DE102020123178A1 - Valve device of an exhaust gas guide section of an exhaust gas turbocharger and exhaust gas guide section of an exhaust gas turbocharger - Google Patents

Abstract

The invention relates to a valve device of an exhaust gas routing section of an exhaust gas turbocharger, with a valve system (11) comprising a first valve body (9) for opening or closing an overflow opening (10) of the exhaust gas routing section ( 1) and a second valve body (30) for opening or closing a flow opening (15) of a bypass channel (14) of the exhaust gas routing section (1), wherein the valve system (11) is accommodated on a valve lever arm (12) of the valve device (8), and wherein the valve lever arm (12) can be moved with the aid of a movement device (18) of the valve device (8). According to the invention, the first valve body (9) is designed to be movable relative to the second valve body (30). Furthermore, the invention relates to an exhaust gas routing section of an exhaust gas turbocharger.

Description

The invention relates to a valve device of an exhaust gas routing section of an exhaust gas turbocharger of the type indicated in the preamble of patent claim 1. The invention also relates to an exhaust gas routing section of an exhaust gas turbocharger according to the preamble of patent claim 13.

Valve devices for exhaust gas routing sections are known. For example, exhaust gas guide sections have a bypass channel for the controllable inflow of a turbine wheel rotatably accommodated in the exhaust gas guide section, which bypass channel is opened or closed with the aid of a valve device. Furthermore, in the case of exhaust gas routing sections, in particular designed with two flows, the valve devices serve to open and close an overflow opening formed between the two flows. The valve device can be designed to open and close the overflow opening and to open and close the bypass channel. In other words, this means that a single valve device, comprising a single valve body, is designed to regulate the inflow onto the turbine wheel.

In the open state, the valve body is positioned in an exhaust gas stream flowing through the exhaust gas guide section and is subjected to a force by this stream. As a result, movements of the valve body can be initiated, which lead to relative movements between the valve body and a valve lever arm that accommodates it movably in the exhaust gas guide section. This can result in noises, for example due to rattling.

That's what the patent says DE 10 2012 015 536 B2 a valve device of an exhaust-gas guide section of an exhaust-gas turbocharger, the exhaust-gas guide section having a single-flow design and having a bypass channel for bypassing a turbine wheel rotatably accommodated in the exhaust-gas guide section. A valve disk of the valve device is in a closed position, in which a throughflow opening formed in the bypass channel is closed with the aid of the valve disk, a longitudinal center axis of the valve disk is configured at a distance from a longitudinal center axis of the throughflow opening.

The disclosure document WO 2017/108160 A1 discloses a valve device of an exhaust-gas routing section of an exhaust-gas turbocharger, the exhaust-gas routing section having two flows and a bypass channel. The valve device is used to open and close the bypass channel and to open and close a flow connection cross section formed in the exhaust gas routing section.

The object of the present invention is to provide an improved valve device of an exhaust gas routing section of an exhaust gas turbocharger. The further object is to specify an improved exhaust-gas routing section of an exhaust-gas turbocharger.

According to the invention, this object is achieved with a valve device of an exhaust gas routing section of an exhaust gas turbocharger with the features of claim 1 . The further object is achieved according to the invention with an exhaust gas routing section of an exhaust gas turbocharger with the features of claim 13. Advantageous configurations with expedient and non-trivial developments of the invention are specified in the dependent claims.

A valve device according to the invention of an exhaust gas routing section of an exhaust gas turbocharger has a valve system, comprising a first valve body for opening or closing an overflow opening of the exhaust gas routing section formed between a first spiral channel and a second spiral channel, and a second valve body for opening or closing a throughflow opening of a bypass channel of the exhaust gas routing section. The valve system is accommodated on a valve lever arm of the valve device. The valve lever arm can be moved with the aid of a movement device of the valve device. According to the invention, the first valve body is designed to be movable relative to the second valve body. In other words, this means that the two valve bodies can be moved relative to one another. The advantage can be seen in an at least to a certain extent decoupling of opening or closing times of the flow opening and the overflow opening. In other words, this means that, for example, the flow-through opening can still be completely closed, with the overflow opening already being at least partially open.

In one embodiment of the valve device according to the invention, the first valve body is immovably accommodated on the valve lever arm relative to the latter. This means that during operation of the exhaust gas turbocharger between the first valve body and the valve lever arm, no moments can be brought about by exhaust gas forces acting on the first valve body, in particular pulsating exhaust gas forces, due to the fixed connection. Thus, there is no wear due to friction between the two components. The second valve body, which is movable relative to the first valve body, since it has the function of closing or opening the through hole, can be used be formed benformartig and thus has a low weight, so that possible contact points with the valve lever arm and / or the first valve body have less wear.

In particular, a gas force acting on the second valve body is not oscillating but pulsating, and thus swelling in only one direction.

Furthermore, the second valve body has a lower temperature than the first valve body during operation of the valve device, since it is not firmly connected to the first valve body, and thus has fewer temperature fluctuations in the material and less wear. It goes without saying that the second valve body already has a lower temperature than the first valve body due to its position at the through-flow opening, since exhaust gas is not directly applied to it permanently.

If the second valve body is designed to at least partially encompass the first valve body and vice versa, a compact valve device can be implemented.

In a further embodiment of the valve device according to the invention, the valve lever arm is arranged opposite the second valve body and is designed to be in contact with it. The second valve body is thus in direct contact with the valve lever arm, so that when the valve lever arm moves, in particular when the throughflow opening is closed, the second valve body can be arranged to close the throughflow opening without a time delay.

In a further embodiment of the valve device according to the invention, a valve lever arm surface of the valve lever arm forming the contact is designed to be complementary to an opposite section surface of the second valve body forming the contact, as a result of which a sealing contact, or in other words a sealing surface, can advantageously be formed.

If the valve lever arm and the second valve body are convexly curved in the area of contact in the direction of the first valve body, there is the advantage of the second valve body being able to move relative to the valve lever arm without jamming. The advantage is a creation of an increased contact area compared to a non-curved contact area. Furthermore, when the valve bodies are in an open position, the valve bodies are pressed by exhaust gases against the valve lever arm, with the curved design, in particular the convexly curved design, in particular the dome-shaped design, centering the valve bodies on the valve lever arm and avoiding or at least reducing rattling in particular will. A further advantage of the curved surfaces is the formation of a large sealing surface between the valve lever arm and the second valve body when the valve body is in a closed position.

If a pretensioning element is designed to secure the position of the second valve body relative to the valve lever arm, it is possible to keep the throughflow opening securely closed when the overflow opening is already open.

In order to reduce wear and increase permanent loading of the prestressing element, this is arranged between the second valve body and the valve lever arm. At this position, exhaust gas, in particular hot exhaust gas, flows around the prestressing element only when the through-flow channel is open, so that the permanent thermal load on the prestressing element is interrupted by the exhaust gas flow around it. This can increase its lifespan.

The second aspect of the invention relates to an exhaust gas duct section of an exhaust gas turbocharger, comprising a first spiral duct, a second spiral duct and a bypass duct, the bypass duct being designed to bypass a turbine wheel rotatably accommodated in the exhaust gas duct section, and the bypass duct having a flow opening, and between the first Spiral channel and the second spiral channel an overflow opening is provided, which is designed to bring about an overflow of exhaust gas from the first spiral channel into the second spiral channel and vice versa, and wherein a valve device is assigned to the exhaust gas guide section, with the help of which the overflow opening and the throughflow opening can be opened or is to be closed, and wherein, in order to reduce wear, the valve device is designed according to one of claims 1 to 12. The advantage is the realization of a reduced-wear exhaust gas routing section, which thus has a longer service life, which means that so-called guarantee and goodwill costs can be reduced. Furthermore, due to the valve bodies that can be moved relative to one another, operation of the exhaust gas turbocharger can be further improved in terms of operation of an internal combustion engine thermodynamically coupled to the exhaust gas turbocharger, which can bring about a reduction in consumption and/or an increase in the output of the internal combustion engine.

• 1 in einem Schnitt einen Abgasführungsabschnitt eines Abgasturboladers mit einer Ventilvorrichtung gemäß dem Stand der Technik in einer ersten Betriebsposition,
• 2 in einer perspektivischen Darstellung die Ventilvorrichtung gemäß dem Stand der Technik,
• 3 in einem Schnitt die Ventilvorrichtung gemäß 2,
• 4 in einer perspektivischen Darstellung die Ventilvorrichtung gem. 2 in einer ersten Betriebsposition in einem Abgasführungsabschnitt eines Abgasturboladers,
• 5 in einem Schnitt eine erfindungsgemäße Ventilvorrichtung in einem ersten Ausführungsbeispiel,
• 6 in einem Schnitt die erfindungsgemäße Ventilvorrichtung in einem zweiten Ausführungsbeispiel in der ersten Betriebsposition, und
• 7 in einem Schnitt die erfindungsgemäße Ventilvorrichtung gemäß dem zweiten Ausführungsbeispiel in einer Zwischenposition.

Further advantages, features and details of the invention result from the following Description of preferred embodiments and based on the drawing. The features and combinations of features mentioned above in the description and the features and combinations of features mentioned below in the description of the figures and/or shown alone in the figures can be used not only in the combination specified in each case, but also in other combinations or on their own, without going beyond the scope of the leave invention. Identical reference symbols are assigned to elements that are the same or have the same function. Show it:

• 1 in a section, an exhaust gas guide section of an exhaust gas turbocharger with a valve device according to the prior art in a first operating position,
• 2 in a perspective view, the valve device according to the prior art,
• 3 in a section according to the valve device 2 ,
• 4 in a perspective view, the valve device gem. 2 in a first operating position in an exhaust gas routing section of an exhaust gas turbocharger,
• 5 in a section a valve device according to the invention in a first embodiment,
• 6 in a section, the valve device according to the invention in a second embodiment in the first operating position, and
• 7 in a section, the valve device according to the invention according to the second embodiment in an intermediate position.

A according 1 Formed flow-through exhaust gas guide section 1 of an exhaust gas turbocharger 2 according to the prior art comprises an inlet channel 3 for the entry of a fluid flow into the exhaust gas guide section 1, generally exhaust gas from an internal combustion engine 7, a first spiral channel 4 and a second spiral channel 5 downstream of the inlet channel 3 for conditioning the flow, and an outlet channel, not shown in detail, downstream of the spiral channels 4, 5, via which the exhaust gas can escape from the exhaust gas guide section 1 in a targeted manner. Between the spiral ducts 4, 5 and the outlet duct, a wheel chamber, not shown in detail, is formed, in which a turbine wheel, not shown in detail, is rotatably accommodated. The spiral channels 4, 5 can be flowed through separately from one another with the aid of a partition T. An overflow opening 10 is formed in the partition T so that exhaust gas can flow from the first spiral duct 4 into the second spiral duct 5 and vice versa.

The exhaust gas routing section 1 also has a bypass channel 14 for bypassing the turbine wheel, with the bypass channel 14 having a throughflow opening 15 via which the exhaust gas can be guided past the turbine wheel.

The exhaust gas routing section 1 is connected to an exhaust manifold 6 of the internal combustion engine 7, so that the exhaust gas of the internal combustion engine 7 can enter the spiral ducts 4, 5 via the inlet duct 3 in order to act on the turbine wheel.

In order to adapt the operating behavior of the exhaust gas turbocharger 2 to the fluid flow of the internal combustion engine 7, and thus to the internal combustion engine 7, a valve device 8 with a valve system 11 for separating and connecting the first spiral channel 4 and the second spiral channel 5 and for opening or Closing the flow opening 15 arranged. To separate the two spiral ducts 4, 5, a first valve body 9 of the valve system 11 is arranged in the overflow opening 10, with the aid of which the two spiral ducts 4, 5 are designed so that a flow can flow through one another. The valve system 11 further comprises a second valve body 30 which is arranged in the through-flow opening 15 in order to close the bypass channel 14 . To move the first valve body 9 and the second valve body 30, a valve lever arm 12 of the valve device 8 is formed, which is firmly connected to at least one of the two valve bodies 9, 30. In the prior art, the valve lever arm 12 is firmly connected to the two valve bodies 9, 30, which are designed in one piece, with a valve arm 13 of the valve system 11 serving as the fixed connection.

In a first operating position, the closed position of the first valve body 9, as shown in 1 is shown, the two spiral channels 4, 5 can be flowed through completely separately from one another, the overflow opening 10 being completely closed with the aid of the valve body 9. The exhaust gas of the internal combustion engine 7 flows through the two spiral channels 4 , 5 , with a first part of the exhaust gas flowing through the first spiral channel 4 and a second part of the exhaust gas flowing through the second spiral channel 5 . Likewise, in this first operating position, and in particular due to the one-piece design of the two valve bodies 9, 30, the through-flow opening 15 is completely closed with the aid of the second valve body 30.

In a second operating position of the valve system 11, the overflow opening 10 is open and exhaust gas can flow out of the first spiral channel 4 into the second spiral channel 5 and vice versa. That is, exhaust gas from the one spiral channel 4; 5 in the other spiral channel 5; 4 can overflow via the overflow opening 10. Likewise, in the second position of the valve system 11, which corresponds to an open position, the flow opening 15 of the bypass channel 14 is open. This means that exhaust gas can also flow past the turbine wheel via the bypass channel 14 . A flow rate of the exhaust gas or its mass flow, which is routed via the bypass channel 14, is dependent on an opening position of the valve system 11. In other words, this means that due to the one-piece form of the first valve body 9 and the second valve body 30 in an open position, which is provided for opening the overflow opening 10, a quantity of exhaust gas formed as a function of the opening position can also flow via the bypass channel 14. This means that the valve device 8 according to the prior art opens the throughflow opening 15 immediately and directly when the overflow opening 10 is opened. If the valve system 11 is in a maximum opening position, the overflow opening 10 and the throughflow opening 15 are fully open, in the sense of maximum opening.

The valve system 11 is to be arranged between the first operating position and the second open position in further operating positions, so-called intermediate positions, so that the exhaust gas quantity flowing via the overflow opening 10 and/or the throughflow opening 15 can be adapted to achieve the highest possible efficiency of the exhaust gas turbocharger 2 in accordance with the exhaust gas quantity flowing through .

The valve lever arm 12 is connected to a moving device 18 of the valve device 8 for moving the valve system 11 . It is designed for pivoting about a pivot axis 20 at its end 19 of the lever arm facing away from the valve system 11 . For this purpose, an adjusting shaft 21 having the pivot axis 20 is arranged at the end 19 of the lever arm. This is rotatably accommodated in a guide opening 22 formed in the exhaust gas guide section 1 .

In order to bring about a preferred closing and opening of the overflow opening 10 and the throughflow opening 15 , the first valve body 9 has a projection 16 which faces away from the valve lever arm 12 . Depending on a contour 17 of the projection 16, certain opening and closing times as well as an effectively released flow cross section of the overflow opening 10 can be realized depending on a movement of the valve lever arm 12. Furthermore, the contour 17 can be formed in the through-flow opening 15 in order to implement a certain through-flow.

In the 2 until 4 a further valve device 8 according to the prior art is shown. The main difference to the valve system 11 acc. 1 is an interior space 23 formed in the valve system 11 and used to accommodate the valve lever arm 12 . In other words, that means that the first valve body 9 according to FIG. 2 is hollow, in particular pot-shaped. The valve arm 13 extends from a base 24 formed in the interior 23 of the first valve body 9 along a longitudinal valve axis 25 of the first valve body 9 in the form of a cylinder, in its longitudinal extension the second valve body 30, which is formed in the form of a ring , superbly executed. Thus, an arm longitudinal axis 31 of the valve arm 13 is formed coaxially with the valve longitudinal axis 25, which forms an axis of symmetry of the first valve body 9 in this exemplary embodiment. The second valve body 30 encompasses the first valve body 9 and projects beyond it in the radial direction and has a contact surface 26 for sealing contact in a valve seat 27 in the exhaust gas routing section 1 , which is associated with the flow opening 15 .

The end of the valve lever arm 12 that faces the valve arm 13 is designed to receive it in a receiving opening 28, as shown in FIG 3 is recognizable. For the secure connection and movement of the hollow first valve body 9 , the valve lever arm 12 is designed to extend into the interior space 23 and is supported with its end 32 opposite the base 24 on the base 24 . The receiving opening 28 has an opening longitudinal axis 29 which is coaxial with the valve longitudinal axis 25 in the first operating position of the first valve body 9 . The valve arm 13 has a securing element 33 for secure mounting on the valve lever arm 12 in the axial direction.

There is a first movement gap 34 between the valve arm 13 and the valve lever arm 12 and a second movement gap 35 between the base 24 and the valve lever arm 12, wear occurring when the opposing surfaces which form the movement gaps 34, 35 come into contact. Both movement gaps 34, 35 are dependent on the temperature of the exhaust gas in terms of their axial and radial expansion. The valve system 11, in particular the first valve body 9, the second valve body 30 and the valve arm 13, as well as a section of the valve lever arm 12 facing the valve arm 13, are permanently directly exposed to the exhaust gas flow and acted upon by it. Furthermore, in particular the first valve body 9 of the exhaust gas flow with its different pressures depending on an operating point of the internal combustion engine 7 and permanently exposed to pressure waves formed within the exhaust gas flow. In other words, this means that exhaust gas forces act on the first valve body 9 in particular and this is subject to alternating loads, which causes wear in particular in the area of the second movement gap 35 and due to a tilting of the valve arm 13 relative to a valve lever arm section 36 of the valve lever arm 12, which is located between the securing element 33 and the base 24 is formed, preferably in an area close to the base 24 and in an area of the valve arm 13 and the valve lever arm section 36 close to the securing element 33 .

The temperature of the exhaust gas flow also fluctuates depending on the operation of the internal combustion engine 7. A spatial expansion of the valve system 11 and the valve lever arm 12 is also dependent on the temperature of the exhaust gas flow and thus also fluctuates or changes with the operation of the internal combustion engine 7. In the first operating position of the valve device 8, this is irrelevant with regard to undesired noise emissions, but forces of the exhaust gas flow act almost entirely on the valve body 9, particularly in the maximum open position, which lead, for example, to rattling due to a movement of the valve system 11 relative to the valve lever arm 12.

one according to 5 trained valve device 8 according to the invention of a first embodiment preferably to eliminate but at least to reduce wear on the two valve bodies 9, 30 movable relative to each other.

The valve arm 13 , which is used to firmly connect the valve system 11 to the valve lever arm 12 , is firmly connected to the first valve body 9 . This means that the valve arm 13 is immovably accommodated relative to the first valve body 9 on the latter. In the present exemplary embodiment, it is designed in one piece with the first valve body 9 . In other words, this means that the first valve body 9 has the valve arm 13 which is connected to the valve lever arm 12 in a fixed and immovable manner. The second valve body 30 , which, in addition to its original function, serves to close the through-flow opening 15 and to cover the interior 23 , is designed to encompass the valve arm 13 . So that the interior 23 is completely covered and a secure seal of the flow opening 15 can be realized, the second valve body 30 is designed to extend in the radial direction beyond the first valve body 9, forming the contact surface 26. This means that a first radius R1 of the first valve body 9, which is an outer radius of a valve surface 42 of the first valve body 9 facing the second valve body 30, is smaller than a second radius R2 of the second valve body, which corresponds to an outer radius of the contact surface 26. In the closed state of the overflow opening 10 and the throughflow opening 15, contact is thus formed between the first valve body 9 and the second valve body 30, starting from the contact surface 26 in the direction of the first valve longitudinal axis 25, with the contact between an annular surface 43 of the second valve body 30 and the valve surface 42 is formed, with the annular surface 43 being positioned adjacent to the contact surface 26 in the direction of the longitudinal axis 25 of the valve.

In the present exemplary embodiment, the second valve body 30 has a guide sleeve 37 for the secure guidance of the valve system 11 with the aid of the valve arm 13 being accommodated in the guide sleeve 37 . The guide sleeve 37 is fastened to a cover disk 44 of the second valve body 30 that covers the interior space 23 , the cover disk 44 enclosing the contact surface 26 and the annular surface 43 . The guide sleeve 37 is preferably designed in one piece with the cover plate 44 . In order to stabilize the valve system 11 , it has a large length L in the direction of the first longitudinal valve axis 25 .

The longitudinal valve axis 25 of the first valve body 9 and a second longitudinal valve axis 38 of the second valve body 30 are coaxial. Likewise, the two longitudinal valve axes 25, 28 could also be spaced apart from one another, in which case the second valve body 30 could be arranged asymmetrically with respect to the valve seat 27. In other words, this means that a greater overlap of the valve seat 27 by the valve body 30 would be realized in sections, as a result of which sealing advantages could be achieved.

The second valve body 30 is at least partially designed to encompass the first valve body 9 and vice versa. The first valve body 9 can thus accommodate the second valve body 30, in particular its guide sleeve 37, and the second valve body 30 can cover the interior space 23, so that exhaust gas can flow into the interior space 23 even when the overflow opening 10 and/or the through-flow opening 15 is open preferably avoided, but at least reduced.

Between the first valve body 9 and the second valve body 30 there are two distances formed in the direction of the valve longitudinal axes 25, 38, a first distance 39 and a second distance 40 and a third distance 41 formed in the radial direction. These distances are 39, 40, 41 on the one hand required for the mobility of the second valve body 30, but on the other hand also due to changes in expansion of the valve device 8 during operation. Thus, the distances 39, 40, 41 are variable depending on the temperatures, the pressures and the movement of the valve device 8.

So that a tight seal between the first valve body 9 and the second valve body 30 can be achieved at least as far as possible, especially when the overflow and throughflow opening 10, 15 is closed, the first distance 39 has a value greater than zero. In other words, this means that there is no contact between the first valve body 9 and the second valve body 15 .

In order to reduce wear, in particular due to exhaust gas forces acting on the valve system 11 in the axial direction, at least one of the axial distances 39, 40 is designed to avoid contact between the first valve body 9 and the second valve body 30, i.e. in other words that it has a value greater than zero. To stabilize the valve system 11, a guide sleeve 37 that is as long as possible is required, but it does not have to touch the bottom 24 for reliable guidance, since the contact between the two valve bodies 9, 30 can already be established. Thus, the second distance 40, which is designed to avoid contact, between the guide sleeve 37 and the bottom 24 is realized. The radial third distance 41 is formed between the guide sleeve 37 and the valve arm 13 . Thus, when the guide sleeve 37 is formed, a sufficient guidance of the valve system 11 can be achieved while at the same time avoiding a wear-producing contact.

With the above-described positioning of the distances 39, 40, 41, mobility of the second valve body 30 with reduced wear can be brought about while the same still has high mobility. Furthermore, due to the positioning of the contact in the area of the first distance 39 with the first radius R1, a large impact surface is formed between the first valve body 9 and the second valve body 30, as a result of which the closing pressures acting on the valve system 11 between the two valve bodies 9, 30 can be reduced compared to the prior art.

In the present exemplary embodiment, the valve lever arm 12 is arranged opposite the second valve body 30 and is designed to be in contact with it. As a result, a reliable movement of the second valve body 30, which can be moved relative to the first valve body 9, is formed. In other words, when the through-flow opening 15 is closed, the valve lever arm 12 acts directly on the second valve element 30 and moves it into its intended closed position until the contact surface 26 comes into contact with the valve seat 27.

A valve lever arm surface 45 of valve lever arm 12, which forms the contact between valve lever arm 12 and second valve body 30, is complementary to an opposite section surface 46 of second valve body 30, which forms contact, valve lever arm surface 45 being convex in the direction of projection 16. The section surface 46 is a section of the cover disk 44 and adjoins the annular surface 43 in the direction of the second valve longitudinal axis 38, but faces away from it in the axial direction. In other words, the valve lever arm 12 and the second valve body 30 are convexly curved in the area of contact in the direction of the first valve body 12 . Likewise, the curvature can also be a spherical curvature.

In an exemplary embodiment that is not shown in detail, the surfaces 44 , 45 that form the contact are curved in a concave manner in relation to the base 24 . In this case, a ring or a ring section extending adjacent to the surface 44 in the radial direction away from the first longitudinal valve axis 25 is configured. A gap is formed between the ring section and the opposite surface of the second valve body 30 to allow the second valve body 30 to move, with the ring section serving as a limit stop.

The curvatures, in particular the convex curvatures, serve to improve the mobility of the second valve body 30.

In 5 force flow lines K are drawn in, which illustrate a force flow on the valve system 11 of the valve device 8 according to the invention. With the help of the fixed connection of the first valve body 9 and the valve lever arm 12, in particular the valve arm 13 and the valve lever arm 12, the preferred flow of forces can be achieved. The valve arm 13 is, for example, integrally welded to the valve lever arm 12, preferably at low cost.

In the 6 and 7 the valve device 8 according to the invention is shown in a second exemplary embodiment. In 6 the valve device according to the second embodiment is illustrated in the first operating position, in 7 she is shown in an intermediate position. In other words, this is an operating position between full closure of the over flow opening 10 and the flow opening 15 and a complete opening of the two openings 10, 15.

A pretensioning element 47 is arranged between the second valve body 30 and the valve lever arm 12 and has a hold-down function. This means that according to a prestressing force of the prestressing element 47 of the second valve body 30 the contact surface 26 can be in sealing contact with the valve seat 27 until the prestressing force is overcome. This makes it possible to open the overflow opening 10 with the aid of the valve lever arm 12, with the throughflow opening 10 being closed, as is shown in FIG 7 is shown.

The second valve body 30 can be lifted off the valve seat 27 with the aid of the first valve body 9 if the first distance 39 has a value of zero, the first valve body 9 is thus in contact with the second valve body 30 .

In the present exemplary embodiment, the pretensioning element 47 is designed in the form of a spiral spring. However, it can also have a different shape, for example it can be designed in the form of a plate spring.

To achieve the same effect, namely the opening of the overflow opening 10 without the opening of the through-flow opening 15, the prestressing element 47 could also be arranged between the base 24 and the guide element 37 of the second valve body 30. The positioning between the valve lever arm 12 and the second valve body 30 is to be preferred, however, since the exhaust gas flows continuously around the first valve body 9 and thus its bottom 24 .

The valve system 11 is thus formed, which comprises the first valve body 9 and the second valve body 30, with the two valve bodies 9, 30 being movable with a single valve lever arm 12, and with the overflow opening 10 and the throughflow opening 15 being opened or closed at different times can take place. This enables improved operation of the exhaust gas turbocharger 2 in connection with the internal combustion engine 7 to be implemented, since between what is known as dynamic charging, which is characterized by an open overflow opening 10 in the case of a dual or multiple-flow exhaust gas turbocharger 2, and what is known as pulse charging, which is characterized by distinguishes a closed overflow opening 10, can be further differentiated. Thus, the exhaust gas turbocharger 2 and the internal combustion engine 7 can be operated at higher efficiencies.

Reference List

1

exhaust routing section

2

exhaust gas turbocharger

3

entry channel

4

First spiral canal

5

Second spiral canal

6

exhaust manifold

7

internal combustion engine

8th

valve device

9

First valve body

10

overflow opening

11

valve system

12

valve lever arm

13

valve arm

14

bypass channel

15

flow opening

16

head Start

17

contour

18

moving device

19

lever end

20

pivot axis

21

adjusting shaft

22

guide hole

23

inner space

24

floor

25

First longitudinal valve axis

26

contact surface

27

valve seat

28

intake opening

29

opening longitudinal axis

30

Second valve body

31

arm longitudinal axis

32

end

33

fuse element

34

First movement gap

35

Second movement gap

36

valve lever arm section

37

guide sleeve

38

Second longitudinal valve axis

39

First distance

40

second distance

41

Third distance

42

valve face

43

ring surface

44

cover disc

45

valve lever arm surface

46

section area

47

biasing element

K

force flow line

L

length

R1

First Radius

R2

second radius

T

partition wall

QUOTES INCLUDED IN DESCRIPTION

This list of the documents cited 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.

Patent Literature Cited

• DE 102012015536 B2 [0004]
• WO 2017/108160 A1 [0005]

Claims (13)

Valve device of an exhaust gas routing section of an exhaust gas turbocharger, with a valve system (11) comprising a first valve body (9) for opening or closing an overflow opening (10) of the exhaust gas routing section (1) formed between a first spiral channel (4) and a second spiral channel (5) and a second valve body (30) for opening or closing a flow opening (15) of a bypass channel (14) of the exhaust gas routing section (1), wherein the valve system (11) is accommodated on a valve lever arm (12) of the valve device (8), and wherein the valve lever arm ( 12) can be moved with the aid of a movement device (18) of the valve device (8), characterized in that the first valve body (9) is designed to be movable relative to the second valve body (30). valve device claim 1 , characterized in that the first valve body (9) relative to the valve lever arm (12) is immovably received on this. valve device claim 1 or 2 , characterized in that the first valve body (9) has a valve arm (13) which is connected to the valve lever arm (12), and wherein the second valve body (30) is formed to encompass the valve arm (13). valve device claim 3 , characterized in that the valve arm (13) is immovably connected to the first valve body (9). Valve device according to one of the preceding claims, characterized in that a first longitudinal valve axis (25) of the first valve body (9) and a second longitudinal valve axis (38) of the second valve body (30) are coaxial. Valve device according to one of the preceding claims, characterized in that the first valve body (9) has a projection (16) which is convex in relation to the second valve body (30). Valve device according to one of the preceding claims, characterized in that the second valve body (30) is designed to at least partially encompass the first valve body (9) and vice versa. Valve device according to one of the preceding claims, characterized in that the valve lever arm (12) is arranged opposite the second valve body (30) and is designed to be in contact with it. valve device claim 8 , characterized in that a contact-forming valve lever arm surface (45) of the valve lever arm (12) is complementary to an opposite section surface (46) of the second valve body (30) forming the contact. valve device claim 8 or 9 , characterized in that the valve lever arm (12) and the second valve body (30) are convexly curved in the area of contact in the direction of the first valve body (9). Valve device according to one of the preceding claims, characterized in that a prestressing element (47) is designed to secure the position of the second valve body (30) relative to the valve lever arm (12). valve device claim 11 , characterized in that the biasing element (47) is arranged between the second valve body (30) and the valve lever arm (12). Exhaust gas duct section of an exhaust gas turbocharger, comprising a first spiral duct (4), a second spiral duct (5) and a bypass duct (14), the bypass duct (14) being designed to bypass a turbine wheel rotatably accommodated in the exhaust gas duct section (1), and the bypass duct ( 14) has a throughflow opening (15), and an overflow opening (10) is provided between the first spiral duct (4) and the second spiral duct (5), which is used to cause exhaust gas from the first spiral duct (4) to flow over into the second spiral duct (5) and vice versa, and wherein a valve device (8) is assigned to the exhaust gas routing section (1), with the aid of which the overflow opening (10) and the throughflow opening (15) can be opened or closed, characterized in that for Reduction of wear the valve device (8) according to one of Claims 1 until 10 is trained.

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