EP4143443A1

EP4143443A1 - Exhaust gas turbocharger with a silencer

Info

Publication number: EP4143443A1
Application number: EP21720266.2A
Authority: EP
Inventors: Christoph Mathey; Carsten Spinder; Bernd Albiez; Detlef Behrendt
Original assignee: Turbo Systems Switzerland Ltd
Current assignee: Turbo Systems Switzerland Ltd
Priority date: 2020-04-29
Filing date: 2021-04-21
Publication date: 2023-03-08
Also published as: EP3904697A1; CN115735057A; US20230167832A1; KR20220164611A; JP2023523769A; WO2021219461A1

Abstract

The invention relates to an exhaust gas turbocharger (30) with a silencer. The silencer comprises a multiplicity of damping elements (41) which are arranged concentrically about a central axis (42) of the silencer and are spaced apart concentrically from one another, with the result that a flow duct (43) is formed in each case between adjacent damping elements. The flow duct (43) has an inlet (44) which is at a greater radial spacing from the central axis (42) than an outlet (45) of the flow duct (43).

Description

EXHAUST TURBOCHARGER WITH A SILENCER

TECHNICAL AREA

The invention relates to the field of exhaust gas turbochargers for supercharged internal combustion engines. In particular, the invention relates to a muffler for an exhaust gas turbocharger of an internal combustion engine. The invention also relates to an exhaust gas turbocharger with a silencer described in the present disclosure and an internal combustion engine with such an exhaust gas turbocharger.

TECHNICAL BACKGROUND

To increase the performance of an internal combustion engine, exhaust gas turbochargers are used as standard nowadays. An exhaust gas turbocharger typically comprises a turbine in the exhaust tract of the combustion engine and a compressor upstream of the combustion engine. The exhaust gases from the internal combustion engine are expanded in the turbine. The work gained in this way is transmitted to the compressor by means of a shaft, which compresses the air supplied to the internal combustion engine. By using the energy of the exhaust gases to compress the air supplied to the combustion process in the internal combustion engine, the combustion process and the efficiency of the internal combustion engine can be optimized.

During the operation of the exhaust gas turbocharger, sound waves typically arise predominantly in the compressor wheel, which are undesirably high: amplitudes that are released to the environment through the air intake duct. These Sound waves are therefore usually attenuated by means of a silencer, in particular a filter silencer.

Filter silencers are known from the prior art, which are typically used on the intake side of a compressor that compresses the combustion air and supplies it to an internal combustion engine. Such a compressor is driven by the exhaust gas turbine of an exhaust gas turbocharger.

Usually, the filter silencer are designed such that ambient air can be introduced through a filter arranged on the periphery of a filter silencer into an interior of the filter silencer equipped with damping elements, then flows past the damping elements, and thereby to the compressor wheel, from which sound waves counter to the air flow go out, is deflected by guide elements. The sound attenuation takes place dissipatively at the damping elements, in that the sound energy is converted directly into heat by porous or fibrous absorber materials from which the damping elements are essentially made up. The absorber materials are usually held in shape by an acoustically transparent shell and protected from the flow. This shell can consist entirely or partially of metallic materials.

It has been found that with the filter silencers known from the prior art, in which the suction lift is sucked in radially through an annular surface, as well as guided radially through curved inserts and then deflected axially to the outlet of the silencer, no optimal sound attenuation is achieved becomes, and undesirable flow and pressure losses occur.

It has also been found that undesirable flow and pressure losses occur in conventional filter silencers. SUMMARY OF THE INVENTION

The object of the present invention is to provide a silencer which is improved at least with regard to one of the above-mentioned disadvantages of the filter silencer known from the prior art Compared to the filter silencer known from the prior art, it has an improved design, in particular to minimize flow and pressure losses.

To achieve the above object, a muffler for an exhaust gas turbocharger is provided according to the independent claim. Further aspects, advantages and features of the present invention can be found in the dependent claims, the description and the accompanying figures.

According to one aspect of the invention, a muffler for an exhaust gas turbocharger is provided which comprises a plurality of damping elements which are arranged concentrically around a central axis of the muffler and are concentrically spaced from one another, so that a flow channel is formed between adjacent damping elements. The damping elements comprise a non-metallic material. In particular, the damping elements comprise one or more absorber materials made of a non-metallic material. Furthermore, the damping elements can comprise a shell made of a non-metallic material. The flow channel has an inflow opening which is at a greater radial distance from the central axis than an outflow opening of the flow channel

Thus, a silencer for an exhaust gas turbocharger is advantageously provided, which compared to the prior art known silencers is improved. In particular, the silencer according to the invention provides a silencer with which flow and pressure losses can be reduced. Thus, a muffler with improved damping properties can be provided.

According to a further aspect of the invention, an exhaust gas turbocharger is provided with a muffler according to one of the Ausftihrungsformen described herein, wherein the muffler is arranged on the intake side of a compressor, in particular a radial compressor, of the exhaust gas turbocharger. In particular, the silencer described herein is advantageously designed such that the silencer can be connected to a radially inner housing area of a compressor housing, the silencer in the assembled state being at least partially enclosed by a radially outer housing area of the compressor housing.

According to a further aspect of the invention, an internal combustion engine with an exhaust gas turbocharger described herein is provided. The exhaust gas turbocharger comprises a muffler according to the embodiment described herein, since the exhaust gas turbocharger is arranged on the intake side of a compressor, in particular a radial compressor an internal combustion engine can be connected.

BRIEF DESCRIPTION OF THE FIGURES

Furthermore, the invention will be explained with reference to embodiments shown in figures, from which further advantages and Variations result. Here shows

FIG. 1 shows a schematic sectional view of a muffler according to the embodiments described herein, which is arranged on an intake side of a compressor;

FIG. 2 shows a schematic axial front view of a silencer according to the embodiments described herein; and

FIG. 3 shows a schematic perspective view of an exhaust gas turbocharger with a silencer according to the embodiments described herein.

DETAILED DESCRIPTION OF THE FIGURES

With reference to Figure 1, a muffler 40 is described for an exhaust gas turbocharger according to the present disclosure. FIG. 1 shows a schematic sectional view of the muffler 40, which is arranged on an intake side of a compressor, in particular a radial compressor 20.

According to an: embodiment, which can be combined with other embodiments described herein, the muffler 40 comprises a plurality of damping elements 41. As shown by way of example in Figure 1, the damping elements 41 are arranged concentrically around a central axis 42 of the muffler. Furthermore, the damping elements 41 are concentrically spaced from one another. In other words, the damping elements 41 are angcordnct spaced from one another in the radial direction R. As is shown by way of example in FIG. 1, the damping elements 41 are designed and arranged in such a way that a respective flow channel 43 is formed between adjacent damping elements 41. The flow channel 43 has a Inflow opening 44 which has a greater radial distance from the central axis 42 than an outflow opening 45 of the flow channel 43. The damping elements 41 comprise a non-metallic material. In particular, the damping elements 41 can consist of a non-metallic material.

Accordingly, a silencer for an exhaust gas turbocharger is advantageously provided, which is improved over the silencers known from the prior art. In particular, the embodiments of the silencer described here can reduce flow and pressure losses. Furthermore, by using a non-metallic material, an inexpensive silencer can be provided. The use of a non-metallic material can also lead to improved sound absorption. In addition, the design of the silencer can be better adapted to the needs of the application. In particular, the silencer can be made smaller, which makes it more cost-effective.

According to one embodiment, which can be combined with other embodiments described herein, the non-metallic material comprises at least one material selected from the group consisting of: polymers, in particular inorganic polymers; polymer-based materials, in particular polymer-based composite materials; ceramic materials, in particular materials comprising ceramic hollow spheres; Fiberglass materials, in particular fiberglass-based absorber materials; Glass fiber materials comprising S1O2 silicate fibers; and foam glass materials. Thus, the damping elements 41 can consist of one or more of the non-metallic materials listed herein, or comprise one or more of the non-metallic materials listed herein.

As can be seen from Figure 1, the arrangement of the differs Flow channels of the silencer described herein from the flow channel arrangement of conventional silencers in that the flow channels of the silencer described herein are designed concentrically. In contrast to this, conventional mufflers for exhaust gas turbochargers are typically designed in such a way that the damping elements are arranged in the circumferential direction around a central axis, flow channels being formed between the damping elements so that their outflow openings are directed essentially perpendicular to the central axis. As shown in FIG. 1, the flow channels of the silencer described herein are designed in such a way that their outflow openings provide an outflow direction which has a radial and a positive axial flow component.

According to one embodiment, which can be combined with other embodiments described herein, the damping elements 41 are arranged in a funnel-like manner around the central axis 42, as is shown by way of example in FIG that the damping element has the shape of a truncated cone, the truncated cone having a central opening which extends from the truncated cone base surface to the truncated cone top surface and thereby tapers. The truncated cone outer surface can be curved. The radially outwardly pointing flow surfaces 48 damping elements shown in FIG. 1 are, for example, concave, curved jacket surfaces.

According to one embodiment, which can be combined with other embodiments described herein, the damping elements 41 are curved between an inflow end 41A and an outflow end 41B, so that the flow channel 43 is formed in such a way as to deflect the flow in the direction of Provide central axis 42. As is shown by way of example in FIG. 1, flow surfaces 48 of the damping elements 41 pointing radially outward typically have a concave curvature. Radially inwardly pointing flow surfaces 49 of the damping elements 41 typically have a convex curvature

In particular, the flow deflection provided by the flow channels can include a deflection of the flow by a deflection angle α of 5 ° <a <180 °, in particular 15 ° <a <180 °. In the present disclosure, the expression “deflection angle” can be understood to mean the angle which results between a main inflow direction of an inflow opening 44 of a flow channel 43 and a main outflow direction of an outflow opening 45 of the flow channel 43

As is shown by way of example in FIG. 1, the respective deflection angles of the respective flow channels in the radial direction R can increase. In other words, flow channels arranged radially further outwards typically provide a larger deflection angle than radially wider flow channels arranged inside.

According to one embodiment, which can be combined with other embodiments described herein, the flow channels (also referred to as link channels) are configured such that the flow rate is as constant as possible and no speed peaks occur. This is particularly advantageous since speed peaks are included in the pressure loss as a square, so that the silencer described here has a reduced pressure loss. A reduction in the pressure loss advantageously has a positive effect on the damping behavior of the silencer, so that the damping behavior of the silencer described herein can be improved. According to one embodiment, which can be combined with other embodiments described herein, the inflow-side ends 41A of the damping elements 41 lie on a surface A which is convexly curved in the axial direction x. For example, the convexly curved surface A can be a partially spherical or partially elliptical surface . Typically, a perforated plate 411 or a filter element is arranged on the convexly curved surface A, as is shown by way of example in FIG

According to one embodiment that can be combined with other embodiments described herein, the inflow opening 44 of the respective flow channels has a larger flow cross-section than the outflow opening 45 of the respective flow channels. As is shown by way of example in FIG. 2, the inflow opening 44 of the respective flow channels 43 can be designed in the manner of a ring around the central axis 42. Furthermore, a distance T between adjacent damping elements 41 is shown by way of example in FIG. 2. The distance T between adjacent damping elements 41 can increase, decrease or be constant in the radial direction R.

In this context, it should be noted that the outflow opening 45 of the respective flow channels 43 can also be designed in a ring-like manner around the central axis 42.

According to one embodiment, which can be combined with other embodiments described herein, the silencer further comprises a connecting structure 46 for connecting at least two adjacent damping elements 41. Typically, connecting structure 46 is designed to improve the stability of the silencer. The connecting structure 46 can be provided, for example, by webs between the damping elements. The connecting structure can comprise or be made of a non-metallic material consist of a non-metallic material. For example, the connecting structure 46 can have at least one non-metallic material selected from the group consisting of: polymers, in particular inorganic polymers; polymer-based materials, in particular polymer-based composite materials; ceramic materials, in particular materials comprising ceramic hollow spheres; Glass fiber materials, in particular absorbent materials based on glass fiber; Glass fiber materials comprising S1O2 silicate fibers; and foam glass materials. Thus, the connection structure 46 may be composed of one or more of the non-metallic materials listed herein, or comprise one or more of the non-metallic materials listed herein.

According to an embodiment that can be combined with other embodiments described herein, the muffler further comprises an outflow-side cylindrical

Damping structure 47. For example, the cylindrical damping structure 47 can be connected to an outflow-side end of the radially outermost damping element 412. The damping properties of the muffler can thus be additionally improved.

According to one embodiment which can be combined with other embodiments described herein, the damping structure 47 comprises a non-metallic material or consists of a non-metallic material. For example, the damping structure 47 can have at least one non-metallic material selected from the group consisting of: polymers, in particular inorganic polymers; polymer-based materials, in particular polymer-based composite materials; ceramic materials, in particular materials comprising ceramic hollow spheres; Fiberglass materials, in particular fiberglass-based absorber materials; Glass fiber materials including S1O2 Silicate Fesem; and foam glass materials, comprised or composed of. Thus, the damping structure 47 can consist of one or more of the non-metallic materials listed herein, or comprise one or more of the non-metallic materials listed herein.

According to one embodiment that can be combined with other embodiments described herein, the cylindrical damping structure 47 can have a connecting structure 471 for connecting the muffler to an intake side of a compressor housing 10 of an exhaust gas turbocharger 30. As shown in FIG. 1, the compressor housing 10 can be, for example, a compressor housing of a radial compressor 20. The connection structure 471 came to be designed as a connection flange.

According to one embodiment that can be combined with other embodiments described herein, the connecting structure 471 comprises a non-metallic material or consists of a non-metallic material. For example, the connecting structure 471 can have at least one non-metallic material selected from the group consisting of: polymers, in particular inorganic polymers; polymer-based materials, in particular polymer-based composite materials; ceramic materials, in particular materials comprising ceramic hollow spheres; Fiberglass materials, in particular fiberglass-based absorber materials; Glass fiber materials comprising S1O2 silicate fibers; and foam glass materials. Thus, the connection structure 471 may be composed of one or more of the non-metallic materials listed herein, or comprise one or more of the non-metallic materials listed herein.

With reference to FIG. 1, a compressor housing 10 of a centrifugal compressor 20 according to the present disclosure is explained in more detail described. According to one embodiment, which can be combined with other embodiments described herein, the compressor housing 10 comprises a radially inner housing area 10A, which forms an axial inflow channel 11 in an intake area of the radial compressor 20. Furthermore, the compressor housing 10 comprises a diffuser area 10B adjoining the radially inner housing area 10A. The diffuser region 10B is designed to deflect a radial flow after a compressor wheel 21 in an axial direction counter to an inflow direction 12 of the inflow channel 11. Furthermore, the compressor housing 10 comprises a radially outer housing area IOC adjoining the diffuser area 10B, which extends axially opposite to the direction of flow 12 and provides one or more charge air collecting spaces 13, 14 the non-metallic materials described here must be sound-absorbent.

As is shown by way of example in FIG. 1, the one or more charge air plenums 13, 14 typically each have a charge air outlet opening 19. The charge air outlet opening is typically designed to provide an outflow of the charge air in an outflow direction 23 which is transverse, in particular essentially is at right angles to the direction of inflow 12.

In the exemplary embodiment shown in FIG. 1, the radially outer housing area IOC comprises a first charge air collection space 13 and a second charge air collection space 14. The first charge air collection space 13 and the second charge air collection space 14 are each connected to the diffuser area 10B, so that a first charge air housing leg 10C1 and a second charge air housing leg 10C2 is provided. Typically, the radially outer housing area IOC has an axial expansion in the opposite direction to the direction of flow 12, which is greater than an axial expansion of the radially inner housing area 10A. The compressor housing is thus designed in such a way that the radially outer housing region IOC at least partially encloses an axial intermediate space 24. The axial gap 24, which typically lies between the first charge air housing limb 10C1 and the second charge shift housing limb 10C2, is shown in FIG. As is shown by way of example in FIG. 1, the cylindrical damping structure 47 can be fastened to the radially outer housing region IOC via a fastening element 472.

In other words, the axial space 24 can be used to supply air to the inflow channel 11 of the radial compressor. The air can be supplied via a supply line, which can be designed as a cylindrical damping structure 47, for example. Such a sound-absorbing intake section can advantageously be used in order to achieve a reduction in the sound pressure level at the intake opening of the centrifugal compressor. A silencer with lower sound absorption can thus be used, which in turn has advantages in terms of pressure loss. This thus leads to a further reduction in losses and can thus contribute to an improvement in the efficiency of a radial compressor.

According to one embodiment that can be combined with other embodiments described herein, at least one of the radially outer housing area 10C and the diffuser area 10B is designed with two shells, so that one for one Cooling medium through which space 15 can flow is provided. In particular, the radially outer housing area 10C is typically designed with two shells and the diffuser area 10B is at least partially or completely designed with two shells. For example, at least one, in particular both, of the radially outer housing area 10C and the diffuser area 10B can comprise an inner shell 16 and an outer shell 17 spaced apart from the inner shell by a distance D, as is shown by way of example in FIG

A compressor housing with integrated charge shift cooling can thus advantageously be provided.

Furthermore, at least one charge air cooler 18 can be provided in the one or more charge shift collecting spaces 13, 14, as is shown by way of example in FIG. 1.

According to an embodiment which can be combined with other embodiments described herein, the muffler 40 can further comprise a central elongated damping element 41Z. The central elongate damping element 41Z typically extends along the central axis and protrudes in the axial direction x beyond an outflow-side end of the radially outermost damping element 412. In particular, the central elongated damping element 41Z can be a dome-like damping element, as is shown by way of example in FIG. Typically, the central elongate damping element 41Z is arranged concentrically around the central axis 42 of the muffler. In this way, the damping properties of the silencer can be additionally improved.

As is shown by way of example in FIG. 1, a mounting structure 41R for mounting the central elongate damping element 41Z can also be provided. For example, the Support structure 41R include radial webs. Typically, the radial webs are connected at one end to the inner circumferential surface of the cylindrical damping structure and at an opposite end to the central elongated damping element 41Z. According to one example, the radial webs can have teardrop-shaped cross-sections.

With reference to Figure 3, an exhaust gas turbocharger 30 is described with a silencer 40 according to the present disclosure. According to one embodiment that can be combined with other embodiments described herein, the exhaust gas turbocharger 30 comprises a muffler 40 according to the embodiments described herein, the muffler 40 being arranged on the intake side of a compressor, in particular a radial compressor 20, of the exhaust gas turbocharger. As can be seen from FIG. 3 in combination with FIG. 1, the silencer 40 can be connected to a radially inner housing area 10A of a compressor housing 10 and at least partially enclosed by a radially outer housing area 10C of the compressor housing 10.

Typically, according to the embodiments described herein, the exhaust gas turbocharger 30 is connected to an internal combustion engine via one or more exhaust gas lines 32 and one or more charge air outlet openings 19 in a vertical or horizontal orientation. Thus, an internal combustion engine with an exhaust gas turbocharger described herein can advantageously be provided, which can be connected to an internal combustion engine via one or more exhaust gas lines and one or more charge air outlet openings in a vertical or horizontal orientation.

As can be seen from the embodiments described herein, a silencer is advantageously provided which is improved over the filter silencers known from the prior art. In particular, the silencer according to the invention provides a silencer with which flow and pressure losses can be reduced. In particular, the silencer according to the invention advantageously has a design and an arrangement of the damping elements with which pressure losses can be reduced when there is a flow through the silencer, which leads to improved damping properties.

REFERENCE LIST

10 compressor housing

10A radially inner housing area 10B difiusor area IOC radially outer housing area 10C1 first charge air housing leg

10C2 second charge air housing leg

11 inlet duct

12 direction of flow 13 first charge air collection chamber

14 second charge air plenum

15 space

16 inner shell

17 outer shell 18 intercooler

19 Charge air outlet opening

20 centrifugal compressors

21 Compressor wheel

23 Direction of outflow of charge air 24 axial gap

30 exhaust gas turbochargers

40 mufflers

41 damping elements

41A inflow end of the damping elements 41B outflow end of the damping elements

41Z central elongated damping element

41R Bearing structure to support the central elongated damping element 411 Perforated plate / filter element 412 radially outermost damping element 42 central axis

43 flow channel

44 Inlet opening

45 outflow port 46 connecting structure

47 cylindrical damping structure

471 connection structure

472 Fastening element for fastening the sound-absorbing element to the radially outer housing area 48 radially outwardly pointing flow surfaces

49 flow surfaces pointing radially inward

31 turbine

32 exhaust pipe

R radial direction x axial direction

T Distance between neighboring damping elements

D Distance between inner shell and outer shell

A convex curved surface

Claims

EXPECTATIONS

1. Exhaust gas turbocharger (30) with even muffler (40), de to de

The suction side is arranged erncs Vendichtes of the exhaust gas turbocharger, the sound fumes (40) comprising a plurality of damping elements (41) which are arranged concentrically around a central axis (42) of the muffler and are concentrically spaced from one another, so that a flow channel (43 ), wherein the damping elements (41) comprise a non-metallic material, and wherein the flow channel (43) has an inflow opening (44) which has a greater radial distance from the central axis (42) than an outflow opening (45) of the Flow channel (43).

2. The exhaust gas turbocharger (30) according to claim 1, wherein the damping elements (41) are arranged like a funnel around the central axis (42) hemm.

3. exhaust gas turbocharger (30) according to claim 1 or 2, wherein the

Bestdien damping elements (41) made of a non-metallic material.

4. exhaust gas turbocharger (30) according to any one of claims 1 to 3, wherein the non-metallic material at least eb material selected from the group consisting of: polymers, in particular inorganic polymers; polymer-based materials, in particular polymer-based composite materials; ceramic materials, in particular materials comprising ceramic hollow spheres; Glass fiber materials, in particular absorber materials based on glass fiber; Glass fiber materials comprising S1O2 silicate fibers; and foam glass materials.

5. exhaust gas turbocharger (30) according to any one of claims 1 to 4, wherein the Damping elements (41) are curved between an inflow-side end (41A) and an outflow-side end (41B) so that the flow channel (43) is designed to provide a flow deflection in the direction of the central axis (42), in particular where the flow deflection is a deflection of the Includes flow around a deflection angle α of 5 ° <α <180 °

6. The exhaust gas turbocharger (30) according to any one of claims 1 to 5, wherein radially outwardly projecting flow surfaces (48) of the damping elements (41) have a concave curvature, and wherein radially inwardly pointing flow surfaces (49) of the damping elements (41) a convex curvature exhibit.

7. Exhaust gas turbocharger (30) according to one of claims 1 to 4, wherein the inflow-side ends (41 A) of the damping elements (41) lie on a surface that is convexly curved in the axial direction, in particular on a partially spherical or partially elliptical surface.

8. Exhaust gas turbocharger (30) according to one of claims 1 to 5, wherein the inflow opening (44) has a larger flow cross-section than the outflow opening (45), in particular wherein the inflow opening (44) and / or the outflow opening (45) of the flow channel (43) ) are formed in a ring around the central axis (42).

9. The exhaust gas turbocharger (30) according to any one of claims 1 to 8, further comprising a connecting structure (46) for connecting at least two adjacent damping elements (41), in particular wherein the connecting structure (46) comprises a non-metallic material or not -metallic material, wherein the non-metallic material consists of at least one material selected from the group made of: polymers, in particular inorganic polymers; polymer-based materials, in particular polymer-based composite materials; ceramic materials, in particular materials comprising ceramic hollow spheres; Fiberglass materials, in particular fiberglass-based absorber materials; Glass fiber materials comprising S1O2 silicate fibers; and foam glass materials.

10. The exhaust gas turbocharger (30) according to one of claims 1 to 8, further comprising an outflow-side cylindrical damping structure (47), in particular wherein the damping structure (47) comprises a non-metallic material or consists of a non-metallic material, the non-metallic material at least one material selected from the group consisting of: polymers, in particular inorganic polymers; polymer-based materials, in particular polymer-based composite materials; ceramic materials, in particular materials comprising ceramic hollow spheres; Glass fiber materials, in particular absorber materials based on glass fiber; Glass fiber materials comprising S1O2 silicate fibers; and foam glass materials, includes ..

11. The exhaust gas turbocharger (30) according to claim 10, wherein the cylindrical damping structure (47) is connected to a discharge side end of the radially outermost damping element

12. The exhaust gas turbocharger (30) according to any one of claims 9 or 10, wherein the cylindrical damping structure (47) has a connection structure (471), in particular a connecting flange, for connecting the muffler to an intake side of a compressor housing, in particular a radial compressor (20), of an exhaust gas turbocharger

13. exhaust gas turbocharger (30) according to one of claims 1 to 11, further comprising a central elongated damping element (41Z), in particular a dome-like damping element, which extends along the central axis (42) and protrudes in the axial direction beyond an outflow-side end of the radially outermost damping element, in particular the central elongated damping element (41 Z) being a non-metallic Material comprises or consists of a non-metallic material, the non-metallic material at least one material selected from the group consisting of: polymers, in particular inorganic polymers; polymer-based materials, in particular polymer-based composite materials; ceramic materials, in particular materials comprising ceramic hollow spheres; Fiberglass materials, in particular fiberglass-based absorbent materials; Glass fiber materials comprising SiO2 silicate fibers; and foam glass materials.

14. exhaust gas turbocharger (30) according to any one of claims 1 to 12, wherein the

The compressor is a radial compressor (20), and the silencer (40) is connected to a radially inner housing area (10A) of a compressor housing (10) and is at least partially enclosed by a radially outer housing area (IOC) of the compressor housing (10) is, in particular wherein individual parts of the compressor housing, in particular a diffuser area (10B) of the compressor housing (10) are lined with sound-absorbing material, in particular sound-absorbing non-metallic material.

15. Internal combustion engine with an exhaust gas turbocharger (30) according to claim 14, in particular wherein the exhaust gas turbocharger is connected to an internal combustion engine via one or more exhaust pipes (32) and one or more charge air outlet openings (19) in a vertical or horizontal orientation.