EP2047073B1 - Silencieux à fabrication facile - Google Patents

Silencieux à fabrication facile Download PDF

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Publication number
EP2047073B1
EP2047073B1 EP07785765A EP07785765A EP2047073B1 EP 2047073 B1 EP2047073 B1 EP 2047073B1 EP 07785765 A EP07785765 A EP 07785765A EP 07785765 A EP07785765 A EP 07785765A EP 2047073 B1 EP2047073 B1 EP 2047073B1
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EP
European Patent Office
Prior art keywords
section
silencer
sound
slots
absorptive
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Not-in-force
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EP07785765A
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German (de)
English (en)
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EP2047073A1 (fr
Inventor
Svend Frederiksen
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Silentor Holding AS
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Silentor Holding AS
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/02—Silencing apparatus characterised by method of silencing by using resonance
    • F01N1/04—Silencing apparatus characterised by method of silencing by using resonance having sound-absorbing materials in resonance chambers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/02—Silencing apparatus characterised by method of silencing by using resonance
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/08—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/08—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling
    • F01N1/086—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling having means to impart whirling motion to the gases
    • F01N1/087—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling having means to impart whirling motion to the gases using tangential inlets into a circular chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/08—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling
    • F01N1/10—Silencing apparatus characterised by method of silencing by reducing exhaust energy by throttling or whirling in combination with sound-absorbing materials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/24—Silencing apparatus characterised by method of silencing by using sound-absorbing materials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
    • F01N3/08—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous
    • F01N3/10—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust
    • F01N3/18—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by methods of operation; Control
    • F01N3/20—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by methods of operation; Control specially adapted for catalytic conversion ; Methods of operation or control of catalytic converters
    • F01N3/206—Adding periodically or continuously substances to exhaust gases for promoting purification, e.g. catalytic material in liquid form, NOx reducing agents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N2230/00—Combination of silencers and other devices
    • F01N2230/04—Catalytic converters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N2240/00—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being
    • F01N2240/20—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being a flow director or deflector
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust

Definitions

  • the invention relies on fitting into silencers silencing sections comprising radially extending, through-flowed slots, being constituted by solid or perforated slots to create Low-Pass filter sections or sound-absorptive sections.
  • These slots and further elements of a completely or partly flat shape that results in efficient and manufacture-friendly silencers, can be made in many configurations, to achieve preferred noise attenuation and pressure-drop characteristics.
  • the invention is not restricted to a round shell, many of the particularly preferable embodiments of the invention are adapted to such shells, in particular to the very common shapes of a cylindrical or nearly cylindrical shell. Furthermore, many configurations using sound-absorptive material in a simple manner prevent contact corrosion of the inner surface of the shell.
  • silencers according to the invention can be adapted to be inserted into new or existing chimneys, for instance dispersing exhaust gas flow from an internal combustion engine.
  • Gas flow silencers come in various basic forms that are often combined to achieve a good broad-banded attenuation of noise; that is noise reduction at low, medium, and high frequencies.
  • a first basic form is the through-flowed, sound-absorptive type of silencer that is predominantly efficient at higher frequencies and sometimes mid-range frequencies as well.
  • a second form is the Low-Pass filter silencer, which in particular is able to reduce noise at low frequencies.
  • Low-Pass filter silencers are sometimes instead termed expansion chamber silencers, reactive silencers, or reflection-type silencers.
  • a common form of an absorptive silencer is the splitter-type silencer. This type above all results in shells of a rectangular shape. It can of course also by adapted to cylindrical shells, but at higher manufacturing cost. As with all absorptive silencers, their performance drops at low frequencies. Although this can be compensated for by combining them with Low-Pass filter silencers, there would be an overall improvement of silencing if the function of absorptive silencers could be extended further down in the frequency range, in particular when space is scarce. The invention makes this possible.
  • absorptive and Low-Pass filter silencing sections are designed in ways that require quite different elements to compose each type of section. This contributes to relatively high manufacturing costs of most high-performance silencers. In contrast, the invention makes it possible to use very similar elements in the two types of silencing sections.
  • silencers of both the absorptive and Low-Pass filter types fitted into cylindrical shells are composed of internal parts, many of them being round. Such elements are rather costly, not least when shells are not perfectly cylindrical, but slightly oval, as is often the case in practice, where silencers, not allowing for costly manufacture of accurate and expensive shells unavoidably will be oval by several units of percentage. By first inspection, such a deviation may not seem great, but in practice it will, in many types of prior art silencers, call for a lot of work to adapt internal elements to such tolerances.
  • the present invention is capable of fulfilling all the needs and overcoming all these difficulties in particularly manufacture-friendly silencers.
  • Figs.1a-1c show a first embodiment of the invention, this first embodiment being an engine exhaust silencer 1 comprising a single silencing section 2, being a through-flowed sound-absorptive section.
  • Fig. 1a is a longitudinal section, and fig. 1b a cross-section, along B-B.
  • Fig. 1c is an enlarged view of part of the cross-section, and fig. 1d is a typical noise reduction spectrum of the first embodiment. In the discussion of other embodiments of the invention, further reference will be made to this kind of spectrum.
  • a silencing section 2 is comprised within a casing 3 being constituted by a cylindrical shell 4 and end flanges 5 and 6 at opposite ends of the casing. Gas is led into the silencer via an inlet opening 7, from an inlet pipe 8 leading gas up to this opening. Similarly, an outlet opening 9 leads gas from the silencer, via an outlet pipe 10, discharging gas to the atmosphere at an opening 11.
  • a silencing section 2 is delimited by a plane inlet face 12 and a plane outlet face 13. Between silencer inlet 7 and section inlet face 12, a cavity 14 is through-flowed in such a manner that gas flow entering this cavity will diverge axi-symmetrically, as indicated by velocity arrows.
  • the inlet face has been divided into two parts: an outer, through-flowed and annular part 15 and an inner, not through-flowed, circular-cylindrical core part 16.
  • a cylindrical, solid shell 4 constitutes the division between these two silencer section parts.
  • the arrangement of forcing flow within the cavity 14 to diverge in this manner serves the purpose of ensuring an approximately uniform flow into and within the annular section. Without such a core part forcing the flow to spread out radially, there would be a tendency for flow into the silencing section 2 to be concentrated around to the centre, especially if the cavity 14 is of a short length, as is the case of the shown embodiment. Below it will be demonstrated how such a concentration can be avoided in other ways within the scope of the invention.
  • Fig. 1c shows an enlargement.
  • the innermost delineation of the segment body is arc 24 of the previously mentioned solid, cylindrical shell 17.
  • Slot 18 is sidewise delimited by plane, perforated plates 23, the lower plane, perforated plate 23 belonging to the adjacent, segmental body (see fig. 1b ), situated below the segmented body shown in fig. 1c .
  • the slot is supplemented by a small distance-controlling member 25 adjacent to a very small arc part 26 of the cylinder.
  • a likewise small distance-controlling member 27 is arranged adjacent to cylindrical shell 4. The two small members will ensure a well-defined width s of slot 18.
  • Sound-absorptive material 28 is comprised within each sector body.
  • the embodiment shown is an exhaust silencer, in which this material will typically be heat-resistant mineral or glass wool. If the silencer had instead operated at low temperature, such as for instance atmospheric air in a ventilation system, alternative types of absorptive materials, such as open-celled polymeric foam, could have been used.
  • a non-perforated plate 29 is arranged, blocking flow from entering the core part 16. Also, segmental bodies 20 delimit each of the eight sectors as well as the core region, such that neither the interior of the sector bodies nor the core part will be entered by any gas flow or by any acoustical energy propagating with the gas. Plate 29 is provided with in total sixteen openings giving gas flow free entrance to all eight slots 18 and all eight outer region void spacings 21. Along contour lines where an inlet face intersects with slots 18 and voids 21, there may be (not shown) roundings, for instance made by impressions onto inlet plate 29. Such roundings will prevent vena contracta flow phenomena and will thus lower flow resistance of the silencing section 2.
  • a plate 30 with in total sixteen openings is provided at silencing section outlet 13 .
  • the shape of this plate resembles that of plate 29, but where plate 29 delimits the core region, plate 30 is not full, but instead perforated to constitute an inner, circular part 31. This will admit sound waves travelling against the overall flow direction within the silencer to enter the core region.
  • a perforated, circular plate 32 has been arranged within the core part 16, dividing it into an upper part 33 and a lower part 34, respectively. The upper part has been filled out with sound-absorptive material 28.
  • the entire core body 16 could have been void.
  • the effect of this would be that at f4 there would be a more pronounced noise-reducing effect, but only in a small frequency range.
  • the shown embodiments of the invention, or variations of the segmental configuration will provide a better sound absorption of noise of relatively low frequencies, corresponding to wavelengths in the order of magnitude corresponding to the diameter D of the cross-section.
  • annular section 15 What has been termed "acoustically effective volume" in the above will substantially be equal to the combined volumes of annular section 15 and voids 14 and 17, that is a major part of interior of the silencer.
  • the volume of annular section 15 would not be lost from a LP-filter effect point of view.
  • a way of illustrating this is to imagine a sound wave being reflected at cross-sectional change from shell diameter to pipe diameter at the opening 9. Such a wave will travel backwards across the silencing section outlet 13. Even though a small sound reflection will occur at the relatively small effective cross-sectional change at the annular part of the outlet section 13, this will only cause a modification of the LP-filter effect; it will not cancel it.
  • Fig. 1d is a schematic diagram of a noise attenuation spectrum of the first embodiment of the invention.
  • the previously mentioned frequency fL p can be seen at the bottom end of the noise reduction spectrum.
  • f4 a relatively high level of noise reduction has been reached.
  • the beneficial effect of f4 manifests itself as a small peak, which may be beneficial if the noise spectrum to be attenuated also exhibits a peak at this frequency.
  • the LP-filter effect can be made effective from a sufficiently low frequency to become effective in a frequency in the range of 100 - 300 Hz, a normal "firing" frequency of a combustion engine. Taking the sizes of penetration depth P (see fig. 1c ) to be around the previously mentioned value of 0.5 meter, not only will this be possible, but sound-absorptive effects will not be insignificant at the firing frequency, which can often be considered to be the most prominent one in the noise spectrum of an engine.
  • the correctness of this postulate can be shown by reference to the chapter on silencers in the well-known acoustical textbook authored by Beranek & Ver, although in corresponding diagrams another notation has been used.
  • Fig. 2a and 2b depict a prior art sound-absorptive silencer configuration that in its essential form is well-known, for instance from Beranek & Ver.
  • This silencer can be viewed as a variation of what is sometimes referred to as "a lined duct".
  • the circular-symmetrical configuration with a shell 4 of length L and a diameter D comprises a lining in the form of sound-absorptive annular body consisting of an inner, perforated cylinder 5 which is surrounded by sound-absorptive material 6. In the absence of further silencing elements, it would have been a proper lined duct silencer.
  • the silencing capacity has been improved by supplementing the lining with an inner body consisting of a somewhat smaller, perforated cylinder 7 harbouring further sound-absorptive material 8. Between the two perforated cylinders 5, 7 a rather narrow annular slot 9 of width s leads flow through the sound-absorptive section.
  • Beranek & Ver for this and other prior art absorption silencers specify the attenuation frequency curve with an ordinate that may essentially be expressed as L/s, although the notation is also different in this case. That is, the attenuation is proportional to the length of the section and inversely proportional to the width. Thus, narrowing down the width for a given length will not only extend the attenuation curve (cf. fig. 1d ) towards higher frequencies, but will also increase the overall attenuation level. An intuitive consideration can explain this: if a slot is made narrower, the mean distance from acoustic energy, distributed across the slot, will be brought closer to the sound-absorptive surface.
  • widths of slots and voids can be made relatively small.
  • Concerning voids 21 the width can be interpreted as the mean value s', taken in the peripheral direction. Admittedly, within the voids 21 there is only sound attenuation on one side. As a general guideline, s' should not exceed s excessively, since this would lead to a situation where a major part of the total flow will pass through parts of the silencing section having a relatively great slot width.
  • Fig. 3 shows a cross-section of a second embodiment of the invention with only three slots 18, three sound-absorptive segments 19, and three outer voids /supplementary 'slots' 21. Comparing with fig. 1b , it can be seen that in the second embodiment widths s and s' are significantly bigger, which will lead to a smaller attenuation per unit length. A relatively open structure may be necessary in some cases to avoid a too big flow velocity. But if ample length is at disposal, attenuation can still be significant.
  • the third embodiment of the invention shown in fig. 4a , can be represented as an attractive configuration.
  • a single, flat and perforated plate delimiting the voids 21 of sound-absorptive material 28, two plates 20, creating a V-shape with an apex 3, have been inserted.
  • a quadruple segmental body has been created.
  • an internal, perforated plate 29, to assist in manufacturing an absorptive structure of great mechanical robustness has been inserted.
  • Figures 4b, 4c, and 4d illustrate a step in manufacturing procedure applied to the V-shape constituted by plates 23 with apex 1 in the core region, with plate 29 in a position ready to be lowered.
  • the procedure being explained here can be applied to all polygonal, outer shells of bodies adopted according to the invention, for example to the triangles of fig. 3 .
  • Plates 23 have been arranged onto a supportive structure 5. At apex 1 in the bottom there may be a sharp connection (as shown in the figure) or a rounding, which may contribute to a simple manufacture.
  • the V-shape could be manufactured by bending a single sheet of perforated metal.
  • Sound-absorptive material 28 has been arranged onto the plate V-shape. More sound-absorptive material than needed to fill out the potential triangle has been brought in place. The reason for this is that when the triangle has been completed by welding at ends 2, there will be a compression of the absorptive material, which will increase the mechanical stability of the absorptive material during service: Firstly, a tendency for fibres to be sucked out of perforations will be smaller.
  • Fig. 4c which is an enlargement of part of the triangular body at a perforated wall, shows that as a refinement, a thin layer of, for instance steel wool, 6 can be interposed between perforated plate 23 and mineral wool 28.
  • a thin structure should be open so as to represent no major resistance to penetrating sound waves, but of greater strength than mineral wool.
  • Fig. 4d shows a sectional view taken across B-B in fig. 4b ; that is if one looks down upon sound-absorptive material and ends 2 of the V-shape.
  • This figure illustrates a further feature of the invention, viz. that silencing sections to a great extent can be produced from metal sheets 7 of identical width that may simply be of a width that is offered as standard widths in the market. This will greatly reduce the amount of cutting.
  • At intersections 8, one may arrange transverse walls 8 that together with internal plates 29 will further contribute to keep the absorptive structure coherent during long time of service.
  • the manufacture-friendly kind of silencing sections described not only permit manufacture to be performed by relatively un-skilled labour and/or with a high degree of automation, but also offers possibilities of dividing manufacture of various parts of silencers into work performed in various geographical locations. This will sometimes be both cost-saving and will simplify logistics to make possible swift arrangement of tailor-made silencers all around the world.
  • parts of the internals such as V-shapes can be manufactured in a first place, for instance a low-cost country. V-shapes can be stacked onto each other in a very compact way, which will reduce shipping costs. In a second place, closer to the final destination, all internals of the silencer can be assembled.
  • Fig. 5a - 5d show a fourth embodiment of the invention.
  • the upper section 2 is a through-flowed, sound-absorptive section like section 2 in fig. 1 .
  • the lower section 1 is instead a through-flowed Low-pass filter section, where flows inside passages 18, 19 are not delimited by perforated plates, but by full plates 23.
  • flow widths here can generally be made narrower compared to providing perforated plates, where the risk of absorptive material being sucked out through perforations exists.
  • From fig. 5a it can be seen that there are small, longitudinally clearances 30 between plates 23 and shell 4. Passages 18, 19 will be closed off by long strips (not shown), arranged adjacent to the clearances, so that the passages are completed closed off radially.
  • a Low-Pass (LP) filter section apart from a general increase in noise reduction, can extend noise reduction spectrum significantly towards lower frequencies. Especially with silencers of small diameter, such a function can be indispensable. Especially the shown type of a Low-Pass filter with built-in diffusers will create a relatively low pressure drop. Significant low frequency noise reduction can indeed be created in a relatively narrow space by strongly throttling flow, but this will represent a significant drawback in terms of pressure drop across the silencer.
  • section 1 by a division line 18 is divided into a lower part 1' with constant slot width, while in the upper part 1" the width of the slots 19 gradually increases in flow direction, to constitute pressure-recovering diffusers.
  • V2 can be interpreted to include volumes of cavities 15 and 16, as well as the volume of a major part of section 2, since sound-absorptive material in relation to the LP filter effect can be taken as void space.
  • inlet face 17 to the LP-section there is a circular plate with such openings only allowing passage of gas from cavity 14 to enter into the - in this embodiment - four radially extending passage entrance parts 18. That is, when comparing the LP-section with a sound-absorptive section, for instance section 2 in the present embodiment, voids 21 adjacent to the shell are not through-flowed, and perforated plates 22, constituting divisions between these voids and the inner, sound-absorptive sectional bodies 20, are not swept by gas flow.
  • a diffuser of the kind shown requires that there is only a rather small increase in flow area inside each passage per length unit in flow direction.
  • splitting up the total flow within the passage into several smaller parallel passages allows for diffusers of a given length to attain a bigger outflow / inflow area ration than if the entire flow were concentrated to a single passage.
  • the pressure-recovering effect will become bigger.
  • this feature is of importance.
  • the present embodiment demonstrates how a through-flowed sound absorptive section and a through-flowed LP-section according to the invention can be combined in a simple way to supplement each other excellently.
  • the LP-section will extend the noise reduction spectrum at very low and very high frequencies, while the sound-absorptive section will help suppress standing waves that would otherwise lead to significant noise reduction at corresponding frequencies.
  • Fig. 6 is a cross-sectional view of a fifth embodiment of the invention, comprising an LP-section of a constitution both bearing similarities to and representing differences compared to section 1 of the previous embodiment.
  • perforated plates 22 there are full plates 22, and the not shown plate 17 will be shaped with additional openings in such a way that voids 21 are being through-flowed supplementary to passages 18. Thereby, the entire flow will be divided into as much as eight flow parts.
  • enclosures 20 comprise sound-absorptive material. This material will be brought to contribute to noise reduction by arranging a transverse, perforated plate, so that the enclosures of the present embodiment will function similarly to the core part of the first embodiment, by way of sound waves penetrating the cavities from the rear end of the section.
  • the shape of the present LP-section can be made in such a way that one could arrange an absorptive section with rather equal quadruple segments downstream of an LP-section represented by the present embodiment, so that flow areas will be unchanged or increase somewhat when passing from the first to the second section.
  • Plate 17 could be perforated adjacent to sound-absorptive material, and a full, transversely arranged plate akin to plate 17, but without perforations, could be arranged at the transition.
  • the fifth embodiment has been adapted to retain simplicity of manufacture in the case of a slightly oval shell.
  • Distance-keeping elements 24 are seen to be shorter than elements 25, and all four segments are substantially identical, one (but not the only) feature that will contribute to simplify manufacture.
  • the design has been made in such a way that identical segments have been accommodated inside a slightly oval shell.
  • Round shells of silencers are usually made by rolling up flat sheets of metal and joining ends by welding. Although there will usually be an ambition to achieve a shape as close as possible to a cylinder, this simple manner of manufacture will in fact seldom yield a perfect, circular symmetrical shape. Experience shows that ovalities of a magnitude of several percentage units of the diameter are more common than not. Of course, if in the previously shown embodiment the shape of the shell had been slightly oval, the contour of plate 17 could also have been made slightly oval to match the ovality of the shell. However, since the degree of ovality will often change slightly in longitudinal direction, a simple oval plate arrangement may cause difficulties when arranging the plate inside the shell. As the person skilled in the art will appreciate, this problem can be taken care of when designing an arrangement akin to that shown in figs. 5a-c , but the fifth embodiment can sometimes represent a cheaper solution.
  • the ovality is not excessive, choosing slot widths smaller than with a cylindrical shell shape can compensate, so that the total flow area is retained.
  • the shapes of the quadruples can be made slightly unsymmetrical.
  • Figs. 7a - 7d show a sixth embodiment of the invention, supplemented by four diagrams 7e - h.
  • Figs. 7a - 7d show a sixth embodiment of the invention, supplemented by four diagrams 7e - h.
  • Figs. 7a - 7d show a sixth embodiment of the invention, supplemented by four diagrams 7e - h.
  • five through-flowed silencing sections have been arranged within a chimney 1.
  • a non-through-flowed silencing section 10 at the bottom there is a non-through-flowed silencing section 10.
  • Sections 11, 13, and 15 are all LP-filter sections, while sections 12 and 14 are through-flowed sound-absorptive sections. Section 10 at the bottom serves as a resonator and sound absorber.
  • the seven sections are of partly differing lengths, for reasons to be explained.
  • manufacture of the embodiment can be rationalised to a great extent, not least because individual lengths (exemplified as part-sections 28 of section 11) of sections have been chosen in a modularised way, as previously shown.
  • the height of a chimney will typically be chosen so as to effectuate a sufficient distribution of discharged gas to the surroundings.
  • the length could sometimes be adapted to better suit noise reduction features.
  • an attractive feature of the present embodiment is that sufficient noise reduction capacity and low pressure drop can often be provided without any change of chimney height. This feature will be especially appreciated when an existing chimney is being retro-fitted by inserting noise reduction elements.
  • FIG. 8 shows a cross-section of a seventh embodiment of the invention, adapted to a shell that is not of a small diameter, but on the contrary as big as for instance 4 meter.
  • hollow, not through-flowed triangles 1 made up of identical, perforated plates 2, 3, and 4 have been arranged inside sound-absorptive sections 5.
  • all sound-absorptive material can be penetrated by a simple arrangement. For example, with a velocity of sound of 400 m/s, according to the formula for fD, full sound-absorptive effect will be attained from a frequency around 100 Hz, which may suffice to provide sufficient noise reduction capacity in the entire frequency range down to firing frequencies of combustion engines, reciprocating engines as well as gas turbine engines.
  • a single, long through-flowed sound-absorptive silencing section may provide sufficient noise reduction.
  • Such a design will indeed be of low manufacturing cost.
  • All embodiments of the invention shown, including the seventh embodiment, display the feature of eliminating contact corrosion between sound-absorptive material and the internal surface (2 in fig. 7a ) of the shell.
  • a chimney weakened by such corrosion could disintegrate completely in the event of a storm causing bending load onto the chimney.
  • LP-filter sections are efficient in enhancing attenuation at low frequencies. In addition they contribute to attenuation within a wide range of mid-frequencies and high frequencies.
  • LP sections also suffer from the disadvantage that they are more prone than pure absorptive sections to perform dips in attenuation, in particular due to half-wave resonances ⁇ /2, cf. figs. 7e, f, and g . These dips are here counteracted by supplementing LP-filtering with sound-absorptive features, both within the LP-sections and within the sound-absorptive sections. Further, coincidences of dip frequencies to a significant extent have been avoided by designing passages of LP-sections to be of unequal lengths.
  • inlet pipe 8 has a right-hand part 8' that is directed partly upwards. This serves the triple purpose of facilitating incoming flow to change direction in an ordered manner inside cavity 16, increasing the length of section 10, and making it possible for the man to enter the chimney via opening 7 (cf. sidewise view in right-hand direction shown in fig. 7b ), by disassembling the pipe arrangement.
  • the sections have been attached to fixture elements as well as transverse plates inhibiting flow through voids 21 at the top of the LP-sections, instead of at the inlet (bottom here), as shown previously.
  • this will facilitate insertion of elements, especially if the sections are to be inserted by being lowered from the top of the chimney.
  • sectional elements can expand and contract freely downwards and upwards. This latter facility in the embodiment shown also pertains to through-flowed absorptive sections 12 and 14.
  • FIG. 7d A further additional facility of the present embodiment can be seen in fig. 7d , combined with inspection of fig. 7a , where, in addition to the previously mentioned man 33, another man 35 at the top of the chimney is shown: Movable wing-like sectional parts 29 can be turned around the longitudinal axis and relative to fixed sectional parts 30, so that cross-sectional areas of slots 31 can be varied, both in section 11 and in section 15. Not shown elements will permit the movable sectional parts to be fixed during operation and released when adjustments are made.
  • Man 35 has been positioned at the top of the chimney by a vehicle equipped with a telescopic arrangement 37. This man is equipped with a tool 36 permitting him to turn the movable section element by making the turning operation by attachment of the tool to central element 37.
  • slot widths of LP-sections 11 and 15 could be made smaller by inserting plane plates into the slots.
  • Figs. 9a - 9e show an eighth and final embodiment of the invention, including an SCR-denox facility.
  • Fig. 9a is a longitudinal view of the embodiment, including exhaust piping 8 connecting a silencer with an engine 9 of which only a small part is depicted, including a turbo-supercharger 10.
  • Fig. 9b is an enlarged longitudinal view of a passage.
  • Figs. 9c and 9d are two cross-sectional views, and fig. 9e is a folded-out side view of a circular arrangement where the last-mentioned cross-sectional view has been arranged.
  • a standard honeycomb SCR catalyser section 11 has been arranged inside shell 4.
  • Urea is injected from the outside, via a pipe 12 that leads a urea flow radially (13) inwards to the core region, where the pipe bends upwardly to form a short, vertical part 14, which is a nozzle for injecting urea via holes 15 into slots 18 of an LP filter section 17 having been arranged.
  • urea is being injected radially outwardly into the slots, but the gas flow will gradually change the direction of urea flow into an approximately longitudinal flow direction, following the main gas stream.
  • the initially quite different flow directions of gas and urea in the centre parts of the slots will promote mixing of urea with gas as well as evaporation of urea in addition to the residual mixing and evaporation (if necessary) taking place in the downstream region.
  • the arranged is supposed to be designed in such a way that all urea will have evaporated before entering the catalyser.
  • This embodiment represents a very compact solution to a combined problem of reducing noise and NOx, within a limited total space available, especially adapted to a case where this space is provided immediately above the engine.
  • it will still be advantageous to arrange the catalyser into the silencer but there may be a significant length of upstream piping, for instance to include a horizontal pipe, at the inlet of which urea can be injected. If the piping is long enough, the injected amount of urea may have evaporated already upstream of the silencer.
  • the arrangement with injection from the core part of the LP filter section eliminates a necessity for several injection nozzles, to achieve good urea distribution.
  • Fig. 9b shows a sidewise view of a slot 18 of the LP filter section.
  • a stepwise increase in width s of the slot from a more narrow slot part 20 to a wider part 21, and thus of the total flow area.
  • a moderate, stepwise increase of flow area although slightly less efficient in terms of pressure recovery, is in fact quite good; it is known as a Borda diffuser.
  • Use of such a stepwise increase instead of a gradual increase of slot width as shown in the first embodiment of the invention, has the advantage of being cheaper to manufacture, in particular when made from standardised (modular) widths of sheets of metal as previously explained.
  • the segments would still serve a noise-reducing purpose, but within a more narrow part of the frequency spectrum.
  • any condensation of corrosive gas components can generally be prevented by arranging sound-absorptive material away from the inside of the shell which, due to heat loss to the surroundings, will attain a temperature that is lower than that of the gas flow. This is avoided, as also pointed out in the present embodiment. Sound absorptive material has been arranged away from the outer shell and will thus be exposed to relatively high temperatures, which will act against condensation or urea. Furthermore, since in the present case sound-absorptive material has been arranged within segments that are not through-flowed by gas, the sound-absorptive segments only to a small degree can be continuously fed with ever new amounts of urea.
  • Urea can 'creep' along surfaces to produce a nasty 'salmon effect', that is propagating opposite to a general flow direction.
  • this problem will usually be easy to handle.
  • urea injection is made close to and above the engine, as in the embodiment shown, via vertical pipe 8 leading up to the silencer, this problem becomes less easy to handle, especially when space for noise reduction is scarce, and only a moderate back-pressure to the engine can be accepted.
  • this problem it is important to take not only the case of steady-state operation into consideration, but also situations where there may be some not-intended urea injection at stand-still.
  • the bottom section 25 of the embodiment solves this problem by a design of a double LP-filter section that will both prevent urea back-flow and contribute significantly to noise reduction, in a flow-friendly way that will require a minimum of pressure drop.
  • a circular inlet plate 26 blocks flow, except for flow parts entering each of four slots 27. Flow leaving these slots will enter an interior chamber 28 of the section. From here, flows enter four further slots 29 attached to a top plate 30 arranged at the outlet of the section, blocking all flow, except for the four flow parts leaving slots 30.
  • the two mentioned groups of four slots are off-set from each other by 45 degrees. In the longitudinal direction, the two groups of slots overlap each other, so that flow parts inside chamber 28 will generally follow a route that turns the flow parts two times 180 degrees.
  • a further facility of section 25 is that it will function as a spark-arrestor, i.e. sparks that may leave the engine and enter the apparatus will be caught so that they will not leave the apparatus or even propagate up to catalyser 11 that may be sensitive to sparks. Since both sections 17 and 25 reduce sound, they will also reduce gas-dynamic, vibratory forces from the gas onto the catalyser, such forces often being seen to reduce the life-time of a catalyser.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Health & Medical Sciences (AREA)
  • Toxicology (AREA)
  • Exhaust Silencers (AREA)

Claims (21)

  1. Silencieux muni d'un boîtier (3), ledit boîtier (3) étant constitué d'une coque (4) cylindrique possédant un axe central longitudinal, ledit silencieux étant destiné à être traversé par un écoulement de gaz pénétrant dans ledit silencieux par au moins une entrée (7) et sortant dudit silencieux par au moins une sortie (9),
    - ledit silencieux comprenant au moins un tronçon interne insonorisant, absorbant le son, comprenant à la fois des pièces de corps segmentaires (20) et des pièces creuses (18, 21), ledit tronçon insonorisant s'étendant entre ladite entrée (7) et ladite sortie (9) dudit silencieux, et ledit tronçon insonorisant étant géométriquement délimité le long de l'axe central longitudinal par une face d'entrée (12) et une face de sortie (13), une première cavité (14) traversée par un écoulement étant située entre ladite entrée (7) du silencieux et une face d'entrée (12) du tronçon et une deuxième cavité (17) traversée par un écoulement similaire étant située en aval du tronçon insonorisant (2), et
    - ledit tronçon insonorisant dans une direction transversale à l'axe central longitudinal comprenant une région centrale, ladite région centrale s'étendant autour dudit axe central longitudinal et vers l'extérieur en direction d'une partie externe de la région centrale,
    - ledit tronçon insonorisant comprenant au moins trois desdites pièces creuses, celles-ci étant des rainures (18) oblongues s'étendant vers l'extérieur depuis ladite région centrale en direction dudit boîtier (3) et s'étendant le long de l'axe central longitudinal, permettant au gaz de s'écouler longitudinalement dans les rainures (18) oblongues,
    - et comprenant au moins trois desdites pièces creuses, celles-ci étant des creux externes (21) adjacents au dit boîtier (3) et s'étendant vers l'intérieur depuis le boîtier vers une pièce de corps segmentaire (20) de manière à ce qu'il n'y ait aucun contact entre les pièces de corps segmentaires (20) et le boîtier (3), et permettant au gaz de s'écouler longitudinalement dans les creux externes (21) et
    - lesdites au moins trois rainures (18) oblongues et lesdits au moins trois creux (21) s'étendant depuis ladite face d'entrée (12) vers ladite face de sortie (13), lesdites rainures (18) oblongues et lesdits creux (21) communiquant avec ladite première cavité (14) et avec ladite deuxième cavité (17), les parois latérales desdites rainures (18) oblongues étant essentiellement planes le long de l'extension vers l'extérieur.
  2. Silencieux selon la revendication 1, dans lequel au moins une desdites rainures (18) forme une intersection dans la région centrale, soit avec un angle entre une extension radiale vers l'extérieur des rainures (18) et/soit de manière à ce qu'une ou plusieurs paires de rainures (18) réunies forment visuellement une seule rainure traversant ladite région centrale.
  3. Silencieux selon la revendication 1 ou 2, dans lequel au moins un corps central (16) est présent dans ladite région centrale.
  4. Silencieux selon la revendication 3, dans lequel ledit corps central (16) est destiné à bloquer pour l'essentiel l'écoulement de gaz entre lesdites rainures traversant ladite région centrale.
  5. Silencieux selon l'une quelconque des revendications précédentes,
    - dans lequel ledit tronçon insonorisant est un tronçon absorbant le son traversé par un écoulement, et dans lequel lesdites rainures (18) sont délimitées transversalement et longitudinalement par des parois latérales, et
    - dans lequel lesdites rainures (18) sont des plaques au moins en partie perforées et au moins en partie essentiellement planes, et dans lequel l'absorption du son est obtenue en plaçant un matériau absorbant le son (28) sur un côté opposé desdites plaques, vues depuis lesdites rainures (18).
  6. Silencieux selon l'une quelconque des revendications précédentes, dans lequel la section d'écoulement moyenne totale dans ledit tronçon insonorisant, celle-ci étant une valeur moyenne le long de l'extension longitudinale dudit tronçon, occupe moins de p % de la section transversale totale dudit tronçon, et dans lequel p est au maximum égal à 50, éventuellement au maximum égal à 30, ou même éventuellement au maximum égal à 20.
  7. Silencieux selon l'une quelconque des revendications précédentes, dans lequel ledit tronçon insonorisant (1) est un tronçon de filtrage passe-bas traversé par un écoulement, et dans lequel au moins une partie des parois desdites rainures (18) est constituée de parois essentiellement étanches au son.
  8. Silencieux selon l'une quelconque des revendications précédentes, dans lequel ledit tronçon (1) est un tronçon non traversé par un écoulement étant en contact acoustique avec ledit écoulement de gaz, et étant conçu pour assurer une fonction de résonateur acoustique et/ou une fonction d'absorption acoustique du son.
  9. Silencieux selon l'une quelconque des revendications précédentes, dans lequel au moins un tronçon (2) est un tronçon absorbant le son traversé par un écoulement et au moins un autre tronçon (1) est un tronçon de filtrage passe-bas traversé par un écoulement, et dans lequel lesdits deux tronçons (1, 2) sont joints, de manière à ce que l'écoulement passe directement de l'un des tronçons (1, 2) dans l'autre tronçon (1, 2), ou dans lequel un espace interstitiel peut être présent entre les deux tronçons (1, 2).
  10. Silencieux selon la revendication 9, dans lequel lesdites rainures (18) faisant partie d'un tronçon sont décalées par rapport aux rainures d'un autre tronçon, de manière à ce que l'écoulement passant entre lesdits deux tronçons (1, 2) soit forcé à dévier substantiellement d'un écoulement longitudinal direct dans le(s) espace(s) interstitiel(s) entre lesdits deux tronçons (1, 2).
  11. Silencieux selon l'une quelconque des revendications précédentes, dans lequel lesdites rainures (18) sont conçues pour être des diffuseurs récupérateurs de pression grâce à une augmentation de la section d'écoulement dans le sens d'écoulement du gaz, soit par augmentation progressive de la section d'écoulement et/soit par augmentation par paliers de la section d'écoulement.
  12. Silencieux selon l'une quelconque des revendications précédentes, dans lequel lesdites rainures (18) et la délimitation desdits creux (21) forment ensemble des tronçons essentiellement en forme de polygones.
  13. Silencieux selon la revendication 12, dans lequel lesdits polygones présentent au moins une des formes suivantes : essentiellement triangles ou essentiellement quadrilatères.
  14. Silencieux selon l'une quelconque des revendications 12 à 13, dans lequel lesdits tronçons ou parties desdits tronçons sont essentiellement identiques.
  15. Silencieux selon l'une quelconque des revendications précédentes, dans lequel au moins une partie de ladite coque (4) présente au moins une des formes suivantes : ronde, cylindrique essentiellement circulaire ou forme autre que cylindrique circulaire.
  16. Silencieux selon l'une quelconque des revendications précédentes, dans lequel le matériau absorbant le son (6) constitue une partie dudit tronçon insonorisant, et dans lequel pour l'essentiel aucun matériau absorbant le son faisant partie dudit tronçon n'est en contact direct avec ladite coque (4).
  17. Silencieux selon l'une quelconque des revendications 1 à 16, dans lequel pour l'essentiel aucun matériau absorbant le son n'est en contact direct avec la dite coque (4).
  18. Silencieux selon l'une quelconque des revendications précédentes, dans lequel au moins un desdits tronçons insonorisant est inséré dans un empilement de plusieurs tronçons insonorisants.
  19. Silencieux selon la revendication 18, dans lequel ledit empilement est destiné à être aligné essentiellement verticalement pendant son utilisation et est destiné à faire partie d'une installation fixe, et dans lequel ledit empilement est destiné à être directement ou indirectement fondé sur un sol solide.
  20. Silencieux selon l'une quelconque des revendications précédentes, dans lequel ledit silencieux comprend au moins un des moyens suivants : un catalyseur (11) destiné à transformer les composants nocifs dudit écoulement d'échappement ou un moyen (12) pour injecter dans ledit silencieux au moins une substance favorisant le fonctionnement dudit catalyseur.
  21. Silencieux selon la revendication 20, dans lequel un tronçon de filtrage passe-bas (17) dudit silencieux est doté d'un moyen (12) pour injecter ladite substance dans ledit silencieux.
EP07785765A 2006-07-14 2007-07-13 Silencieux à fabrication facile Not-in-force EP2047073B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DKPA200600986 2006-07-14
PCT/DK2007/050097 WO2008006383A1 (fr) 2006-07-14 2007-07-13 Silencieux à fabrication facile

Publications (2)

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EP2047073A1 EP2047073A1 (fr) 2009-04-15
EP2047073B1 true EP2047073B1 (fr) 2011-09-21

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EP (1) EP2047073B1 (fr)
AT (1) ATE525551T1 (fr)
WO (1) WO2008006383A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8309045B2 (en) 2011-02-11 2012-11-13 General Electric Company System and method for controlling emissions in a combustion system
US9067176B2 (en) 2013-03-15 2015-06-30 Honeywell International, Inc. Specialized ammonia injection grid with the dual purpose of suppressing noise
CN106523439B (zh) * 2016-10-26 2017-10-10 湖南航翔燃气轮机有限公司 中、高频复合式消声器和鼓风机
CN106762064A (zh) * 2017-03-13 2017-05-31 上海航天能源股份有限公司 一种燃气内燃机分布式能源脱硝及消音一体化装置
CN109838293B (zh) * 2019-03-29 2024-04-16 潍柴动力股份有限公司 一种混合器

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1857845A (en) * 1930-05-24 1932-05-10 Francis F Hamilton Exhaust gas silencer
US4325459A (en) * 1980-09-29 1982-04-20 Martin Mack M Muffler diffuser
DE102004057413A1 (de) * 2004-11-26 2006-06-29 Mahle Filtersysteme Gmbh Schalldämpfer für eine Brennkraftmaschine

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EP2047073A1 (fr) 2009-04-15
ATE525551T1 (de) 2011-10-15

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