WO2013152793A1

WO2013152793A1 - Reflection silencer

Info

Publication number: WO2013152793A1
Application number: PCT/EP2012/056684
Authority: WO
Inventors: Wolfgang Freund; Sven KÖNIG
Original assignee: Siemens Aktiengesellschaft
Priority date: 2012-04-12
Filing date: 2012-04-12
Publication date: 2013-10-17

Abstract

The invention relates to a reflection silencer for a turbocompressor. The reflection silencer (1) has a tubular or (circularly) annular reflection body (10), through which a flow medium (2) flows axially (5) in a flow direction (3). In the reflection body (10), cavities (20) which are arranged in each case in the circumferential direction of the reflection body (10) are formed in a plurality of planes (11) which are radial with respect to the axial flow direction (3, 5).

Description

description

Reflection silencer The invention relates to a reflection silencer, in particular for a turbocompressor.

Turbo compressors, i. in general compressor or

Fluid compressing devices are used in various industries for various applications involving compression of fluids, in particular

(Process) gases, goes. Well-known examples of this are

Turbo compressors in mobile industrial applications, such as in exhaust gas turbochargers or in jet engines, or in stationary industrial applications, such as stationary steam or gas turbines, or process gas compressors.

In such a - in his way of working continuously - turbo compressor is the pressure increase

(Compression) of the fluid caused by the fact that the angular momentum of the fluid is increased from inlet to outlet by the rotation of the blades. Here, i. in such a

Compressor stage, increase pressure and temperature of the fluid, while the relative (flow) speed of the fluid in the impeller decreases. In order to achieve the highest possible pressure increase or compression of the fluid, a plurality of such compressor stages can be connected in series.

As types of turbocompressors, a distinction is made between radial and axial compressors.

In the axial compressor, the fluid to be compressed, for example, a process gas flows mainly in a direction parallel to the axis (axial direction) through the compressor. In the centrifugal compressor, the gas flows axially into the impeller of the compressor stage and then becomes outwardly (radially,

Radial direction) deflected. With multistage centrifugal compressors, this means there is a flow deflection behind each stage necessary. Also, "mixed" versions of compressors, such as semi-axial compressors, are known.

Furthermore, it is known that such turbocompressors cause relatively high sound emissions or noise levels, which represent a (noise) impairment of an environment of the turbocompressor. In addition, these sound emissions can trigger vibrations and structure-related malfunctions.

For example, dominant sound sources in one

Turbocompressor typically generated at the location of the impeller and the diffuser inlet or any Diffusorschaufein due to a high speed of the fluids flowing through these regions fluids.

In particular, it is known here that turbocompressors at an exit from the turbocompressor, i. one

Pressure side, or at an entrance, i. one

Produce suction side, complex three-dimensional, rotating and / or pulsating pressure fields or sound fields whose attenuation is technically difficult.

On the basis of this, efficient soundproofing measures are necessary for such sound-emitting turbocompressors.

Various noise emission limiting measures, such as

Housing or enclosures are known. These

Noise reduction techniques can be relatively expensive, especially when offered as a "later" add-on product.

Furthermore, silencers for limiting

Noise emissions in (turbo) compressors known.

Mufflers in general are devices for

Reduction of noise emissions. Different types of silencers are distinguished, which produced one due to different mechanisms of action Reduce sound power. For example, a distinction is made between absorption and reflection silencers.

Reduce sound power. For example, a distinction is made between absorption and reflection silencers.

An absorption silencer contains porous (absorbent) material, typically rock wool, glass wool or glass fiber, which partially absorbs sound energy, that is, converts it to heat. By absorption, in the muffler

mainly upper frequencies of the sound medium are damped.

Absorption mufflers have the disadvantage that they are usually unsuitable for high pressures, as - combined with the high pressures - high energy inputs to the

Absorption material act or high heat inputs are absorbed by the absorbent material, resulting in damage to the porous material, such as a resolution of the

Absorption material, can lead.

Reflection silencer, which is the principle of a

Use sound reflection, this usually contain several cavities or chambers, where the sound medium

passes by, where it comes to reflections. When passing several passages of interiors of the chambers through the

Sound medium it comes to a reduction of

Sound pressure peaks of different frequency. These reflections are - constructively - by baffles,

Cross-sectional extensions and constrictions generated. By reflection, any frequencies of the sound medium can be damped in the muffler.

From EP 1 291 570 A2 is a modular structure

Reflection silencer known for a turbocharger.

This reflection muffler has one of a

Flow medium in a flow direction axially

flowed through, tubular reflection body on wherein a plurality of disks are arranged in the axial direction, thereby forming circumferential reflection cavities in the disks.

Thus, the invention has the object, a

Specify silencer, which improves the disadvantages of the prior art, easy to implement and also easy - in a sound-emitting system or device - is installed and which is particularly suitable for attenuation of sound emissions in a turbocompressor.

The object is achieved by the reflection muffler with the features according to the independent claim.

This reflection muffler has one of a

Flow medium in a flow direction axially

flowed through, tubular or (circular) annular

Reflection body on. In the reflection body, cavities arranged in the circumferential direction of the reflection body (reflection depressions or also cavities hereinafter) are formed in a plurality of radial planes arranged in the circumferential direction of the reflection body relative to the axial flow direction.

Preferred developments of the invention will become apparent from the dependent claims.

Such a reflection depression or such a cavity whose geometry - via a geometrically caused

Resonant frequency of the reflection well - a

fixes mainly to be damped frequency of the flow medium can, as a bore, in particular in the radial direction of the tubular reflection body and with in

Reflecting body varying (hole) depth, or be designed as (radial) Schiitz.

It is also possible, this cavity as a chamber or as a combination of connected chambers, in particular as a chamber - with varying in the reflection body three-dimensional

Extension - with a radial feed channel and / or with a specially trained, in particular narrow, (chamber) opening to train.

In particular, it can be provided here that the

Reflection recesses or cavities form a lambda / 2 resonator and / or a lambda / 4 resonator and / or a Helmholtz resonator.

Reflection recesses or cavities according to the lambda / 2 principle or according to the lambda / 4 principle are based on a reflection of sound waves at openings of the - in particular chamber-like - reflection recesses.

Within these cavities there are certain frequencies

- the resonance frequencies - to standing waves with a pressure node in the vicinity of the openings of

Reflection wells, being in the respective

Reflection pit - in the case of a lambda / 2 resonator

approximately half a wavelength or, in the case of a lambda / 4 resonator, approximately one-quarter wavelength at the resonant frequency of the respective reflection depression. As a result, the sound waves whose frequency corresponds to the resonant frequency of the reflection well, thrown back and attenuated.

Reflection recesses or cavities according to the Helmholtz principle are realized by a special one

chamber-like reflection recess with one or more narrow opening to the flow channel. By a

Elasticity of the fluid volume in the interior of the chamber-like reflection recess in combination with an inertial mass of the fluid located in the opening of the chamber-like reflection depression results in a mechanical mass-spring system with a pronounced

Eigenresonance or resonance frequency. This will be the

Sound waves whose frequency is the resonance frequency of

Reflection well corresponds, thrown back and

steamed. In order to achieve efficient damping, the cavities arranged in an axial plane (or also only briefly in the following) can be arranged uniformly over the circumference of the reflection body. A division of

Reflection recesses in an axial plane may depend on a number of over the circumference of the

Reflection body to be distributed in the axial plane

Reflection recesses and / or of a geometry of the reflection recesses and / or of a cross section or a cross-sectional size of the reflection body in the

Axial plane.

For example, it is possible to have at least 16 or 20 or 24

Reflection wells, especially 28 or more

Reflection pits, in an axial plane of the

Provide reflection body. Depending on the frequency to be damped or the size of the chambers but can also significantly less

Chambers such as 2 to 10 chambers or 4 to 8

Chambers to be provided.

Furthermore, it can be provided that each arranged in an axial plane cavities for damping

at least one particular frequency or more

Frequencies, for example two or three or four

certain frequencies are designed. This can be realized in that in each case a certain number of lying in the axial plane cavities have the same geometry - and thus the same resonant frequency and frequency to be damped.

Preferably - due to a high efficiency of

Damping effect - but can be provided that all

Cavities or reflection depressions in an axial plane have the same geometry and are thus designed for the attenuation of a specific frequency.

If so provided for each of the reflection depressions having axial planes, in which case each axial plane for the Damping a particular frequency can be interpreted, can be a broadband attenuation of the introduced

Sound emission can be achieved. In a preferred embodiment, the reflection body made of metal, in particular steel, formed what

Especially at high pressures of the flow medium and the process gas is advantageous. Furthermore, it can be provided that the reflection body is formed in one piece, for example as a solid component, in particular made of steel.

It can also be provided that the reflection body

is formed in several pieces. Such a configuration of the reflection body may preferably have a plurality of disc-shaped and / or annular elements, wherein such a disc and / or such a ring each one of

Axial levels of the reflection body with the local in

Circumferentially arranged the reflection body

Cavities corresponds.

That is, on such a disc-shaped and / or annular element which are assigned to this axial plane

Reflection wells arranged.

In a preferred embodiment, the

Reflection body in each case a plurality of first and second discs, which are arranged alternately. These first disks can be so-called resonator rings or resonator disks; These second discs can be called

Intermediate rings or intermediate discs (also sealing washers) represent. It is particularly advantageous if such a first disk or such a resonator disk has sectors which are distributed over the disk circumference, in particular evenly distributed sectors separated by radial webs. Corresponding can be provided for such a second disc or for such a washer. That is, even one

Washer has over the disk circumference, in particular evenly, distributed, separated by radial webs sectors.

Furthermore, it can be provided that such a first and / or second disc have or have a central bore, in particular for receiving a substantially cylindrical carrier. As a result, a centering of the discs - to form the reflection body - simplified.

It can also be provided that such a first and / or second disc have or have one or more centering bores, whereby they can be centered relative to one another and / or with respect to a housing and / or a sheathing. If such first and second discs - each arranged alternately and centered and aligned, i. the sectors of the disks form a continuous axial

Flow channel from - lined up in a sandwich-like composite and thereby formed the tubular reflection body, this can be a highly efficient reflection muffler can be realized. In particular, it is possible with such a reflection muffler to reduce complex three-dimensional, rotating and / or pulsating pressure fields or sound fields to fields with approximately plane waves, which are easier and more efficient to damp.

The efficiency of such a reflection body can be further increased if over the disk circumference of a

Resonator disc, in particular evenly, distributed, in the radial direction inwardly open first recesses,

in particular chamber-shaped cavities, and / or over the

Disc circumference of the resonator discs, in particular

even, distributed, radially outward open second recesses, in particular chamber-shaped cavities, are arranged.

The openings of the first and the second recesses or cavities can be oriented toward one another in the radial direction

In a further embodiment it can be provided that in a composite of a first disc and a second disc (axially) adjacent to the first disc

Disc a part of a second disc a recess, in particular a chamber-shaped cavity, the first

Disc axially limited. This composite can with a

be complemented accordingly further second disc such that axially between the two second discs, the first disc is arranged, wherein the recess of the first

Disk axially bounded on both sides by the second disks. Preferably, it can further be provided that the

Reflection body has a substantially cylindrical core for receiving, in particular to a centered recording, the first and / or second discs. For this purpose, the first and / or second discs may each have center holes, by means of which the discs on the core

can be arranged. A stability of

Reflection body can be increased thereby; An assembly of the reflection body can be simplified. Furthermore, this reduces a flow cross-section or

Flow diameter of the reflection body, resulting in

Improvement of the sound field and thus contributes to the increase in efficiency of the reflection silencer.

It can also be provided that the reflection muffler has at least two connection elements, between which the reflection body is held, in particular is kept clamped. Simplified, the tension can be realized by a screw connection of the two connection elements.

Such an arrangement or such a system has in particular the advantage that it or it is easy and quick to assemble and disassemble, as well as that used between the connection elements

Reflection body is easy and quick to replace. Also, such a system proves to be highly flexible, since by different designed reflection body - in the sense of various uses - the reflection muffler can be easily adapted to different, predetermined conditions of use and / or changed.

For this purpose, it may be expedient that the connection elements each have a flange with at least one bore, with the use of which the screw is realized (flanged reflection body).

Especially with first and second discs

trained reflection bodies, it may also be appropriate that the discs also with bottle and / or

Holes are formed, via which a screw connection - in particular centered clamping - or clamping can be realized.

Preferably, it is also possible that the reflection body, in particular disks of the reflection body, is or are received in a tubular casing, in particular in a liner. Among other things, here can be one

Assembly of the reflection body can be simplified.

In a further preferred embodiment, it is provided that the reflection body has at least five axial planes, in particular at least 10, 12 or 14 axial planes or even more axial planes, each with reflection recesses arranged in the circumferential direction. This can be preferably realized by a corresponding number of slices. The reflection recesses of an axial plane can be formed substantially identical, so that the respective axial plane (or disc) is designed for the damping of a (completely) certain frequency.

Are the reflection pits different

Axial planes each designed differently, so can thereby achieve a broadband attenuation of noise emissions of the turbocompressor.

In a further development it can be provided that the

Cavities are formed such that such a broadband attenuation of the acoustic emissions over a range of Flügelradumlauffrequenz ("blade passing frequency") of the turbocompressor extends to at least a second harmonic and / or third harmonic and / or fourth harmonic to the Flügelradumlauffrequenz.

It can also be provided that the cavities in such a way

are designed that damping for a large

Speed range of e.g. 50% to 105% of a rated speed of the turbocompressor is designed.

For example, a frequency band to be attenuated by

700 hertz - 2000 hertz, 700 hertz - 4000 hertz or 700 hertz

- 6000 Hertz be realized.

Furthermore, it can be provided that the flow medium

- compressed or compressed process gas,

for example, with a pressure of at least 20 bar or at least 50 bar or at least 75 bar or of

at least 100 bar, is. The turbo compressor can

Axial turbo-compressor or a radial turbo-compressor. Preferably, the reflection muffler is directly on a pressure side of the turbocompressor, for example at a local pressure port at the outlet or outlet of the turbocompressor, or directly to a suction side of the Turbo compressor, for example, at a local suction at the entrance or entry of the turbocompressor arranged. Alternatively, however, the reflection muffler can also be arranged further downstream or upstream-with regard to the turbocompressor-in a pipeline system.

In particular, the tubular formation of the

Reflection body and thus the reflection silencer allows an easy-to-implement installation at said locations, i. to the nozzle of the turbo compressor or in piping of the piping system.

The installation of the reflection silencer directly on

Turbo compressor proves to be advantageous because no further soundproofing measures downstream of the flow medium or for local process gas lines must be more necessary.

Furthermore, it proves in the invention of great advantage that - with appropriately designed reflection depressions in the multiple axial planes - a broadband attenuation of the introduced sound can be achieved.

Furthermore, it proves to be advantageous in the invention that the reflection muffler according to the invention in a high-pressure region, such as turbocompressors and turbocompressors produced and in subsequent

Process gas lines fed sound emissions,

can be used.

In figures, embodiments of the invention

illustrated, which are explained in more detail below.

Show it

Figure 1 Sketch of a sectional view of a

Reflection silencer in sandwich construction individual resonator discs with intermediate discs (intermediate seal);

Figure 2 is a sketch of a sectional view of a

Flanged reflection muffler in

Solid construction;

3 shows a sketch of a sectional view of a

Flanged reflection silencer from individual resonator discs with washers with inner part and pressure-bearing liner;

Figure 4a, b sketches and views of a Resonatorscheibe;

Figure 5a, b sketches and views of a washer

(Intermediate seal);

FIG. 6 Schematic diagram of a reflection body of a

Reflection muffler based on the principle of a Labda / 4 resonator;

Figure 7 schematic diagram of a reflection body of a

Reflection silencer based on the principle of a Lambda / 2 resonator;

8 shows a schematic diagram of a reflection body of a

Reflection silencer based on the principle of a Helmholtz resonator.

Exemplary embodiments: reflection muffler in

Pipelines in turbocompressors

The generated by a turbocompressor 100 and in

subsequent process gas lines 103 via the process gas fed sound emissions are subject to high

Operating pressures, for example, about 100 bar. These require appropriate soundproofing measures, such as a

Reflection silencer 1.

To avoid complex soundproofing measures,

In particular for the entire pipeline system 103 of the turbocompressor 100, a reflection muffler 1 is connected directly to an outlet 101 or to the pressure side 101 of the turbocompressor 100, i. at a pressure outlet there, and thus directly at the entrance of the subsequent

Process gas line 103 attached. Further

Noise protection measures can be omitted hereby.

In Figures 1 to 3 are fundamental constructive

Embodiments of such usable

Reflection silencer 1 shown. Figures 4 and 5 show details of such reflection muffler 1, in particular parts of the internal structure. FIGS. 6 to 8 illustrate various reflection or resonator principles in connection with their design

Implementation of the reflection silencers 1.

Fig.l shows a reflection muffler 1 in

Sandwich construction comprising a plurality of discs 30, 31 having reflection body 10th

The composite of the discs 30, 31 is held axially on both sides by a respective connecting element 50, 51 braced. For this purpose, the connection elements 50, 51 each have one

Flange 53 with holes 54 through which the composite is clamped by means of screw 52.

The disk composite forming the reflection body 10 has alternating resonator disks 30 and, as compared to the resonator disks 30, substantially narrower washers or intermediate seals 31, wherein as illustrated a total of seven resonator disks 30 and eight intermediate seals 31 are used alternately. Each resonator disc 30 as well as the two

Connection elements 50, 51 are preferably made of steel and have a central, axial central bore 35, which has an open to both axial sides and the process gas 2 of

Turbo compressor axially, flowing in the flow direction 3 flow channel 6 form.

Furthermore, each resonator disk 30 - in this case 28 - uniformly distributed over the circumference 12, radially inwardly or to the central bore 35 toward open reflection recesses 20.

Each intermediate seal 31 has - apart from the

Center hole 35 - further solid material on. at

Arrangement of a resonator 30 between each two such intermediate seals 31 are the

Reflection recesses 20 a Resonatorscheibe 30 axially on both sides by (full) material of the intermediate seals 31 limited, resulting - from the reflection wells 20 - corresponding only to the flow channel 6 through open

form (sound-absorbing) chambers 20.

About the geometric design of the reflection pits 20, the main to be damped frequency is set. In this case, all reflection recesses 20 a

Resonator 30 has the same geometry, so that this resonator 30 is designed for a frequency to be damped.

The more different rows or resonator disks 30 with different reflection recesses 20 are present, the broader the sound emissions of the

Turbo compressor 1 are damped.

2 shows a flanged reflection muffler 1 in solid construction of metal comprising a one-piece tubular reflection body 10th The one-piece tubular reflection body 10 is also held axially on both sides by a respective connection element 50, 51. For this purpose, the connecting elements 50, 51 each have a flange 53 with holes 54, via which the

Reflection body 10 on both sides by means of axial

Screws 52 is held.

The reflection body 10 as well as the two

Connection elements 50, 51 have a central, axial

Central bore 35, which form an open axially to both axial sides and the process gas 2 of the turbocompressor, flowed through in the flow direction 3 flow channel 6.

Next, the reflection body 10 in four

Axialbenen 11 evenly distributed over the circumference 12, radially inwardly or to the central bore 35 toward open chamber-like (sound-absorbing) reflection depressions 20.

About the geometric design of the reflection pits 20, the main to be damped frequency is set. In this case, all reflection depressions 20 of an axial plane 11 have the same geometry, so that this axial plane 11 is designed for a frequency to be damped.

The more different axial planes 11 with different reflection recesses 20, the more

wideband, the sound emissions of the

Turbo compressor 1 are damped.

3 shows a flanged reflection muffler 1 with inner part 40 and pressure-bearing liner 60. This reflection muffler 1 has - similar to

Reflection silencer according to Figure 1 - also one

Reflection body 10 of a composite of alternating

Resonator discs 30 and - compared to the Resonator discs 30 much narrower - intermediate discs or intermediate seals 31 on. For example, 16 resonator disks 30 and 17 intermediate disks 31 are here

arranged, which are shown in Figures 4a, b and 5a, b in detail.

The resonator discs 30 as well as the intermediate seals each have a central, axial center bore 35 and from there radially outward, over the

Disk circumference evenly distributed, forming sectors 34, seven webs 33 on. With a corresponding centered axial arrangement and orientation of the disks 30, 31, this results in the formation of seven sectoral flow channels 6 for the process gas.

The arrangement and centering of the discs 30, 31 on the one hand by an inner, cylindrical support 40, the inner part 40, on which the Resonatorscheiben 30 and the intermediate seals 31 sit with their central bore 35 in their mutual arrangement, and on the other hand by an outer, tubular sheath 60, the liner, in which the discs 30, 31 and held by flanges 53 - together with corresponding axial end pieces forming connecting elements 50, 51 - and bores 36 are held and screwed 52.

When using such an inner core 40 and the sectoral distribution 34 of the flow cross section through the sectoral design 34 of the discs 30, 31 of the

Flow flow through guidance and distribution is steady.

In particular, this is possible, the complex

three-dimensional, rotating and / or pulsating pressure field or sound field of the turbocompressor 100 to reduce fields with approximately plane waves. Both contribute to an improvement of the sound field and thus to

Increase in efficiency of the reflection muffler 1. Further, each resonator disc 30 - in this case 28 - evenly distributed over the circumference 12, radially inward or to the respective sector 34 open towards (outer)

Reflection wells 20 on. Also, each assigns

Resonator 30 - in this case 7 - evenly distributed over the circumference 12 of the central bore 35, radially outward or also to the respective sector 34 open towards further (inner) reflection depressions 20. As a result, if there are seven sectors 34 per resonator disk 30, each sector 34 has four "outer" and one "inner" reflection indentations 20, each of which in the

Essentially cuboid shaped as well as on her

Opening 24 to the respective sector 34 has an inlet 25 forming a constriction.

Each intermediate seal 31 has - apart from the

Center hole 35 and the seven sectors 34 - further on solid material. When a resonator disk 30 is arranged between each two such intermediate seals 31, the outer and inner reflection depressions 20 of a resonator disk 30 are bounded on both sides by (full) material of the intermediate seals 31, resulting in - corresponding to the respective flow channel 6 - out of the reflection depressions 20 (FIG. sound-absorbing) chambers 20 form.

About the geometric design of the reflective recesses 20, such as their volume, shape, width or

Depth, becomes the main frequency to be damped

established. In this case, all reflection depressions 20 of a resonator disk 30 have the same geometry, so that this resonator disk 30 is designed for a frequency to be damped.

Turbo compressor 1 are damped.

FIGS. 6 to 8 illustrate different reflection or resonator principles in connection with their structural conversions in the reflection sound absorbers 1.

6 shows a schematic diagram of a lambda / 4 resonator; FIG. 7 shows a schematic diagram of a lambda / 2 resonator.

Reflection recesses 20 or cavities 20 after the

Lambda / 2 - principle or according to the Lambda / 4 - principle are based on a reflection of sound waves at openings 24 of - in particular chamber-like - reflection recesses 20, which is usually a narrow opening 24, 25 to the outside, which also as a channel 21

may be formed.

Within these reflection recesses 20, for certain frequencies - the resonance frequencies - standing waves occur with a pressure node in the vicinity of the openings 24 of the reflection recesses 20, wherein in the respective reflection recess 20 - in the case of a lambda / 2 resonator - an approximately half wavelength or - in the case of a lambda / 4 - resonator, an approximately quarter wavelength at the resonant frequency of the respective

Reflection pit 20 forms. This will be the

Sound waves whose frequency is the resonance frequency of

Reflection pit 20 corresponds, thrown back and muted.

FIG. 6 shows a special design for a lambda / 4 resonator, according to which the signals associated with a frequency

Single chambers 20 (an axial plane 11 of the

Reflection muffler 1 and the reflection body 10 - in total 9 illustrated axial planes 11) are each arranged as a bore of different radial length over the circumference 12. FIG. 7 shows, for a lambda / 2 resonator, like the individual chambers 20 associated with a frequency (an axial plane 11 of the reflection silencer 1 or of the reflection body 10 - with a total of 9 axial planes 11 shown) via a respective channel 21 with the flow cross section 6

are connected.

8 shows a schematic diagram of a Helmholtz resonator.

Reflection recesses 20 or cavities 20 after the

Helmholtz - principle are realized by an im

Special chamber-like reflection recess 20 (main volume) with a narrow opening 24, 25 to the outside, which may also be formed as a channel 21.

Fig. 8 shows such large main volumes 20 in several, i. Nine, axial planes 11 of the reflection muffler 1 or reflection body 10, which via such channels 21st

different length are connected to the flow cross-section 6.

By an elasticity of the fluid volume in the interior of the chamber-like reflection recess 20 in FIG

Combined with an inertial mass of the fluid contained in the opening 24, 25 of the chamber-like reflection recess 20, a mechanical mass-spring system with a pronounced self-resonance or

Resonant frequency.

As a result, the sound waves whose frequency of the

Resonant frequency of the reflective recess 20 corresponds, reflected and damped.

Claims

claims

1. Reflection silencer (1), in particular for a

Turbo-compressor (100) with a tubular reflection body (10) through which a flow medium (2) flows axially (5) in a flow direction (3),

wherein in the reflection body (10) in each case a plurality of first and second disks each alternately in the axial

Direction (5) are arranged and the first discs (30) each distributed over the disc periphery (12), in

Radial direction (4) have inwardly open first recesses (22),

characterized in that

in a composite of a first disc (30) and the first disc (30) in the axial direction (5)

Parts of the second disks (31) arranged adjacent to one another in the axial direction (5) are adjacent to the second disks (31) arranged adjacent to one another

Recesses (22) of the first disc (30) axially (5)

limit,

in the reflection body (10) in a plurality of planes (11) which are radial with respect to the axial flow direction (3, 5) in the circumferential direction (12) of the reflection body (10)

arranged cavities (20) through the limited recesses (22) are formed.

2. reflection silencer (1) according to at least one of the preceding claims,

characterized in that

the cavities (20) as bores and / or chambers,

in particular as chambers with radial feed channels (21) are formed.

3. reflection silencer (1) according to at least one of the preceding claims,

characterized in that

each arranged in an axial plane (11) cavities (20) for attenuation of at least one specific frequency, in particular for the attenuation of a specific frequency, are designed.

4. reflection silencer (1) according to at least one of the preceding claims,

characterized in that

the first discs (30) in each case over the disc periphery (12), in particular evenly distributed, by radial webs (33) separated sectors (34) and / or a central bore (35), in particular for receiving a in

Substantially cylindrical support (40), and / or

at least one centering bore (36) and / or over the

Disk periphery (12), in particular uniformly distributed, in the radial direction (4) outwardly open second recesses (23), in particular chamber-shaped cavities, in particular the openings (24) of the first and second recesses (22, 23) in each other Radial direction (4) facing oriented.

5. reflection silencer (1) according to at least one of the preceding claims,

characterized in that

the second discs (31) in each case over the disc periphery (12), in particular evenly distributed, by radial webs (33) separated sectors (34) and / or a central bore (35), in particular for receiving a in

Substantially cylindrical support (40), and / or

have at least one center hole (36).

6. reflection silencer (1) according to at least one of the preceding claims,

characterized in that

the reflection body (10) is a substantially

cylindrical core (40) for receiving the first and / or second discs (30, 31).

7. reflection silencer (1) according to at least one of the preceding claims,

characterized in that

the reflection muffler (1) at least two

Connection elements (50, 51), between which the reflection body (10) is held, is held in particular braced, and that in particular the tension is realized by a, in particular via flange elements (53) realized, screw (52).

8. reflection silencer (1) according to at least one of the preceding claims,

characterized in that

the reflection body (10), in particular the discs (30, 31) of the reflection body (10), in a tubular

Sheath (60), in particular in a liner (60),

is included or are.

9. reflection silencer (1) according to at least one of the preceding claims,

characterized in that

at least in five axial planes (11), in particular at least in 10, 12 or 14 axial planes (11) of the reflection body

(10), respectively in the circumferential direction (12) of

Reflection body (10) arranged cavities (20)

are formed and / or the cavities (20) of the axial planes

(11) are each formed so differently that a broadband attenuation of sound emissions of the

Turbo compressor (100) takes place.

10. reflection muffler (1) according to at least one of the preceding claims,

characterized in that

the cavities (20) are formed such that a

Damping in a range of a Flügelradumlauffrequenz

("Blade passing frequency") of the turbocompressor (100) and at least one second harmonic and / or third

Harmonic and / or fourth harmonic to the

Impeller rotational frequency of the turbo compressor (100) takes place.

11. reflection silencer (1) according to at least one of the preceding claims,

characterized in that

the cavities (20) are formed such that a

Damping is designed for a speed range of 50% to 105% of a rated speed of the turbocompressor (100).

12. reflection muffler (1) according to at least one of the preceding claims,

characterized in that

the turbocompressor (100) is an axial turbocompressor or a radial turbocompressor and / or that the

Reflection muffler (1) directly on a pressure side (101) of the turbo compressor (100) or directly on a suction side (102) of the turbocompressor (100) is arranged.