 26 is adjusted from the closed position to the at least one open position, the valve element 26 simultaneously releases both the bypass channel 24 and the flow opening 32, so that, for example, there is no position of the valve element in which the valve element blocks the bypass channel 24 and the flow opening 32 releases, and preferably there is no position of the valve element 26 in which the valve element 26 releases the bypass channel and blocks the flow opening 32. If the valve element 26 is thus moved out of the closed position, in particular towards the at least one open position, both the flow opening 32 and the bypass channel 24 are opened immediately and simultaneously.

In order to be able to realize particularly efficient operation of the turbine 10, the turbine 10 is designed to be particularly good 4 is recognizable, in at least one, in 4 shown open position of the valve element 26, a first surface area 38 of the valve element 26 and a second surface area 40 of the turbine housing 12, in the at least one open position, the blow-off mass flow can flow through on its way from the respective flood 14, 16 to the bypass channel 24, in particular to the inflow opening , limit the first flow cross section Q1. In addition, it is provided that in the at least one open position a third surface region 42 of the valve element 26 spaced from the first surface region 38 and a fourth surface region 44 of the turbine housing 12 spaced from the second surface region 40 have one in the at least limit an open position of the blow-off mass flow on its path from the respective flood 14, 16 to the bypass channel 24, in particular to the inflow opening, through which flow can flow and the second flow cross-section Q2 which is arranged downstream of the first flow cross-section Q1. Furthermore, it is provided that the first flow cross section Q1 and the second flow cross section Q2 are each smaller than all of the blow-off mass flows flowing from the first flow cross section Q1 to the second flow cross section Q2 between the first flow cross section Q1 and the second flow cross section Q2 arranged in the flow direction and from which Blow-off mass flow on its path from the flow cross-section Q1 to the flow cross-section Q2 flow cross-sections through which flow can flow. As a result, the flow cross sections Q1 and Q2 are or form two throttles connected in series, which enable particularly efficient operation.

To move the valve element 26 from the closed position into the at least one, in 4 To move the open position shown, the valve element 26 is pivoted, for example, by a maximum of 10 degrees, in particular by, in particular, precisely, 5 degrees, from the closed position in the direction of the second open position, so that it is preferably provided that the previous and following statements apply to the Flow cross sections Q1 and Q2 apply to the at least one open position and to all other open positions that lie between the closed position and the at least one open position.

In the exemplary embodiment shown in the figures, the valve element 26 is particularly good 5 can be seen, a first sealing surface 46, which rests on a corresponding, second sealing surface 48 of the turbine housing 12, in particular directly, for blocking the bypass channel 24 and in the at least one open position and preferably also in all others, between the closed position and the at least one Open position lying open position of the valve element 26, is at least partially spaced from the second sealing surface 48. For example, the third surface area 42 is formed by the sealing surface 46, and for example, the fourth surface area 44 is formed by the sealing surface 48.

Particularly good looking 5 It can also be seen that the second surface area 40 is formed by a bulge 50 of the turbine housing 12, the bulge 50 of which faces a partial area 52 of the turbine housing 12 that adjoins the bulge 50 towards the bypass channel 24 and in the at least one open position to the valve element 26 is raised and therefore stands out. The bulge 50 is convex. In particular, the bulge 50 has an in 2 Radius marked R. It is therefore preferably provided that the first surface region 38 is curved, in particular convex.

Reference symbol list

10

turbine

12

Turbine housing

14

flood

16

flood

18

Arrow

20

Arrow

22

intermediate wall

24

Bypass canal

26

Valve element

28

Swing arm

30

Pivot axis

32

Flow opening

34

branch channel

36

branch channel

38

first surface area

40

second surface area

42

third surface area

44

fourth surface area

46

first sealing surface

48

second sealing surface

50

bulge

52

Sub-area

Q1

first flow cross section

Q2

second flow cross section

R

radius

QUOTES INCLUDED IN THE DESCRIPTION

This list of documents listed by the applicant was 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 102013002894 B4 [0002]

Claims (10)

Turbine (10) for an exhaust gas turbocharger, with a turbine housing (12), which has at least two flows (14, 16) that are fluidly separated from one another at least in some areas and through which exhaust gas from an internal combustion engine can flow, with a turbine wheel that can be driven by the exhaust gas and which is in the turbine housing ( 12) is included, with at least one bypass channel (24), via which the turbine wheel can be bypassed by at least a part of the exhaust gas forming a blow-off mass flow, with at least one flow opening (32), via which the flows (14, 16) can be fluidly connected to one another are, and with at least one valve element (26), which is between a closed position that simultaneously closes the bypass channel (24) and the flow opening (32) and at least one open position that simultaneously releases the bypass channel (24) and the flow opening (32) relative to at least some areas the turbine housing (12) is movable, characterized in that : - in the at least one open position, a first surface area (38) of the valve element (26) and a second surface area (40) of the turbine housing (12) one of the blow-off mass flow on its way from limit the first flow cross section (Q1) through which the respective flood (14, 16) can flow through to the bypass channel (24); - In the at least one open position, a third surface region (42) of the valve element (26) spaced from the first surface region (38) and a fourth surface region (44) of the turbine housing (12) spaced from the second surface region (40) one of which limit the blow-off mass flow on its path from the respective flood (14, 16) to the bypass channel (24) through which the second flow cross-section (Q2) can flow and which is arranged downstream of the first flow cross-section (Q1); and - the first flow cross section (Q1) and the second flow cross section (Q2) are each smaller than all of the blow-off mass flow flowing from the first flow cross section (Q1) to the second flow cross section (Q2) between the first flow cross section (Q1) and the second flow cross section (Q2) arranged flow cross sections through which the blow-off mass flow can flow. Turbine (10) after Claim 1 , characterized in that the first flow cross section (Q1) and the second flow cross section (Q2) are each smaller than all of the blow-off mass flows flowing from the respective flood (14, 16) to the first flow cross section (Q1) upstream of the first flow cross section (Q1 ) and flow cross sections arranged downstream of the respective flood (14, 16) through which the blow-off mass flow can flow. Turbine (10) after Claim 1 or 2 , characterized in that the first flow cross section (Q1) and the second flow cross section (Q2) are each smaller than all of the blow-off mass flows flowing from the respective flood (14, 16) to the bypass channel (24) downstream of the second flow cross section (Q2) and flow cross sections arranged upstream of the bypass channel (24) through which the blow-off mass flow can flow. Turbine (10) according to one of the preceding claims, characterized in that the valve element (26) has a first sealing surface (46) which rests on a corresponding, second sealing surface (46) of the turbine housing (12) to block the bypass channel (24). and in the at least one open position is at least partially spaced from the second sealing surface (46), Turbine (10) after Claim 4 , characterized in that the third surface area (42) is formed by the first sealing surface (46) and the fourth surface area (44) is formed by the second sealing surface (48). Turbine (10) according to one of the preceding claims, characterized in that the second surface area (40) is formed by a bulge (50) of the turbine housing (12), the bulge (50) of which faces towards the bypass channel (24). the bulge (50) adjoining portion (52) of the turbine housing (12) and in the at least one open position is raised towards the valve element (26). Turbine (10) after Claim 6 , characterized in that the bulge (50) is convex. Turbine (10) after Claim 6 or 7 , characterized in that the bulge (50) has a radius (R). Turbine (10) according to one of the preceding claims, characterized in that the first surface region (38) is curved, in particular convex. Internal combustion engine for a motor vehicle, with at least one turbine (10) according to one of the preceding claims.

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