Turbine and internal combustion engine for exhaust turbochargers, especially for motor vehicles

Abstract

The invention relates to a turbine (10) for a turbocharger of an exhaust gas turbocharger, comprising a turbine housing (12) having at least two at least partially fluidically separated and at least partially flowable by exhaust gas of an internal combustion engine; a turbine wheel (24) accommodated in the turbine housing (12) and drivable by the exhaust gas; at least one bypass channel (32) through which the turbine wheel (24) can be bypassed by at least a portion of the exhaust gas; at least one flow opening (34) fluidically connecting the flow channels (14, 16) to one another; and at least one valve element (36) movable between a closed position in which the bypass channel (32) and the flow opening (34) are closed and at least one open position in which at least one of the bypass channel (32) and the flow opening (34) is at least partially open, wherein the valve element (36) has at least one flow channel (44) passing through the valve element (36) and flowable by the exhaust gas.

Description

Technical Field

[0001] This invention relates to a turbine for an exhaust gas turbocharger, particularly for motor vehicles, according to the preamble of claim 1. The invention also relates to an internal combustion engine for motor vehicles. Background Technology

[0002] Turbines of the same type for exhaust gas turbochargers, particularly for motor vehicles, have been disclosed, for example, by DE102013002894B4. The turbine has a turbine housing having at least two flow channels that are at least partially fluid-isolated from each other and through which exhaust gas from an internal combustion engine can pass. Additionally, DE102016208163A1 discloses a turbine for an exhaust gas turbocharger. Furthermore, DE 11 2015 005 540B4 discloses an exhaust gas turbocharger. DE 10 2016 208 160A1 also discloses a turbine for an exhaust gas turbocharger. DE 10 2006 058 102 A1 discloses an internal combustion engine with an exhaust gas turbocharger. DE 10 2011 115 206 A1 discloses an exhaust gas turbocharger for an internal combustion engine. Additionally, EP 3 401 528 A1 discloses a turbocharger system. Summary of the Invention

[0003] The object of the present invention is to provide a turbine for an exhaust gas turbocharger and an internal combustion engine having at least one such turbine, thereby enabling particularly advantageous inrush passage connectivity.

[0004] This task is accomplished by a turbine having the features of claim 1 and an internal combustion engine having the features of claim 5. Advantageous designs with suitable inventive improvements are given in the remaining claims.

[0005] The first aspect of the invention relates to a turbine for an exhaust gas turbocharger, particularly for motor vehicles. This means that motor vehicles, preferably designed as automobiles, especially passenger cars, or simply vehicles, have an exhaust gas turbocharger including a turbine in their manufactured state. In particular, the motor vehicle, in its manufactured state, has an internal combustion engine, for example designed as a piston engine, also called an engine or internal combustion engine, thereby driving the motor vehicle. During the ignition and operation of the internal combustion engine, a combustion process takes place in the internal combustion engine. In the corresponding combustion process, a fuel-air mixture, also referred to as a mixture, is burned, thereby producing exhaust gas from the internal combustion engine. As will be explained in detail below, the turbine can be driven by means of the exhaust gas. The mixture here has at least air and, in particular, a fuel in a fluid state. In particular, the fuel is gasoline, and therefore gasoline engine fuel. Thus, the internal combustion engine is preferably designed as a gasoline engine. The turbine has a turbine housing having at least two or exactly two at least partially fluid-isolated flute passages, which are fluidly isolated from each other by partition walls of the turbine housing. The corresponding flute passages can be traversed by exhaust gas flow. The turbine also has a turbine impeller, which is rotatably housed within the turbine casing. The turbine impeller is driven by exhaust gas and therefore can rotate relative to the turbine casing, for example, about an axis of rotation. In particular, the corresponding flow channel can be designed as a helical passage, which extends at least substantially helically along its circumference of the turbine impeller. In particular, the turbine impeller is housed in a receiving space within the turbine casing, also known as a receiving area. Here, for example, the corresponding flow channel opens into the receiving area, such that exhaust gas flowing through the corresponding flow channel can be guided from the corresponding flow channel into the receiving area and then towards the turbine impeller. Therefore, exhaust gas flowing through the corresponding flow channel can exit from the corresponding flow channel and flow into the receiving area, subsequently flowing towards the turbine impeller and thereby driving the turbine impeller.

[0006] The turbine casing has at least one or exactly one bypass passage / bypass channel formed in the partition wall, through which at least a portion of the exhaust gas bypasses the turbine impeller. In particular, the bypass passage extends at least partially within the turbine casing and / or is at least partially defined directly by the turbine casing. The characteristic of "at least a portion of the exhaust gas can bypass the turbine through the bypass passage" means that the exhaust gas flowing through the bypass passage bypasses the turbine impeller and therefore does not drive the turbine impeller. The bypass passage is also referred to as an exhaust valve, exhaust valve channel, bypass, or bypass passage.

[0007] The turbine, and especially the turbine housing, also has at least one or exactly one flow port through which the flow channels can communicate with each other. In particular, the flow port can be defined directly through the turbine housing. Specifically, the flow port is a separate or additional flow port, distinct from or separate from the bypass channel, through which the flow channels can communicate with each other fluidly. The bypass channel is typically used to regulate, and especially control, the boost pressure that can be provided by the exhaust gas turbocharger.

[0008] Furthermore, the turbine has at least one valve that can be adjusted, particularly relative to the turbine housing, between a closed position and at least one open position; that is, it is movable. In the closed position, the bypass passage and the flow port are always completely closed, i.e., fluid flow is blocked, by means of the valve, also called the valve body. It is therefore preferable that no exhaust gas flows through the bypass passage in the closed position, and preferably no exhaust gas flows through the flow port in the closed position, thereby, for example, prohibiting, i.e., closing, the fluid communication between the flow channels through the flow port. More particularly, it is specified that the flow channels are completely fluidly isolated from each other in the closed position. In the open position, the valve at least partially opens the bypass passage and the flow port, particularly simultaneously, so that in the open position, the exhaust gas flows into and through the bypass passage. Additionally, the exhaust gas can flow through the flow port in the open position and thus, for example, flow in from one of the flow channels via the flow port, and therefore overflow to the corresponding other flow channel.

[0009] If the flow channels are fluidly isolated from each other in such a way that the flow ports are closed by a valve in the closed position (i.e., fluid blockage), then so-called pulse boosting can be performed to boost the internal combustion engine, that is, to supply compressed air to the internal combustion engine. By opening the flow ports, that is, by connecting the flow channels to each other through the flow ports, so-called constant pressure boosting can be achieved to boost the internal combustion engine.

[0010] Preferably, the valve is designed as a single piece, i.e., a one-piece valve body. In other words, it is preferably specified that the valve is not composed of multiple separately constructed and interconnected components, but rather that the valve is preferably integral, therefore a single piece, and thus manufactured as a single or integral valve body, designed as a single block. More preferably, it is specified that when the valve moves from the closed position to the open position, both the bypass passage and the flow port are opened at least partially, respectively.

[0011] Now, in order to particularly advantageously fluidize the turbine's flow passage and thus achieve particularly advantageous flow passage connectivity, the present invention specifies that the valve has at least or exactly one flow passage that is particularly completely through the valve and therefore extends particularly within the valve and is through which exhaust gas can flow, which is therefore completely defined by the valve (valve body) for example, circumferentially surrounding it and particularly extending over its entire range in the flow direction of the exhaust gas flowing through the flow passage.

[0012] In the closed position, the flow port is completely closed by means of a valve.

[0013] In the closed position, fluid communication between the flow channels via the flow path is prohibited, so that these flow channels are not fluidly connected to each other via the flow path in the closed position. Therefore, strict flow channel isolation can be achieved in the closed position, so it is possible to switch between flow channel fluid communication and flow channel fluid isolation as needed.

[0014] In the open position, the valve opens a first partial region of the flow port, and in the open position, the valve also protrudes into a second partial region of the flow port immediately following the first partial region, such that the valve is arranged in the second partial region, wherein a flow channel is located in a portion of the second partial region, thus forming a fluid connection between the flow channels in addition to the opened first partial region, and exhaust gas can flow through the opened first partial region and the flow channel and thus through said portion of the second partial region.

[0015] The flow channel can be used, for example, to fluidly connect the flow channels in the open position, in addition to only partially opening the flow port. That is, especially when, for example, in the open position, the valve itself opens a first partial region of the flow port and also protrudes into a second partial region of the flow port, particularly immediately adjacent to the first partial region, and is therefore arranged in the second partial region, the flow channels are fluidly connected to each other. Thus, for example, the flow channel can be located in a part of the second partial region, or exhaust gas can flow through the opened first partial region and the flow channel and then through a part of the second partial region, such that, for example, a large volumetric flow and / or mass flow of exhaust gas can overflow from one flow channel to the corresponding other flow channel.

[0016] For example, the flow channel is formed by at least or exactly one orifice, making it particularly cost-effective to form the flow channel. For example, the turbine is at least or exactly a two-stage segmented turbine, thereby enabling particularly advantageous or efficient operation. Here, the invention is based on the flow channel connection already known from the prior art, which is particularly variable in that the flow port is particularly completely blocked by moving the valve to the closed position, and thus can be closed, wherein the flow port can be at least partially opened by moving the valve to the open position. It is particularly conceivable that the valve can be adjusted, i.e., moved to the closed position and at least one of the open positions, as well as at least one or more other open positions, wherein in the respective other open positions, the flow port is always at least partially open. In particular, in the respective open positions, the respective exhaust gas volume flow and / or mass flow can flow through the flow port, wherein the volume flow and / or mass flow are different from each other in these open positions. This allows for a flow channel connection, also known as a flow channel connection, which is particularly on-demand and therefore variable. The valve here should have a dual function. Firstly, the valve is used as a flow channel connecting valve to selectively close or open the flow port. Secondly, the valve is used as an exhaust valve or bypass valve to selectively open or close the bypass channel. The valve here, particularly in the corresponding open position, simultaneously defines a first effective area for turbine impeller bypass and a second effective area for flow channel connection. Exhaust gas can flow through the first effective area and into the bypass channel, and exhaust gas can flow through the second effective area and overflow from one flow channel to another. Turbine impeller bypass means that at least a portion of the exhaust gas bypasses the turbine impeller. In other words, for example, particularly in the open position, the first and second effective areas are each at least partially directly defined by the valve, particularly the outer peripheral surface of the valve, wherein exhaust gas flowing through the first effective area bypasses the turbine impeller, and wherein exhaust gas flowing through the second effective area overflows from one flow channel to the other. This allows for pulse boosting, for example, when there is a surge in load and high demands on the transient characteristics of the internal combustion engine. On the other hand, the turbine can also operate at higher efficiency at rated power. A characteristic of the valve element can be its area ratio, or a certain area ratio (i.e., the ratio of a first effective area to a second effective area, or vice versa). Here, the profile of the valve element, particularly its outer periphery, can define the area and thus the area ratio and the resulting exhaust gas mass flow ratio according to the corresponding opening position and, more particularly, the valve opening angle. The mass flow ratio refers to the ratio of a first exhaust gas mass flow to a second exhaust gas mass flow, wherein, for example, the first mass flow flows through a first area or around the turbine impeller, and the second mass flow flows through a flow port or overflows from one flow channel to another.

[0017] However, existing solutions fail to produce any desirable flow channel connectivity characteristics from an engine perspective in terms of geometry. Compared to conventional solutions, this invention now allows for improved and, in particular, on-demand adjustment or regulation of the mass flow ratio, especially in the corresponding open position. In particular, this invention expands the possibilities regarding the adjustment of the mass flow ratio, especially in the corresponding open position, where the effective flow area is changed rather than merely altering the gap area of ​​the geometry. For this purpose, the flow channel, also referred to as a flow passage, is formed in the valve. For example, even with a small valve opening angle, i.e., when the valve is opened only slightly, for example, in the manner described above as the first local region being opened while the valve itself remains, for example, in the second local region, and where, although the bypass channel and the flow port are opened simultaneously, but the flow port is only slightly opened, the flow channel now allows, for example, exhaust gas to flow not only through the opened first local region but also through the flow channel. Thus, significant or large-scale flow channel connectivity can be exhibited even with a small opening angle or when the valve is only slightly open. In other words, even with a small opening angle, or even at a small valve opening angle, a large volumetric flow and / or mass flow can be achieved, which can overflow from one flow channel to the corresponding flow channel. Therefore, due to the valve movement mechanism, a relatively small flow channel connected mass flow can be obtained even at a small opening angle, which is significantly improved at a larger opening angle. The corresponding flow channel connected mass flow refers to the corresponding mass flow of exhaust gas overflowing from one flow channel to the corresponding flow channel.

[0018] By designing the flow channels, the main exhaust gas flow, for example, through a first local region, can be used to enable an additional exhaust gas flow mass flow through the flow channels. Therefore, this invention allows for the attainment of desirable or required flow channel connectivity characteristics, wherein, for example, advantageous, especially advantageous, small valve size can be achieved or maintained simultaneously. This results in efficiency improvements without the need for additional forces in, for example, the motion mechanisms for valve body movement or adjustment. Motion mechanisms for shifting or moving the valve, particularly between open and closed positions, include, for example, electrically actuated components, also known as electrically adjustable components. The electrically actuated components are electric actuators, thereby enabling, for example, the valve to be moved from a closed position to an open position and / or from an open position to a closed position using electrical energy.

[0019] In order to guide the exhaust gas flow through the channel in a particularly timely and advantageous manner, the channel is specified to have at least one arched length section in at least or exactly one imaginary plane.

[0020] Alternatively or additionally, the flow channel is specified to have at least two length regions that extend at an angle or perpendicular to each other, particularly in at least or exactly one imaginary plane, thereby allowing exhaust gas to be particularly advantageously guided through the flow channel and through the valve.

[0021] Alternatively or additionally, the flow channel extends in an S-shape or Z-shape, at least in a local area and especially in at least or exactly one imaginary plane. This allows for a particularly advantageous arrangement of the corresponding parts of the exhaust gas inflow and outflow channels, thereby enabling particularly advantageous exhaust gas guidance.

[0022] Therefore, it is particularly advantageous that the flow channels are in fluid communication with each other in the open position of the valve. In other words, it is preferably specified that the flow channels are designed in such a way or for such purpose that, in the open position, the flow channels are in fluid communication with each other. In other words, exhaust gas can flow into one flow channel from one flow channel in the open position, then through that channel and into the other flow channel, such that the flow channels are specifically designed to guide exhaust gas from one flow channel to the corresponding other flow channel in the open position. This allows for particularly advantageous operation because the flow channels can also be significantly in fluid communication with each other at a small opening angle, i.e., when the valve is slightly open.

[0023] Another implementation is characterized by the flow channels being fluidly blocked through the turbine housing wall region in the closed position. This ensures, in a very simple way, that no exhaust gas can overflow from one flow channel to the corresponding other flow channel in the closed position, thus allowing the flow channels to be fluidly isolated or fluidly connected to each other, as needed and selectively.

[0024] In a particularly advantageous embodiment of the invention, the flow port is completely closed by means of a valve in the closed position. This allows for precise and predetermined switching between flow channel connectivity (i.e., fluid communication between the flow channels) and flow channel isolation (meaning the flow channels are particularly completely fluidly isolated from each other). This enables highly advantageous operation.

[0025] The second aspect of the invention relates to an internal combustion engine for motor vehicles, simply referred to as an internal combustion engine or engine, and designed, for example, as a piston engine. The internal combustion engine has at least one exhaust gas turbocharger having a turbine according to the first aspect of the invention. The advantages and advantageous designs of the first aspect of the invention should be regarded as advantages and advantageous designs of the second aspect of the invention, and vice versa. Attached Figure Description

[0026] Other advantages, features, and details of the invention will become apparent from the following description of preferred embodiments and from the figures. The features and combinations of features mentioned above in the specification, as well as those mentioned below in the description of the drawings and / or shown individually in the figures, may be used not only in the correspondingly specified combinations, but also in other combinations or individually, without departing from the scope of the invention. The figures show:

[0027] Figure 1 A perspective view of a portion of the turbine used in an internal combustion engine exhaust gas turbocharger is shown.

[0028] Figure 2 Another perspective view of a section of the turbine is shown.

[0029] Figure 3 Another perspective view of a section of the turbine is shown.

[0030] Figure 4 A perspective schematic diagram showing a first embodiment of the valve components of a turbine is shown.

[0031] Figure 5 A perspective view of a second embodiment of the valve is shown.

[0032] In the figures, identical or functionally identical components are labeled with the same reference numerals. Detailed Implementation

[0033] Figure 1 and Figure 2 Partial cross-sections of the turbine 10 for an internal combustion engine exhaust gas turbocharger are shown in perspective schematic diagrams. The internal combustion engine is, for example, designed as a piston engine and has multiple combustion chambers. For example, an internal combustion engine has at least or exactly four combustion chambers. Each combustion chamber is partially defined by a corresponding cylinder. A corresponding piston is movably accommodated within the corresponding cylinder, wherein the corresponding combustion chamber is defined partly by the corresponding cylinder and partly by the corresponding piston movably accommodated within the corresponding cylinder. During the ignition operation of the internal combustion engine, a combustion process takes place within the combustion chamber. During this combustion process, a fuel-air mixture, also simply referred to as a mixture, is burned. The mixture includes at least air and, in particular, fluid fuel. The internal combustion engine is preferably a gasoline engine. The combustion process produces exhaust gases. The exhaust gases can flow out from the corresponding combustion chamber, into an internal combustion engine exhaust gas device, and through the exhaust gas device. Here, the turbine 10 of the exhaust gas turbocharger is arranged in an exhaust gas device, also known as an exhaust manifold.

[0034] The exhaust gas turbocharger has a compressor / air compressor located within the intake manifold of the internal combustion engine, also known as the intake manifold. Here, the aforementioned air can flow through the intake manifold and, via the intake manifold, enter the combustion chamber. The air flowing through the intake manifold can be compressed by the compressor.

[0035] From Figure 1 and 2 As seen in the image, the turbine 10 has a turbine casing 12 with exactly two flow channels 14 and 16, wherein the flow channels 14 and 16 are fluidly isolated from each other and can be traversed by exhaust gas. Figure 1 and 2In the illustrated embodiment, the turbine 10 is designed as a two-stage segmented turbine. This means that the corresponding flow channels 14, 16 have corresponding outlets 18, 20 and lead into the receiving area 22 of the turbine housing 12 through the corresponding outlets 18, 20, wherein the outlets 18, 20 are consecutively arranged in the circumferential direction of the turbine 10, i.e., sequentially arranged. Furthermore, the turbine 10 has a turbine impeller 24, which is housed in the receiving area 22 and further housed in the turbine housing 12, and is rotatable relative to the turbine housing 12 about a rotational axis. The aforementioned circumferential direction of the turbine 10 extends about the rotational axis such that the outlets 18, 20 are sequentially arranged in their circumferential direction when viewed from their circumferential side along the circumference of the turbine impeller 24. Here, the corresponding flow channels 14, 16 are designed as helical channels. The flow channels 14, 16 are fluidly isolated from each other by the partition wall 26 of the turbine housing 12. Figure 1 Arrow 28 indicates the first flow of exhaust gas, which in this case flows through the inrush channel 14. Arrow 30 indicates the second flow of exhaust gas through the turbine housing 12, which will be explained in detail below.

[0036] The turbine 10, and especially the turbine housing 12, has a bypass passage indicated by arrow 32, through which at least a portion of the exhaust gas can bypass the turbine impeller 24. Arrow 32 shows that the exhaust gas flowing through the bypass passage bypasses the turbine impeller 24 and therefore does not drive it. The exhaust gas flowing through the corresponding inflow channels 14, 16 and guided into the receiving area 22 via these channels flows towards and drives the turbine impeller 24, causing it to rotate about its axis of rotation relative to the turbine housing 12. The compressor here has a compressor impeller arranged in the intake manifold, which can be driven by the turbine impeller 24 via a shaft. By driving the compressor impeller, the air flowing through the intake manifold can be compressed.

[0037] The turbine 10, and especially the turbine housing 12, has exactly one flow port 34 formed in the partition wall 26. As will be explained in detail below, the flow channels 14 and 16 are in fluid communication with each other by means of the flow port 34, especially at exactly one location S.

[0038] Turbine 10 has in Figure 1 The valve element 36, also referred to as the valve body, is partially visible in the turbine housing 12. The valve element 36 is movable relative to the turbine housing 12 between a closed position, in particular, where the bypass passage and flow port 34 are completely closed, and an open position, in which at least one of the bypass passage and flow port 34 is at least partially open. Figure 1 and Figure 2As shown. According to arrows 28 and 32, and another arrow 38, the exhaust gas, for example, first flows through the flow channel 14. If valve 36 is in its open position, a first portion of the exhaust gas that first flows through the flow channel 14 exits from the flow channel 14, flows through the flow port 34, and flows into the flow channel 16. This first portion then flows through the flow channel 16 and is guided by the flow channel 16 into the receiving area 22 and subsequently to the turbine impeller 24. A second portion of the exhaust gas that first flows through the flow channel 14 remains in the flow channel 14 and is guided by the flow channel 14 to and into the receiving area 22 and subsequently to the turbine impeller 24. The first portion of the exhaust gas is indicated by arrow 38, while arrow 28 indicates the second portion. Arrow 32 indicates that a third portion of the exhaust gas, initially flowing through the inflow channel 14, enters the bypass channel, particularly through the flow port 34, with valve 36 in the open position. This gas then flows through the bypass channel and subsequently around the turbine impeller 24. In the closed position, valve 36 completely closes the flow port 34, thus completely blocking its fluid flow. It is also preferred that valve 36 completely closes the bypass channel in the closed position, i.e., completely blocking the fluid flow. In the open position, valve 36 at least partially opens both the flow port 34 and the bypass channel.

[0039] Here, turbine 10 can have in Figure 1 The actuator 40, which is schematically represented or also referred to as an actuating component, thereby, for example, moving the valve 36 relative to the turbine housing 12 from a closed position to an open position and / or from an open position to a closed position. For example, the actuator 40 is an electric actuator, and therefore an electrically driven actuator; hence, the actuator 40 is also referred to as an electric regulator. More preferably, the valve 36, when moving from the closed position to the open position, simultaneously at least partially opens both the bypass passage and the flow port 34.

[0040] Now, in order to achieve a particularly advantageous fluid communication, also known as a flow channel connection, in the location S, such as in the assembly... Figure 4 and 5 As can be clearly seen, valve 36 has at least one or more features, or as shown in... Figure 4 and 5 The middle is set to have exactly one that completely passes through the valve member 36 and therefore extends within the valve member 36, and as in Figure 4 Arrow 42 indicates the flow channel 44 through which the exhaust gas can flow, which is particularly fully defined by the valve 36 in its entire circumferential direction within the valve 36. Figure 4 Arrow 42 indicates the flow of exhaust gas via flow channel 44. The turbine 10 is designed such that flow channels 14 and 16 are in fluid communication with each other via flow channel 44 when valve 36 is in the open position.

[0041] For example, valve 36 is pivotable about a pivot axis between the open and closed positions. Therefore, valve 36 can, for example, pivot to different angular positions, also called rotational positions. One of these, especially exactly one of these angular positions, is the closed position. Another or all other angular positions are also called opening angles and are opening positions in which valve 36 opens both the bypass channel and the flow port 34, especially simultaneously. Especially at small opening angles, for example, valve 36 opens a first partial region of the flow port 34, but valve 36 still protrudes into a second partial region of the flow port 34, especially immediately adjacent to the first partial region, so that valve 36 is still positioned in the second partial region even at a small opening angle. If valve 36 does not have a flow path (such as flow channel 44) through which waste gas can flow, then waste gas can only flow through the opened first partial region of the flow port 34, but cannot utilize the second partial region to overflow from one of the flow channels 14, 16 into the corresponding other flow channel 16 or 14. However, valve 36 now has a flow channel 44, which extends, for example, from a first end E1 to a second end E2. Here, end E1 is arranged, for example, in a second partial region of the flow port 34 at a small opening angle, such that exhaust gas can now flow into the flow channel 44 from one end E1, E2 to the other end E2, E1 and thus through the flow channel 44, and then be guided from one of the flow channels 14, 16 to the corresponding other flow channel 16 or 14 via the flow channel 44. Thus, exhaust gas not only flows from one of the flow channels 14 or 16 to the corresponding other flow channel 16 or 14 through the opened first partial region, but also flows through the flow channel 44 and thus through the flow channel 44 from one of the flow channels 14 or 16 to the corresponding other flow channel 16 or 14. Therefore, flow channel 44 is a fluid connection between flow channels 14 and 16, in addition to the first local area that is opened, so that, for example, a large amount of waste gas mass flow can also overflow between flow channels 14 and 16, and in particular, valve 36 opens the bypass channel only slightly.

[0042] Figure 4 A first embodiment of the valve 36 is shown. In the first embodiment, end E2 is arranged on the axial end side 46 of the valve 36.

[0043] Typically, and especially when valve 36 lacks a flow path (such as flow path 44) through which exhaust gas can flow, the ratio of the first mass flow of exhaust gas flowing through the bypass passage in the open position to the second mass flow of exhaust gas flowing through the flow port 34 in the open position, also known as the mass flow ratio, is defined solely by the contour of the outer periphery of valve 36, also referred to as the valve body. This mass flow ratio depends on the corresponding opening angle of valve 36. However, it is generally not possible to produce any desirable inrush passage connectivity feature from an engine perspective geometrically, i.e., by the contour of valve 36. Based on the dimensions of the exhaust gas turbocharger, the specifications of actuator 40, and the catalytic converter flow direction, several parameters of turbine 10, and primarily valve 36, are determined, particularly regarding inrush passage connectivity and the opening and closing of the bypass passage. Adjusting the movement of valve 36, or the shape and, consequently, the outer periphery of valve 36, and then changing the opening mechanism, directly affects the required protection range. Therefore, valve 36 occupies a special position in defining inrush passage connectivity and, in particular, its characteristics.

[0044] The engine-related objective might be to establish a target curve for the inflow channel connectivity characteristics during engine process simulation. Typically, this target curve, also simply referred to as the curve, indicates the maximum adjustment range of valve 36, within which the flow port 34, also known as the inflow channel connectivity area, is first increased, while the second area, the area for exhaust gas to flow into the bypass channel, also known as the exhaust valve area, only increases significantly at the maximum opening angle of valve 36. If such possibilities (e.g., by adjusting valve 36) have been exhausted and the overall increase of valve 36 is excluded, then according to the prior art, further increases in the inflow channel connectivity area cannot be achieved. Therefore, one objective could be to make the inflow channel connectivity characteristics approach the target curve in other ways, and here through, for example, an additional feature. This additional feature should be prevented from affecting the inflow channel connectivity characteristics when valve 36 is closed, i.e., in the closed position. Simulations show that although valve 36, without flow channel 44, can achieve fairly significant or large-scale flow channel connectivity due to its expensive and complex, especially peripheral geometry and thus profile, it may not be possible to use the entire local area of ​​the flow port 34 opened by valve 36 in the corresponding open position for fluid connectivity of flow channels 14, 16. This may be attributed to undesirable flow guidance toward valve 36, especially when the exhaust gas turbocharger structure is small.

[0045] By equipping valve 36 with at least or exactly one flow channel 44, the flow channel connectivity can be optimized at least approximately selectively. By equipping valve 36 with flow channel 44, another cross section is provided for the exhaust gas or its flow to be used for flow channel connectivity, because the exhaust gas can now overflow from one flow channel 14, 16 to the corresponding other flow channel 16 or 14 not only through the first local area opened by the flow port 34, but also through the flow channel 44 opened in the open position.

[0046] exist Figure 4 In the first embodiment shown, for example, end E2 is the channel outlet, which appears at the height of the partition in the first embodiment. This prevents fluid communication between the flow channels 14, 16 in the closed position of valve 36, specifically in that, in the closed position, end E2 and consequently flow channel 44 are closed, i.e., blocked by fluid, particularly in that, for example, the axial end side 46 and consequently end E2 are in close contact with the corresponding wall of the turbine housing 12 in the closed position. Thus, for example, the entire outlet (end E2) is closed through this wall. It has been found that, furthermore, the local high speed at the partition, or the resulting low static pressure, can be used to guide the largest possible mass flow from the active flow channels 14, 16 to the passive flow channels 16, 14. The active and passive flow channels specifically refer to: at least one of the first combustion chambers, especially at least or exactly two of the first combustion chambers, correspondingly assigned to flow channel 14, and in particular, fluidly connected to flow channel 14; wherein at least one of the second combustion chambers, especially at least or exactly two of the second combustion chambers, correspondingly assigned to flow channel 16, and in particular, fluidly connected to flow channel 16. Exhaust gas from the first combustion chambers, especially with respect to flow channels 14 and 16, initially flows only into flow channel 14 and not into flow channel 16. Exhaust gas from the second combustion chambers, especially with respect to flow channels 14 and 16, initially flows into flow channel 16 but not into flow channel 14. Figure 1 The flow channel 14 is an active flow channel, and the flow channel 16 is a passive flow channel because, for example, with respect to the first combustion chamber and the second combustion chamber, only the first combustion chamber supplies exhaust gas. Therefore, exhaust gas from the first combustion chamber first flows into the flow channel 14, and then, at least partially, flows from the flow channel 14 into the flow channel 16 when the valve 36 is in the open position. Figure 2 In the middle, flow channel 16 is an active flow channel, while flow channel 14 is a passive flow channel, because according to Figure 2 Regarding the first and second combustion chambers, only the second combustion chamber supplies exhaust gas, while the first combustion chamber does not. Therefore, the exhaust gas from the second combustion chamber first flows into the inflow channel 16, and then, when the valve 36 is in the open position, at least partially flows out of the inflow channel 16 at part S and into the inflow channel 14. (As in...) Figure 1 Like in the middle, in Figure 2The middle arrow 28 indicates the following exhaust gas, which first flows into and remains in the active inrush channel, is guided by the active inrush channel to and enters the containment area 22, and thus reaches the turbine impeller 24. (As in...) Figure 1 Like in the middle, in Figure 2 The middle arrow 38 indicates the following exhaust gas, which first flows into the active flow channel, but does not remain there. Instead, it flows through the at least partially open passage 34 at point S and thus overflows from the active flow channel into the passive flow channel. Additionally, in Figure 2 It is like being in Figure 1 As shown in the image, arrow 32 indicates the exhaust gas flowing through the bypass channel.

[0047] Now, since both the first partial region opened at the corresponding opening position and the flow channel 44 are available for exhaust gas, especially from the active flow channel, to overflow from the active flow channel into the passive flow channel, a large exhaust gas mass flow can be achieved even with a small opening angle, as it overflows from the active flow channel into the passive flow channel. Compared to valve 36 without flow channel 44, a significant increase in the flow channel connectivity can be determined, i.e., a significant increase in the exhaust gas mass flow overflowing from the active flow channel into the passive flow channel. In particular, turbine power can be increased even when valve 36 is in the same position by incorporating flow channel 44.

[0048] For example, valve 36 itself is designed to be solid and is provided with a flow channel 44. The flow channel 44 is formed by at least one orifice, exactly one orifice, or at least or exactly two orifices. The flow channel 44 is an internal flow channel of valve 36, used to achieve advantageous flow channel communication. In the closed position, the flow channel 44 does not create fluid communication between flow channels 14 and 16. However, in the open position, the flow channel 44 creates additional mass flow, also known as flow channel communication mass flow, between flow channels 14 and 16, in addition to the fluid communication between the first open local area and the waste gas overflowing from the active flow channel to the passive flow channel. This additional flow channel communication mass flow is achieved in addition to the waste gas mass flow through the first open local area. The additional flow channel 44 can be formed by a single orifice or multiple intersecting and therefore fluidly communicating orifices. It is conceivable that valve 36 has multiple fluidly separated flow channels such as flow channel 44 within valve 36. The flow channel 44 may be configured to facilitate flow, particularly with respect to one or more of its arcs and / or one or more of its fillets.

[0049] Exhaust gas can flow into flow channel 44 from the corresponding active overflow channel via, for example, an inlet located at or through end E1. In the case of the corresponding active overflow channel, which is therefore the overflow channel being supplied with gas, and for example, when valve 36 is fully open, for example, when the opening angle is greater than 30% of the maximum opening angle, the inlet of this channel is directly located in the overflow exhaust gas or its flow, and thus allows the exhaust gas to flow directly into flow channel 44. The outlet of flow channel 44, for example, located at end E2 and formed by end E2, is located at, for example, a portion of valve 36 that is blocked when valve 36 is closed, i.e., in the closed position.

[0050] exist Figure 4 In the embodiment shown, the flow channel 44 terminates directly at its end E2 at the partition wall where the flow channel is connected.

[0051] Figure 5 The second embodiment is shown, in which end E2 is arranged on the back side of valve 36, which, in the closed position, is in close contact with a wall, also known as a wall portion, for example, formed by a housing, in which valve 36 is arranged. This housing is, for example, turbine housing 12, but may also be another housing separately constructed from and connected to turbine housing 12.

[0052] List of reference numerals

[0053] 10 Turbines

[0054] 12 Turbine casing

[0055] 14. Flow channel

[0056] 16 Flow Channel

[0057] 18 Outlets

[0058] 20 Outlets

[0059] 22 Accommodation Area

[0060] 24 Turbine impeller

[0061] 26. Partition wall

[0062] 28 arrows

[0063] 30 arrows

[0064] 32 arrows

[0065] 34 Circulation Port

[0066] 36 valve components

[0067] 38 arrows

[0068] 40. Implementing agencies

[0069] 42 arrows

[0070] 44 flow channels

[0071] 46 end side

[0072] E1 First End

[0073] E2 Second End

Claims

1. A turbine (10) for an exhaust gas turbocharger, comprising: The turbine housing (12) has at least two flow channels (14, 16) that are at least partially fluid-isolated from each other and through which exhaust gas from an internal combustion engine can pass, the flow channels being fluidly isolated from each other by means of a partition wall (26) of the turbine housing (12); A turbine impeller (24) housed in the turbine housing (12) and driven by exhaust gas; At least one bypass channel (32) through which the turbine impeller (24) can be bypassed by at least a portion of the exhaust gas; At least one flow port (34) is formed in the partition wall (26), through which the flow channels (14, 16) are in fluid communication with each other; and At least one valve (36) is movable between a closed position that closes the bypass passage (32) and the flow port (34) and at least one open position that at least partially opens the bypass passage (32) and the flow port (34), wherein, The valve (36) has at least one flow channel (44) through which the exhaust gas flows. Its characteristics are, In this closed position, the flow port (34) is completely closed by means of the valve (36), and in this closed position, the fluid communication between the flow channels (14, 16) caused by the flow channel (44) is prohibited, so that the flow channels (14, 16) are not in fluid communication with each other through the flow channel (44) in this closed position. In the open position, the valve (36) opens a first partial area of ​​the flow port (34) and also protrudes into and is thus arranged in a second partial area of ​​the flow port (34) immediately adjacent to the first partial area, wherein the flow channel (44) is located in a portion of the second partial area. Therefore, the flow channel (44) is an additional fluid communication between the flow channels (14, 16) in addition to the opened first partial area, and exhaust gas can flow through the opened first partial area and the flow channel (44) and further through the portion of the second partial area. The flow channel (44) has at least one arched length section, and / or The flow channel (44) has at least two length regions that extend at an angle or perpendicular to each other, and / or The flow channel (44) extends in an S-shape or Z-shape at least in a local area.

2. The turbine (10) according to claim 1, characterized in that, The flow channels (14, 16) are in fluid communication with each other through the flow channel (44) when the valve (36) is in the open position.

3. The turbine (10) according to claim 1 or 2, characterized in that, The flow channel (44) is blocked by fluid through the wall region of the turbine housing (12) in the closed position.

4. The turbine (10) according to any one of the preceding claims, characterized in that, In the closed position, the flow port (34) is completely closed by means of the valve (36).

5. An internal combustion engine for a motor vehicle, having at least one exhaust gas turbocharger having a turbine (10) according to any one of the preceding claims.

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