EP2446128B1 - Elément d isolation acoustique tubulaire - Google Patents

Elément d isolation acoustique tubulaire Download PDF

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Publication number
EP2446128B1
EP2446128B1 EP20100728196 EP10728196A EP2446128B1 EP 2446128 B1 EP2446128 B1 EP 2446128B1 EP 20100728196 EP20100728196 EP 20100728196 EP 10728196 A EP10728196 A EP 10728196A EP 2446128 B1 EP2446128 B1 EP 2446128B1
Authority
EP
European Patent Office
Prior art keywords
exhaust system
insulating element
connecting piece
central axis
section
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.)
Not-in-force
Application number
EP20100728196
Other languages
German (de)
English (en)
Other versions
EP2446128A1 (fr
Inventor
Tobias Pfeffer
Bernd Fuhrmann
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.)
Tenneco GmbH
Original Assignee
Tenneco GmbH
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Filing date
Publication date
Application filed by Tenneco GmbH filed Critical Tenneco GmbH
Publication of EP2446128A1 publication Critical patent/EP2446128A1/fr
Application granted granted Critical
Publication of EP2446128B1 publication Critical patent/EP2446128B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/08—Other arrangements or adaptations of exhaust conduits
    • 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
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/18—Construction facilitating manufacture, assembly, or disassembly
    • F01N13/1805—Fixing exhaust manifolds, exhaust pipes or pipe sections to each other, to engine or to vehicle body
    • F01N13/1811—Fixing exhaust manifolds, exhaust pipes or pipe sections to each other, to engine or to vehicle body with means permitting relative movement, e.g. compensation of thermal expansion or vibration
    • F01N13/1816—Fixing exhaust manifolds, exhaust pipes or pipe sections to each other, to engine or to vehicle body with means permitting relative movement, e.g. compensation of thermal expansion or vibration the pipe sections being joined together by flexible tubular elements only, e.g. using bellows or strip-wound pipes
    • 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
    • F01N2260/00—Exhaust treating devices having provisions not otherwise provided for
    • F01N2260/10—Exhaust treating devices having provisions not otherwise provided for for avoiding stress caused by expansions or contractions due to temperature variations

Definitions

  • the invention relates to an exhaust system for an internal combustion engine for connection to a manifold.
  • the exhaust system consists of at least one in the flow direction middle or immediately after the manifold provided first portion and a subsequent flow in the second portion, the two sections are connected to each other via a mechanical decoupling element, wherein in the flow direction before the first section or in the first section a single-walled and self-supporting element is integrated into the exhaust system, wherein the element has at least one inner nozzle and at least one radially outwardly offset to a central axis outer nozzle, and in each case one between the two nozzles arranged connecting the two nozzles in the direction the center axis is provided in the length compressed center part, which forms a U or S-blow in cross section.
  • the element is formed as an acoustic insulating element and formed of sheet metal or metal casting and in a direction along the workpiece continuously or suddenly increasing wall thicknesses between 1 mm and 2.8 mm, in particular between 1.2 mm and 1.9 mm.
  • This type of structure-borne noise can be caused by damping elements in the exhaust system or by large impedance jumps be reduced in components of an exhaust system directly in the structure.
  • Impedance jumps are in accordance with the DE 10 2006 040 980 A1 achieved with a damping element having radial extensions of the cross section, which are placed in the manner of a pipe clamp on the pipe.
  • the invention has for its object to dampen resonant vibrations in the range above 600 Hz in an exhaust system by more than 15 dB and at the same time form the exhaust system sufficiently rigid and self-supporting and permanently gas-tight.
  • the element is formed as an acoustic insulating element and is formed from sheet metal or metal casting and in one direction along the workpiece continuous or increasing wall thickness suddenly increasing between 1 mm and 2.8 mm, in particular between 1.2 mm and 1, 9 mm.
  • the achieved by a decreasing wall thickness insulating effect has an advantageous effect especially in the frequency range above 2000 Hz to 6000 Hz. This is advantageous in that when calibrating the diameter of the outer nozzle from a smaller on a greater degree the wall thickness becomes thinner anyway.
  • a cylindrical tube having a base diameter matching the inner neck on the exit side would be up-calibrated to the dimension of the diameter for the outer neck.
  • tubular acoustic insulation element in the direction of the central axis as short as possible and thus to achieve sufficient bending stiffness in order to be used as a self-supporting acoustic insulation element can.
  • the acoustic insulation element does not have to fulfill the function of a mechanical decoupling and can be designed relatively rigid.
  • the insertion depth is between 5 mm and 16 mm, maximum 30 mm.
  • the insulating property can be further improved if the acoustic insulating element is connected directly in front of or on the component which ultimately generates the resonances in the continuing components.
  • the inner radius and the outer radius advantageously have a dimension of between 6 mm and 30 mm, but the two radii have a different dimension relative to each other.
  • the inner nozzle is arranged offset in the direction of the central axis to the outer nozzle and / or cover the two sockets to the extent of an insertion depth e between 5 mm and 30 mm.
  • the length of the insertion depth e is the extent to which the outer neck projects beyond the inner neck in the direction of the central axis. At this length, both the pipe part provided between the inner radius and the outer radius and the two radii themselves must be included in the dimension of the insertion depth e. The shorter the insertion depth e, the larger the acoustic insulation achieved with the element.
  • the basic diameter of the inner neck is at least 20% to a maximum of 40% smaller than the diameter of the outer neck.
  • the insulation can be significantly influenced by the two end geometries of the two nozzles, since the vibration behavior in the transition from a small to a large nozzle deviates significantly from the vibration behavior that would be achieved if the inner nozzle would have the same measure as the inlet nozzle the outer nozzle as outlet nozzle.
  • a middle part connecting the two tubular connecting pieces has at least one outer radius adjoining the outer connecting piece and an inner radius adjoining the inner connecting piece and a tube part connecting the two radii, wherein the tube wall of the Pipe part is arranged in parallel or at an angle a between 2.5 ° and 15 ° to the central axis.
  • connection geometry can be increased or decreased by varying the angle a for both the inner nozzle and the outer nozzle.
  • the acoustic insulation element in the flow direction S after the inner nozzle has a reduced diameter compared to the base diameter.
  • a kind of taper is formed in the transition from the inner nozzle to the central part, are influenced by the particular existing vibrations in the exhaust pipe with respect to the insulation.
  • the acoustic insulation element is formed from a calibrated pipe section with an input side base diameter between 45 mm and 85 mm and an output side diameter between 55 mm and 115 mm and an absolute in the direction of the central axis length between 230 mm and 420 mm.
  • the ratio of basic diameter to diameter significantly influences the insulation properties of the element.
  • the acoustic insulating element is integrated in an end wall of a sheet metal housing for a filter or a converter or a silencer, wherein at least a part of the end wall in the radial direction to the central axis at the inner nozzle and / or connects to the outer neck.
  • the integration of the Dämmelements is made possible in a present in the exhaust systems component to which an exhaust pipe would be connected anyway.
  • the integration in an end wall also has the advantage that the overall length and thus the rigidity of the element can be increased, which has a significant effect on the insulation property.
  • the acoustic insulating element is arranged at an outlet of a housing for a turbocharger. Since turbochargers contribute a relatively large contribution to the resulting in the exhaust system structure-borne noise in the range between 600 Hz and 6 kHz, positioning of such a Dämmelements immediately after the turbocharger is of great importance, also can be arranged by such an arrangement in the oversized nozzle easier to integrate larger diameter in the geometry of an exhaust system, because this outer nozzle connects directly to the housing and a possibly necessary reduction of the diameter is not necessary again to the extent of the provided for the other exhaust pipes diameter of the inner nozzle.
  • the use of an acoustic Dämmelements for an exhaust system for acoustic insulation of an exhaust system in the frequency range between 600 Hz and 6 kHz be advantageous if the acoustic insulation element has at least one inner nozzle and at least one radially outwardly offset to a central axis outer nozzle, in each case one arranged between the two stubs, connecting the two stubs compressed middle part is provided, which forms a U- or S-blow in cross-section and is formed from single sheet metal or metal casting and in a direction along the workpiece continuously or suddenly increasing wall thicknesses between 1 mm and 2.8 mm, in particular between 1.2 mm and 1.9 mm.
  • FIG. 1 is an exhaust system 4 consisting of a first portion 41 and a second portion 42 shown.
  • the first portion 41 is formed of a converter 45 and on both sides of the converter 45 respectively connected exhaust pipes 47.
  • the second section 42 consists of a particulate filter 44 and a muffler 46, wherein the particulate filter 44 and the muffler 46 are connected to each other via an exhaust pipe 47.
  • an exhaust pipe 47 is also provided, to which a mechanical decoupling element 40 connects, via which the two sections 41, 42 are interconnected.
  • the mechanical decoupling element 40 serves essentially to ensure a certain freedom of movement of the exhaust system 4 over its entire length.
  • the entire exhaust system 4 is connected via an acoustic insulating element 1 to an outlet opening of a turbocharger 5, which further connects the exhaust system 4 via the manifold 3 with the engine 2.
  • the vibrations introduced via the exhaust gas flow and the turbocharger 5 into the exhaust system 4 are significantly attenuated via the acoustic insulating element 1 in the range between 600 Hz and 6 kHz, so that the body radiation of the converter 45, of the particulate filter 44 and of the silencer 46 is reduced.
  • the vibrations still present in the first part 41 of the exhaust system 4 are also influenced and partially damped by the mechanical decoupling element 40, so that the combination of the acoustic insulation with the insulating element 1 and the vibration damping with the mechanical decoupling element 40 reduces the structure-borne noise in the second part 42 causes the exhaust system 4.
  • FIG. 2 is a schematic cross section of an acoustic Dämmelements 1 shown with an S-beat 120.
  • the acoustic insulating element 1 has an inner nozzle 10 and a radially outer to the central axis 13 outer nozzle 15.
  • the outer nozzle 15 is in the axial direction to the central axis 13 via the inner nozzle 10 via.
  • the connection of the outer nozzle 15 with the inner nozzle 10 forms a central part 12 with an S-beat 120 in cross section.
  • the middle part 12 is formed by the outer radius 152 adjoining the outer connecting piece 15 and the inner radius 102 adjoining the inner connecting piece 10 and a tubular part 14 connecting the two radii 102, 152.
  • the projection of the outer nozzle 15 via the inner nozzle 10 is referred to as insertion depth e, which is formed in the sum of the dimension of the tube part 14 and the two radii 102, 152.
  • the length L of Dämmelements 1 in the direction of the central axis 13 is measured from the inlet opening on the inner nozzle 10 to the outlet opening at the outer nozzle 15th
  • FIG. 2 connects to the inner nozzle 10 in the flow direction S the insulating element 1 preceded by an exhaust pipe 47 at.
  • a schematically illustrated exhaust element 48 connected to the insulating element 1.
  • Examples of such exhaust elements 48 are represented by sheet metal housing 43.
  • the natural frequency can be shifted in the range of 400 Hz to 700 Hz compared to a cylindrical exhaust pipe, with a positive insulation from 600 Hz or 900 HZ is achievable. Furthermore, a maximum insulation of 30 dB between 600 Hz 6 kHz can be realized.
  • FIG. 3 shows a particular embodiment of the S-beat 120, in which the pipe section 14 provided between the two radii 102, 152 is employed with respect to the central axis 13 by an angle a. It can be seen that the tube part 14 is thus not arranged parallel to the central axis 13, as for example in FIG FIG. 3 is shown.
  • the angle a By varying the angle a, both the base diameter 101 of the inner nozzle 10 and the diameter 151 of the outer nozzle 15 to each other can be varied.
  • the acoustic insulating element 1 is manufactured and calibrated from a cylindrical tube which has a tube diameter substantially equal to the basic diameter 101 corresponds to the inner nozzle 10, the outer nozzle 15 is calibrated by a certain amount.
  • the insertion depth e by the dimensions of the two radii 102, 152 and the length L of the pipe part a in the direction of the central axis 13 prevail.
  • FIG. 4 is one opposite FIG. 3 modified embodiment shown in which in the region of the inner radius 102 of the inner diameter 103 is reduced relative to the base diameter 101 of the inner nozzle 10.
  • a compression of the exhaust gas flow is thus achieved and at the same time influence on the running in the inner nozzle 10 sound waves.
  • FIG. 5 shows a preferred embodiment in which the acoustic insulation element 1 is integrated into an end wall 430 of a sheet metal housing 43 of an exhaust system 4.
  • the end face 430 is inserted in the direction of the central axis 13 in the sheet metal housing 43, so that a mounting of the insulating element 1 in the end wall 430 before winding the housing is possible.
  • the insulating element 1 is welded to the outer nozzle 15 in a corresponding opening of the end wall 430.
  • the opposite of the inner nozzle 10 in diameter 151 substantially larger outer nozzle 15 forms, so to speak, the output side for the flowing in the flow direction S exhaust, so that the exhaust gas or the exhaust stream after the insulating element 1 on in the sheet metal housing 43 propagates in the radial direction.
  • This also has the advantage that by reducing the diameter 151 of the outer nozzle 15, if necessary, with a continuation within the exhaust pipe, which has approximately the same diameter as the inner nozzle 10, a taper can be avoided.
  • FIG. 6 is a similar embodiment as in FIG. 5 with regard to the positioning in an end wall 430 of a sheet-metal housing 43.
  • the S-shaped insulating element 1 is arranged in the radial direction to the central axis 13 approximately in the middle of the end wall 430, so starting from the mounted in the end wall 430 exhaust pipe 47 initially a first part of the end wall 430 in the radial direction a connection to Dämmelement 1 forms and to the insulating element 1 in the radial direction then a second part of the end wall 430, the connection and the connection to the circumferentially arranged sheet metal housing 43 represents.
  • the inner nozzle 10 and the outer nozzle 15 is formed extremely short and the adjacent components are not arranged as in the previous embodiments in the axial direction to the central axis 13 adjacent to the insulating element 1 but in the radial direction.
  • FIG. 7 is one too FIG. 6 similar embodiment shown, in which the insulating element 1 does not have an S-shaped cross-section but a U-shaped cross section 120.
  • the U-shaped insulating element 1 has only a radius, which is referred to as inner radius 102 and can be used only in the areas due to the geometric conditions in which connect the other components in the radial direction to the central axis 13 to the insulating element 1.
  • FIG. 8 an embodiment is shown, in which the insulating element 1 forms a connection between an exhaust pipe 47 and a sheet metal housing 43, wherein the sheet metal housing 43 has a conical end face.
  • the larger diameter 151 of the outer nozzle 15 with respect to the inner nozzle 10 is advantageously carried out via the connection to the sheet metal housing 43, so that a tapering of the diameter 152 of the outer nozzle 15 to a smaller extent is not necessary.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust Silencers (AREA)
  • Pipe Accessories (AREA)

Claims (9)

  1. Système d'échappement(4), formé de plusieurs composants pour un moteur à combustion (2) pour le raccordement à un collecteur (3), avec au moins un premier tronçon (41) formant un début dans le sens d'écoulement S et un deuxième tronçon (42) qui y est adjacent dans le sens d'écoulement S, les deux tronçons (41, 42) étant raccordés l'un à autre par le biais d'un élément de découplage (40) mécanique, un élément (1) à paroi unique et autoportant étant intégré dans le système d'échappement (4) en amont du premier tronçon dans le sens d'écoulement S ou dans le premier tronçon (41), l'élément (1) présentant au moins une tubulure (10) intérieure et au moins une tubulure (15) extérieure décalée vers l'extérieur dans la direction radiale par rapport à un axe central (13), et une partie centrale (12) comprimée dans la longueur (L) en direction de l'axe central (13), raccordant les deux tubulures (10, 15) et disposée ente les deux tubulures (10, 15), étant respectivement prévue, et cette partie centrale (12) forme une courbure (120) dont la section transversale est en U ou en S, caractérisé en ce que l'élément est constitué en tant qu'élément isolant (1) acoustique et est formé en tôle ou en métal coulé et présente, dans une direction le long de la pièce, des épaisseurs de paroi augmentant de façon continue ou brusque entre 1 mm et 2,8 mm, en particulier entre 1,2 mm et 1,9 mm.
  2. Système d'échappement (4) selon la revendication 1, caractérisé en ce que, dans l'élément isolant (1), la tubulure (10) intérieure est disposée de façon décalée en direction de l'axe central (13) par rapport à la tubulure (15) extérieure et/ou les deux tubulures (10, 15) se chevauchent sur une longueur correspondant à la dimension d'une profondeur d'enfichage (e) entre 5 mm et 30 mm.
  3. Système d'échappement (4) selon la revendication 1 ou 2, caractérisé en ce que, dans l'élément isolant (1), le diamètre de base de la tubulure (10) intérieure est inférieur d'au moins 20 % et au maximum de 40 % au diamètre (151) de la tubulure (15) extérieure.
  4. Système d'échappement (4) selon une des revendications précédentes, caractérisé en ce que, dans l'élément isolant (1), la partie centrale (12) raccordant les deux tubulures (10, 15) de forme tubulaire présente au moins un rayon (152) extérieur adjacent sur la tubulure (15) extérieure et un rayon (102) intérieur adjacent sur la tubulure (10) intérieure ainsi qu'une partie de tube (14) raccordant les deux rayons (102, 152), la paroi de tube de la partie de tube (14) étant disposée parallèlement à l'axe central (13) ou bien en formant avec ce denier un angle a entre 2,5 ° et 15 °.
  5. Système d'échappement (4) selon une des revendications précédentes, caractérisé en ce que l'élément isolant (1) acoustique présente, en aval de la tubulure (10) intérieure dans le sens d'écoulement S, un diamètre intérieur (103) réduit par rapport au diamètre de base (101).
  6. Système d'échappement (4) selon une des revendications précédentes, caractérisé en ce que l'élément isolant (1) est formé d'un morceau de tube calibré, ayant un diamètre de base (101) côté entrée compris entre 45 mm et 85 mm, et un diamètre (151) côté sortie compris entre 55 mm et 115 mm, ainsi qu'une longueur (1) absolue dans la direction de l'axe central (13) comprise entre 230 mm et 420 mm.
  7. Système d'échappement (4) selon une des revendications précédentes, caractérisé en ce que l'élément isolant (1) acoustique est intégré dans une paroi frontale (430) d'un carter en tôle (43) pour un filtre à particules (44) ou un convertisseur (45) ou un silencieux (46), au moins une partie de la paroi frontale (430) étant, dans la direction radiale vers l'axe central (13), adjacente à la tubulure (10) intérieure et/ou à la tubulure (15) extérieure.
  8. Système d'échappement (4) selon une des revendications précédentes 1 à 7, caractérisé en ce que l'élément isolant (1) acoustique est disposé à une sortie d'un carter pour un turbocompresseur (5).
  9. Utilisation d'un élément isolant (1) acoustique pour un système d'échappement (4) pour l'isolation acoustique d'un système d'échappement (4) dans la plage de fréquences entre 600 Hz et 6 kHz, l'élément isolant (1) acoustique présentant au moins une tubulure (10) intérieure et au moins une tubulure (15) extérieure décalée vers l'extérieur dans la direction radiale par rapport à un axe central (13), une partie centrale (12), comprimée dans la longueur (L) en direction de l'axe central (13), raccordant les deux tubulures (10, 15), disposée entre les deux tubulures (10, 15), étant prévue respectivement, cette partie centrale (12) forme une courbure (120) dont la section transversale est en U ou en S, et l'élément isolant (1) acoustique est formé avec une paroi unique en tôle ou métal coulé et présente, dans une direction le long de la pièce, des épaisseurs de paroi augmentant de façon continue ou brusque entre 1 mm et 2,8 mm, en particulier entre 1,2 mm et 1,9 mm.
EP20100728196 2009-06-23 2010-06-23 Elément d isolation acoustique tubulaire Not-in-force EP2446128B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009030258 2009-06-23
PCT/EP2010/058952 WO2010149723A1 (fr) 2009-06-23 2010-06-23 Elément d’isolation acoustique tubulaire

Publications (2)

Publication Number Publication Date
EP2446128A1 EP2446128A1 (fr) 2012-05-02
EP2446128B1 true EP2446128B1 (fr) 2015-05-06

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP20100728196 Not-in-force EP2446128B1 (fr) 2009-06-23 2010-06-23 Elément d isolation acoustique tubulaire

Country Status (5)

Country Link
US (1) US8443933B2 (fr)
EP (1) EP2446128B1 (fr)
CN (1) CN102482979A (fr)
BR (1) BRPI1010067A2 (fr)
WO (1) WO2010149723A1 (fr)

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US20150061174A1 (en) * 2013-08-28 2015-03-05 Volvo Car Corporation Sound isolation unit and production method thereof
DE102015108495A1 (de) 2015-05-29 2016-12-01 Eberspächer Exhaust Technology GmbH & Co. KG Abgasschalldämpfer zum Quereinbau in ein Fahrzeug
DE102016123114A1 (de) * 2016-11-30 2018-05-30 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Fahrzeugkomponente
US11639676B2 (en) 2019-06-17 2023-05-02 Tenneco Automotive Operating Company Inc. Vehicle exhaust system
US11549422B1 (en) 2021-12-06 2023-01-10 Tenneco Automotive Operating Company Inc. Exhaust system for a combustion engine including a flow distributor

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Also Published As

Publication number Publication date
US8443933B2 (en) 2013-05-21
EP2446128A1 (fr) 2012-05-02
BRPI1010067A2 (pt) 2016-03-15
CN102482979A (zh) 2012-05-30
US20120160600A1 (en) 2012-06-28
WO2010149723A1 (fr) 2010-12-29

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