EP2913513A1 - Silencieux d'admission - Google Patents

Silencieux d'admission Download PDF

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Publication number
EP2913513A1
EP2913513A1 EP15151861.0A EP15151861A EP2913513A1 EP 2913513 A1 EP2913513 A1 EP 2913513A1 EP 15151861 A EP15151861 A EP 15151861A EP 2913513 A1 EP2913513 A1 EP 2913513A1
Authority
EP
European Patent Office
Prior art keywords
resonator
channel
assembly
fluid
fluid channel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP15151861.0A
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German (de)
English (en)
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EP2913513B1 (fr
Inventor
Ingo Naubert
Michael Böhm
Olaf Lichtenberg
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Volkswagen AG
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Volkswagen AG
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Filing date
Publication date
Application filed by Volkswagen AG filed Critical Volkswagen AG
Publication of EP2913513A1 publication Critical patent/EP2913513A1/fr
Application granted granted Critical
Publication of EP2913513B1 publication Critical patent/EP2913513B1/fr
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Classifications

    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K11/00—Methods or devices for transmitting, conducting or directing sound in general; Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/16—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/172—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general using resonance effects
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
    • F02M35/1255—Intake silencers ; Sound modulation, transmission or amplification using resonance
    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K11/00—Methods or devices for transmitting, conducting or directing sound in general; Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/16—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/161—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general in systems with fluid flow

Definitions

  • the invention relates to an intake silencer for a fluid line and a heater with the intake silencer.
  • auxiliary heaters in motor vehicles.
  • a fluid such as air, mufflers
  • the intake is known to be a significant source of noise in the near field of the intake of the heater, it comes in the operation of the Heater and the necessary for combustion intake of combustion air to intake noise in different frequency ranges.
  • noise In the near field of the intake mouth arise noise with predominantly low-frequency frequency components, which are caused in particular by the combustion noise of the heater. Furthermore, noises arise with predominantly higher-frequency frequency components, which are caused in particular by a fan of the heater which heats the fluid, which are comparable to a turbine noise.
  • the publication DE 10 2010 049 578 A1 discloses a muffler assembly having a fluid conduit through which a fluid, in particular air, is guided.
  • the fluid line has seen in the flow direction to a fluid drain and a fluid supply.
  • the fluid, in particular the air thus flows from the fluid supply to the fluid outlet.
  • the fluid line is surrounded by a resonator arrangement which has three resonator tubes connected in series and arranged concentrically with one another.
  • the first resonator tube of the resonator arrangement is connected in a sound-transmitting manner to the fluid line via a connection opening in a wall. Only a small fluid exchange takes place via the connection opening, since the resonator arrangement has no outflow.
  • the muffler assembly further includes absorption devices that can be designed for different frequencies.
  • the invention is based on the object to further reduce the noise of the known muffler assemblies. Furthermore, the muffler assembly should be compact be formed and inexpensive and easy to produce. In addition, the silencer assembly should only have a low weight and be produced with low material costs.
  • the starting point of the invention is a silencer assembly comprising an insertion part, which is pushed in a state of assembly of the silencer assembly in a housing part, wherein the housing part has a fluid channel in which a fluid in the axial direction of the silencer assembly from an inflow opening to an outflow opening flows, and at the same time acts as a resonator tube for propagating in the fluid channel sound waves.
  • the housing part and the insertion part each have, prior to the assembly state, an open resonator chamber for each branch resonator branching off from the fluid channel, which are closed in the assembled state and in operative connection with the fluid channel acting as the resonator tube.
  • the noise development is substantially reduced by such a silencer assembly, wherein two resonator chambers are designed as branch resonators and a resonator tube by simple assembly, each providing the appropriate attenuation of sound waves.
  • the muffler assembly is thereby formed very compact, wherein the resonator tube and one of the resonator chambers are applied in the housing part, while the other resonator is applied in the insertion part, wherein advantageously the two resonator chambers are formed only by the assembly.
  • the two components, the housing part and the insertion part interlock with one another in such a way that two components of the silencer assembly which can be produced relatively simply and inexpensively can be produced.
  • These components also have a low weight, since only a small amount of material is necessary.
  • the two components, the insertion part and the housing part are designed such that they are in an advantageous manner after assembly in corresponding operative connection.
  • a lying on a midpoint in the axial direction longitudinal axis of a second housing part opening, which forms a feed channel of the fluid channel is arranged eccentrically with respect to a center of the lying in the axial direction longitudinal axis of the resonator chambers of the branch resonators.
  • This embodiment has the advantage that within the cylindrical muffler assembly of the feed channel is not in the center of the muffler assembly, in other words, the feed channel is arranged eccentrically with respect to the silencers of the prior art.
  • the eccentric arrangement of the feed channel has the advantage that a larger space is available for the resonator chambers above the longitudinal axis of the feed channel, so that a larger volume is available within the resonator chambers of both branch resonators, which is available to form a plurality of sub-chambers available.
  • the advantageous effects of these sub-chambers are explained in more detail in the description.
  • the muffler assembly is characterized in that the fluid channel comprises a first channel segment as inlet channel with the inlet opening for the fluid and coaxial thereto a second channel segment as a feed channel with the discharge opening for the fluid, so that the inflow opening and the outflow opening are arranged on one side of the muffler assembly, since the fluid channel is deflected within the housing part on the opposite side of the insertion part.
  • This embodiment has the advantage that the fluid channel is designed to be longer overall, since two channel segments are formed running substantially over the entire length of the muffler assembly.
  • the deflection also increases the sound attenuation within the fluid channel and part of the fluid channel, namely the inflow channel, can advantageously be used to collect condensate.
  • a further advantageous embodiment of the invention is that the housing part before the assembled state has an open resonator chamber which comprises a housing part plate extending in the axial direction, which already forms two partial chambers in the resonator chamber.
  • the insertion part which has a push-in plate, which is inserted in the assembled state into the resonator chamber designed as a branch resonator coaxially with the housing part plate extending in the axial direction.
  • three partial chambers are thus formed in the assembly state in the resonator chamber, which are connected to the fluid channel via a connection opening and in turn via connection openings according to the principle of reflection of sound in conjunction.
  • the insertion part which has the resonator chamber designed as a branch resonator, seen in the axial direction formed of two consecutive discs.
  • the two discs lying one behind the other are arranged on their inner diameters on a cylindrical wall, wherein the conversion comprises a nozzle opening extending in the axial direction of the muffler assembly of the insertion part forms.
  • the wall connecting openings are formed to two sub-chambers, which are connected via the connection openings with the fluid channel and in turn according to the principle of reflection of sound in conjunction.
  • the insertion part is thus already designed as a component so that a closed resonator chamber is created by simple insertion into the housing part, which ensures a sound attenuation of propagating into the muffler assembly sound.
  • first the second branch resonator, then the first branch resonator and finally the resonator tube develop their damping effect in the acoustic emission direction, the sound waves being transmitted radially into the branch resonators.
  • FIGS. 1 to 11 show a series type 100 of the muffler assembly.
  • FIGS. 12 to 14 show a prototype of the muffler assembly P100.
  • FIG. 1 shows a perspective view of a housing part 10 of a muffler assembly 100, in particular an assembly of a Ansauggeräuschdämpfers for a heater, in particular for a heater.
  • the intake silencer or the silencer assembly is referred to below as the silencer 100 shortened.
  • the muffler 100 in addition to the advantageous design and arrangement of the components 10, 20, 30, S1, S2 of the muffler assembly 100, achieves a broadband attenuation of sound waves L, wherein the muffler 100 uses the principle of absorption or reflection as well as the combination of absorption and reflection in certain areas.
  • FIG. 1 is a bottom of the muffler 100 visible.
  • a fastener 10E arranged in the later installation situation on the side (in FIG. 1 shown above) of the muffler 100.
  • the fastening element 10E is advantageously connected in one piece with the body of the housing part 10.
  • the housing part 10 and thus the entire muffler 100 can be connected via the fastening element 10E with a body or the like. It is understood that the fastening element 10E can also be arranged at a different location of the housing part 10 of the silencer 100.
  • the housing part 10 has a fluid channel which comprises a first channel segment 10A, in particular an inflow channel and a second channel segment 10B angled away from the first channel segment 10A, as well as a feed channel.
  • a fluid channel which comprises a first channel segment 10A, in particular an inflow channel and a second channel segment 10B angled away from the first channel segment 10A, as well as a feed channel.
  • FIG. 1 Within the feed channel 10B, an axially extending projection 10B-12 is visible.
  • fluid, in particular combustion air flows to the heater connected to the muffler 100.
  • FIG. 2 shows in a perspective view an insertion part 20 of the muffler 100.
  • the exact arrangement of the insertion part 20 within the housing part 10 will be explained in more detail.
  • the insertion part 20 comprises a nozzle 20A-1 provided with a nozzle 20A, which is integrally connected to a first disc 20B-1.
  • the first disk 20B-1 is located in the axial direction with respect to the nozzle opening 20A-1 of the nozzle 20A parallel to a second disk 20B-2 spaced from the first disk 20B-1.
  • the muffler 100 is connected to the heater.
  • the nozzle 20A represents in principle on the side of the insertion part 29 is an extension of the second channel segment 10B of the fluid channel.
  • a ridge 20G arranged in the installation situation on the underside of the insertion part 20 separates two sub-chambers 20E-1 and 20E-2 of a small resonator chamber 20E (of a second branch resonator R2) with a small volume from each other and at the same time ensures stability.
  • the smaller volume of the small resonator chamber 20E refers to the larger volume of a large resonator chamber 10C (a first branch resonator R1), and the branch resonators R1, R2 will be discussed in more detail.
  • a push-in shield 20F Disposed on the second disc 20B-2 is a push-in shield 20F which extends in the assembled state inside the muffler 100 in the axial direction, the function of the push-in shield 20F being discussed in more detail below.
  • a cylindrical wall 20C is provided on the inner diameter of the disks 20B-1 and 20B-2, and in the wall 20C in the radial direction, the axially extending nozzle port 20A-1 communicating holes 20D-1 and 20D -2 are arranged, which will also be discussed in more detail later. In FIG. 2 only one of the connection openings 20D-1 is visible.
  • the communication ports 20D-1, 20D-2 provide access to the small, lower volume sub-chambers 20E-1 and 20E-2 of the small resonator chamber 20E as described in the description of FIG. 10 will be explained in more detail.
  • FIG. 3 shows in a further perspective view of the lid 30 as a final element, which in the assembled state of the muffler 100 according to FIG. 5 closes the housing part 10 on one end, without the connecting opening S11 according to FIG. 7 close.
  • the housing part 10 is according to FIG. 5 in the assembled state by the insertion part 20 according to FIG. 2 closed, wherein the first disc 20B-1 of the insertion part 20 is flush with the edge of the housing part 10, as in FIG. 5 is shown in a slightly perspective side view of the muffler 100.
  • FIG. 4 shows to further explain the construction of the housing part 10 in yet another perspective view, a view into the interior of the housing part 10th
  • FIG. 4 shown position of the housing assembly 10 corresponds to the later installation situation of the muffler 100. It is clear that the supply channel 10B below and the fastener 10E are arranged laterally. It is also clear that the large resonator chamber 10 C is arranged in the installation situation of the muffler 100 above.
  • the viewing direction of the viewer in the interior of the housing part 10 is according to FIG. 4 Starting from the nozzle 20A directed towards the lid 30, wherein the lid 30 in FIG. 4 not mounted yet.
  • the housing part 10 comprises the slit-like inlet channel 10A, which is open on both sides and, in the assembled state, has a housing partial opening 10A-1 at one end and forms an inflow opening 10A-11, and at the other end in the assembled state to form a connection opening S11, as will be explained, is closed by the lid 30.
  • the housing part 10 further comprises the circular feed channel 10B, which is also initially open on both sides, and in the assembled state on one side by means of the lid 30 (see FIG. 7 ) is closed and is open on the other side facing the nozzle 20A, since there the insertion part 20 is inserted into the housing part 10, wherein the open nozzle opening 20A-1 forms the outflow opening 10B-11 for the fluid.
  • the circular feed channel 10B which is also initially open on both sides, and in the assembled state on one side by means of the lid 30 (see FIG. 7 ) is closed and is open on the other side facing the nozzle 20A, since there the insertion part 20 is inserted into the housing part 10, wherein the open nozzle opening 20A-1 forms the outflow opening 10B-11 for the fluid.
  • the housing part 10 has a third substantially circular resonator chamber opening 10C-1, which forms the access to the large resonator chamber 10C.
  • the large resonator chamber 10C forms a second branch resonator R2 of a plurality of sub-chambers 10C-I, 10C-II, 10C-III, as shown in FIG FIG. 9 is clarified.
  • FIG. 4 Furthermore, it is clear that the large resonator chamber 10C is closed on the bottom side.
  • the floor 10C-4 is in the assembled state, such as FIG. 5 in particular illustrated on the side of the lid 30.
  • the housing part 10 circumferentially has a widening 10C-2, which extends in the axial direction and whose length corresponds to the distance between the two discs 20B-1, 20B-2 of the insertion part 20.
  • the visible end face 10B-13 of the feed channel 10B also analogous to the expansion 10C-2 relative to the nozzle-side end face 10-1 of the housing part 10 is reset in the upper region, while it is continued in the lower region in the axial direction and the one flush end face 10A-12th to the end face 10-1 of the housing part 10 forms.
  • the lower part of the feed channel 10B with the end face 10A-12 and the shoulder 10C-21 with the end face 10B-13 of the feed channel 10B are designed to be flush in the assembled state, such as FIG. 6 clarified.
  • FIG. 4 Inside the large resonator chamber 10C is how FIG. 4 Further, a housing part plate 10D arranged, which also extends in the assembled state of the muffler 100 in the axial direction. It can be seen that the in FIG. 4 visible end face 10D-1 of the housing partial shield 10D is reset in the axial direction by an amount relative to the end face 10B-13 of the feed channel 10B, which will be discussed in more detail.
  • the housing part plate 10D is guided to the bottom 10C-4 of the large resonator 10C and thus already forms two sub-chambers, a third sub-chamber 10C-III and a sub-chamber 10C-II / 10C-I, which in the assembled state by the insertion plate 20F in two further individual chambers 10C-II and 10C-I is divided.
  • FIG. 5 shows the muffler 100 in a perspective view obliquely from above in the assembled state.
  • the arrow P1 shows the flow direction of the fluid in the inflow direction, wherein the inflow passage 10A forms an inflow opening 10A-11.
  • the arrow P2 shows the flow direction of the fluid in the outflow direction, wherein the nozzle 20A forms the outflow opening 10B-11.
  • the sound emission direction is opposite to the flow direction of the fluid.
  • the heater not shown is connected to the nozzle 20A.
  • the propagation of the sound waves L is in the FIGS. 7 and 10 shown with dashed lines L.
  • FIG. 6 shows a vertically extending in a plane section through the muffler 100 by the fastener 10E, which in FIG. 6 is arranged below. Across from FIG. 5 Thus, the muffler 100 is shown rotated by 90 ° down, so that the viewer looks at the muffler 100 from above with respect to the installation situation.
  • FIG. 7 shows a running in a vertical plane section through the muffler 100 right through the center of the muffler 100.
  • the muffler 100 in FIG. 7 has the same situation as FIG. 5 with the viewer now looking from the side of the muffler 100.
  • the insertion plate 20F also forms a distance at the front side with its free end opposite the bottom 10C-4 of the large resonator chamber 10C (FIG. FIG. 7 ), which will be discussed later ..
  • the feed channel 10B and the inflow channel 10A form a further resonator chamber in the manner of an angled resonator tube R.
  • the angled resonator tube R predominantly uses the functional principle of the absorption of sound waves L in the region of the straight feed channel 10B, since it is provided with an absorber element S1.
  • the supply channel 10B is in operative connection with the angled inflow channel 10A, it is seen in the direction of propagation of the sound waves L that the functional principle of the reflection is advantageously used as well.
  • the sound waves L propagate to the bend between the supply passage 10B and the inflow passage 10A and reach the U-shaped communication opening S11 between the supply passage 10B and the inflow passage 10A, and are strongly reflected on the inner wall of a lid 30, and then further into the inflow passage 10B in that they are reflected on the walls of the inflow channel 10A, 10B, whereby an attenuation of the sound waves L is achieved in an advantageous manner.
  • the resonator tube R attenuates sound frequencies in the acoustic wave range within a high-frequency frequency band by approximately 5 kHz, which is generated by the Volume of the resonator tube R, its cross section and its length and the arranged in the resonator tube R1 internals, such as the arranged first absorber element S1 and the absorber material depends.
  • an open-celled polyurethane foam based on polyester [polyester-based PU foam] is used as an absorber material for the first absorber element S1 in the resonator tube R.
  • the open-cell PU foam forms cell-like pores, which provide for reflection of the sound waves L in the pores for damping the sound waves L in the high-frequency frequency range by about 5 kHz around. It has been found that for the damping in the resonator tube R, a polyurethane foam based on polyester with a bulk density of about 57 kg / m 3 (+/- 5 kg / m 3 ) according to ISO 845 is particularly suitable.
  • FIGS. 6 and 7 illustrated how the first absorption element S1 within the feed channel 10B, here cylindrical, is arranged in FIG. 8 is shown as a detail.
  • the absorption element S1 extends in its longest extent from the cover 30 to the first disc 20B-2 of the insertion part 20 and is thereby easily positionable in the axial direction within the muffler 100.
  • the absorption element S1 is advantageously prior to installation a lying in a plane mat predeterminable thickness of about 5 -10 mm, in particular 6 mm, which is rolled up for installation to the cylindrical member, so that the axially extending end faces to each other lie.
  • a contact zone S13 forms (FIG. FIGS. 6 ) extending at the axially extending projection 10B-12 (FIG. FIGS. 1 and 6 ), so that the absorbing member S1 is uniquely positioned in the feeding channel 10B and secured against twisting at the same time. This solution is in FIG. 9 also recognizable.
  • the absorption element S1 according to FIG. 8 has at each end a segment-like cutout S11, S12, as seen in the flow direction of the fluid, the first segment-like Section S11 forms the fluid and sound transmitting connection opening S11 between the inflow passage 10A and the supply passage 10B, as in FIG. 7 is clearly visible.
  • the second segment-like cutout S12 forms a radially outgoing sound-transmitting connection opening S12 between the inflow channel 10A and the large resonator chamber 10C.
  • This connection opening S12 takes place almost no fluid exchange, that is, the fluid does not flow into the large resonator 10C.
  • FIG. 9 first shows for further explanation a running in a vertical plane section transverse to the axial extent of the muffler 100, wherein the section in the region of the second segment-like cutout S12 of the first absorption element S1 analogous to FIG. 4 is laid.
  • FIG. 9 and FIG. 4 differ in that in FIG. 9 in contrast to FIG. 4 the insertion part 20 is already inserted into the housing part 10 and the first absorption element S1 is already inserted.
  • FIG. 9 As a result, the sectional area of the insertion panel 20F in the area of the segment-like cutout S12 and the sectional area of the absorption element S1 are visible.
  • the insertion plate 20F is inserted with its extending in the axial direction outer end edge in a groove 10C-3, which also in FIG. 7 at least partially visible.
  • the insertion part 20 is advantageously positioned clearly within the large resonator chamber 10C and at the same time seals against the wall of the resonator chamber 10C.
  • the insertion part 20 is secured against rotation within the resonator 10C.
  • FIG. 9 shown section is that through the insertion plate 20F of the insertion part 20 within the resonator chamber 10C, three sub-chambers 10C-I; Form 10C-II and 10C-III. It has been proven by experiments that it is advantageous that the cross sections of the chambers 10C-I; I0C-II and I0C-III are formed substantially equal in size to effect an efficient sound attenuation.
  • the fluid flows in FIG. 9 in the direction of the viewer, while the sound or the sound wave propagates into the feed channel 10B, that is to say into the sheet plane, and radially into the large resonator chamber 10C via the segment-like cutout S12.
  • the resonator chamber 10C with the three large chambers 10C-I; 10C-II and 10C-III forms a resonator tube R of three adjacent large chambers 10C-I; 10C-II and 10C-III, which are interconnected by two connection openings A1, A2.
  • the first connection opening A1 ( FIG. 7 ) is formed by the gap between the bottom 10C-4 of the large resonator chamber 10C and the free end of the insertion shield 20F.
  • connection opening A2 is formed between the end face 10D-1 of the housing partial shield 10D within the resonator chamber 10C and the wall of the second disc 20B-2 of the insertion shield 20F facing the resonator chamber 10C. It has been found that it is advantageous if the cross sections of the connection openings A1, A2 are of substantially equal size, as in the exemplary embodiment shown, in order to bring about efficient sound damping.
  • connection openings A1, A2 are substantially the cross sections of the chambers 10C-I; 10C-II and 10C-III correspond to a highly effective sound dissipation within the interconnected chambers 10C-I; To reach 10C-II and 10C-III.
  • the optimal overall length of the resonator tube R was determined by special experiments using a prototype.
  • the opening size of the connection opening S12 of the segment-like section of the first absorption element S1 was also determined by special experiments by means of the prototype, as will be explained.
  • FIG. 10 shows for further explanation of the muffler 100 extending in a vertical plane section transverse to the axial extent of the muffler 100, wherein the section is in the region between the two discs 20B-1 and 20B-2 of the insertion part 20.
  • the communication holes 20D-1 and 20D-2 are visible to the sub-chambers 20E-1 and 20E-2 of the small resonator chamber 20E.
  • the second branch resonator R2 is designed such that it uses the principle of operation of the combination of absorption and reflection.
  • the two sub-chambers 20E-1 and 20E-2 of the small resonator chamber 20E are separated from each other by an upper vertical divider 20H.
  • an upper vertical divider 20H is formed between the two disks 20B-1 and 20B-2.
  • the upper vertical divider 20H is starting from the center M1 of the feed channel 10B in FIG. 10 formed in the vertical direction only so long that it does not reach the inner wall of the expansion 10C-2 of the resonator chamber opening 10C-1, so that the two sub-chambers 20E-1 and 20E-2 are still connected to each other in the upper area.
  • the second absorption element S2 forms two wing-like elements S21 and S22 corresponding to the inner contour of the sub-chambers 20E1 and 20E-2, so that the elements S21 and S22 in the two sub-chambers 20E-1 and 20E-2 can be arranged accurately.
  • the second absorption element S2, viewed in the axial direction, has a thickness of approximately 5 -10 mm, in particular 5 mm.
  • the small resonator chamber 20E thus forms, viewed in the propagation direction of the sound waves L, first a resonator chamber without absorption element S2 and then a resonator chamber with the absorption element S2, wherein the small resonator chamber 20E is formed from the two interconnected subcompartments 20E-1 and 20E-2.
  • the embodiment described and the absorbent internals in the small resonator chamber 20E ensure that the functional principle of the combination of reflection and absorption is utilized by the two chambers 20E-1 and 20E-2 first by reflection and then by the absorber element S2 by absorption becomes.
  • the small resonator chamber 20E is formed relatively large by the eccentric design of the muffler 100 compared to other mufflers from the prior art, so that the damping effect compared to conventional mufflers is further improved.
  • the center point M1 of the axial center axis of the second housing part opening 10B-1 which constitutes the supply passage 10B is positioned as shown in FIG FIG. 10 with respect to the center M2 of the axial center axis of the small resonator chamber 20E eccentrically.
  • connection openings 20D-1 and 20D-2 respectively in the radial direction, wherein it has been found that the segment-like connection openings 20D-1, 20D-2 are advantageously in an angular range between 60 ° to 150 ° and in particular in each case approximately 120 ° be to effect an efficient attenuation of the sound waves L.
  • the small resonator chamber 20E designed as branch resonator R2 likewise dampens sound frequencies in the acoustic wave range within a high-frequency frequency band by approximately 5 kHz, that of the volume of the small resonator chamber 20E, its chamber cross-section, the cross-sections of the connection openings 20D-1, 20D-2 and the in the Branch resonator R2 arranged internals, such as the arranged second absorber element S2 and the absorber material depends.
  • an open-celled polyurethane-based polyurethane foam [polyester-based polyurethane foam] is also used.
  • the open-cell PU foam of the second absorber element S2 likewise forms cell-like pores, which provide for reflection of the sound waves L in the pores for damping the sound waves L in the high-frequency frequency range by approximately 5 kHz. It has been found that for cushioning in the resonator chamber 20E, a polyester-based polyurethane foam having a bulk density of about 120 kg / m 3 (+/- 12 kg / m 3 ) according to ISO 845 is particularly suitable.
  • both in the resonator tube R and in the second branch resonator R2 sound waves L in the high-frequency frequency range are attenuated by approximately 5 kHz, but different foams are used. It has been found according to the invention that the further different boundary conditions, such as respectively different volumes, respectively different cross sections of the resonator chambers and respectively different cross sections of the connection openings, require different foams in order to match the desired high-frequency frequency ranges by approximately 5 kHz in the described manner.
  • both in the resonator tube R and in the second branch resonator R2 sound waves L in the higher-frequency range are attenuated by approximately 5 kHz.
  • high-frequency intake noise which is known in particular by a turbine-like noise of an intake fan of the heater, is effectively damped in the small resonator chamber 20E near and through the second branch resonator R2 away from the port side intake port of the heater.
  • the FIGS. 12 to 14 The prototype P100 differs from the series type 100 on the one hand in that in the third chamber 10C-III a displaceable in the axial direction volume controller 10V is arranged, which consists of the housing part 10 is pulled out so that it is displaceable on both sides in the axial direction.
  • the volume regulator 10V By means of the volume regulator 10V, the optimum overall length of the large resonator chamber 10C was determined in order to bring about a highly efficient damping of the sound waves L.
  • FIG. 12 is illustrated by the arrow P4, as the volume controller 10V is reciprocated in corresponding experiments within the third chamber 10C-III to at given Cross sections of the chambers 10C-I, 10C-II and 10C-III and at predetermined cross sections of the overflow or connection openings A1, A2, the optimal length of the large resonator chamber 10C formed from the sub-chambers 10C-I, 10C-II and 10C-III most efficient attenuation of the sound waves L to determine.
  • the first absorption element S1 has likewise been pulled out of the housing part 10, so that by rotation in accordance with the arrow P3 in FIG. 14 it is possible to rotate the segment-like opening S12 of the first absorption element S1 with respect to the first chamber 10C-I of the large resonator chamber 10C.
  • the necessary open cross-section of the segment-like cutouts S11 and S12 of the first absorption element S1 could thus be determined by corresponding experiments, in which a highly efficient attenuation of the sound waves entering the large resonator chamber 10C and deflected and reflected between the feed channel 10B and the inflow channel 10A through the connection opening L is feasible.
  • the opening angles of the segment-like cutouts S11 and S12 and also the width of the cutouts S11, S12 necessary in the axial direction were determined.
  • volume regulator 10V By the volume regulator 10V, the length of the resonator 20E and the first absorption element S1, the size of the connection opening S12 to the large resonator 10C is variable and adjustable within the planned controlled system.
  • Volumetric regulator 10V and rotatable first absorption element S1 are no longer prototype components in such an embodiment, but instead represent series components.
  • the described solution according to the invention also has the advantage that the body of the muffler is formed only of three simple components, the housing part 10, the insertion part 20 and the lid 30.
  • the described insertion of the insertion part 20 in the housing part 10 and placing the lid 30 can be assembled without error by simple installation of the body of the muffler 100 from the worker.
  • the lid 30 also has appropriate provisions for error-free installation.
  • the complementation with the absorption elements S1 and S2 is likewise simple, wherein the absorber elements S1 and S2 can be easily and securely positioned by the operator before assembly of the body into the feed channel 10B or into the small resonator chamber 20E.
  • the angled resonator tube R is already applied in the housing part 10.
  • the material requirement is small and the space required for reducing the intake noise in the resonator chambers 10C, 20E is particularly large compared to conventional silencers, as the explained eccentric design has been selected.
  • Another advantage is that an efficient reduction of the noise effect of intake noise is also achieved by the first absorption element S1 in the feed channel 10B, since it has been found that the deflection of the inflow channel 10A into the feed channel 10B also has a reducing and damping effect Sound is effected.
  • the inlet channel 10A which is arranged in the installation situation of the muffler 100 on the underside, acts as a collecting space for condensate possibly occurring within the muffler 100.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Multimedia (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust Silencers (AREA)
EP15151861.0A 2014-02-12 2015-01-20 Silencieux d'admission Active EP2913513B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102014202538.9A DE102014202538A1 (de) 2014-02-12 2014-02-12 Ansauggeräuschdämpfer

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EP2913513A1 true EP2913513A1 (fr) 2015-09-02
EP2913513B1 EP2913513B1 (fr) 2018-08-08

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DE (1) DE102014202538A1 (fr)

Cited By (2)

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CN109339997A (zh) * 2018-12-04 2019-02-15 南京工程学院 一种连续可变谐振腔的内燃机进气系统
CN110617121A (zh) * 2018-06-19 2019-12-27 现代自动车株式会社 易于排出冷凝液的消声器

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016215176A1 (de) * 2016-08-15 2018-02-15 Elringklinger Ag Resonanzvorrichtung und Verfahren zur Herstellung einer Resonanzvorrichtung

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Publication number Priority date Publication date Assignee Title
FR2392228A1 (fr) * 1977-05-27 1978-12-22 Honda Motor Co Ltd Silencieux pour moteurs a combustion interne
DE102008020721A1 (de) * 2008-04-23 2009-10-29 J. Eberspächer GmbH & Co. KG Schalldämpferbaugruppe für eine Abgasleitung
DE102010049578A1 (de) 2010-10-26 2012-04-26 Webasto Ag Schalldämpfereinrichtung für eine Fluidleitung sowie Heizgerät mit einer Schalldämpfereinrichtung

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Publication number Priority date Publication date Assignee Title
US5952625A (en) * 1998-01-20 1999-09-14 Jb Design, Inc. Multi-fold side branch muffler
DE202010012541U1 (de) * 2010-09-13 2011-12-15 Aerzener Maschinenfabrik Gmbh Schalldämpfender Ansaugtopf
DE102010037540A1 (de) * 2010-09-15 2012-03-15 Contitech Mgw Gmbh Fluidleitung mit Resonator
CN102644531B (zh) * 2011-02-16 2015-02-25 曼·胡默尔有限公司 谐振系统

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2392228A1 (fr) * 1977-05-27 1978-12-22 Honda Motor Co Ltd Silencieux pour moteurs a combustion interne
DE102008020721A1 (de) * 2008-04-23 2009-10-29 J. Eberspächer GmbH & Co. KG Schalldämpferbaugruppe für eine Abgasleitung
DE102010049578A1 (de) 2010-10-26 2012-04-26 Webasto Ag Schalldämpfereinrichtung für eine Fluidleitung sowie Heizgerät mit einer Schalldämpfereinrichtung

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110617121A (zh) * 2018-06-19 2019-12-27 现代自动车株式会社 易于排出冷凝液的消声器
CN110617121B (zh) * 2018-06-19 2022-08-02 现代自动车株式会社 易于排出冷凝液的消声器
CN109339997A (zh) * 2018-12-04 2019-02-15 南京工程学院 一种连续可变谐振腔的内燃机进气系统
CN109339997B (zh) * 2018-12-04 2023-04-07 南京工程学院 一种连续可变谐振腔的内燃机进气系统

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DE102014202538A1 (de) 2015-08-13

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