EP2446128A1 - Rohrförmiges akustisches dämmelement - Google Patents
Rohrförmiges akustisches dämmelementInfo
- Publication number
- EP2446128A1 EP2446128A1 EP10728196A EP10728196A EP2446128A1 EP 2446128 A1 EP2446128 A1 EP 2446128A1 EP 10728196 A EP10728196 A EP 10728196A EP 10728196 A EP10728196 A EP 10728196A EP 2446128 A1 EP2446128 A1 EP 2446128A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- exhaust system
- central axis
- insulating element
- diameter
- nozzle
- 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
Links
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 vorgesehe ⁇ NEN first section and a subsequent thereto in the flow direction second portion, wherein the two sections are connected to each other via a mechanical decoupling element.
- decoupling element By decoupling element, the exhaust system is mecha ⁇ cally decoupled so that a certain flexibility is provided via the vehicle's length.
- flexible connecting elements such as shaft pipes or flexible hoses between two sections of the exhaust system are used.
- Such flexible acoustic damping elements are described in ⁇ example in US 5,456,291 A and in EP 1 431 538 Bl.
- This type of structure-borne noise can be reduced by damping elements in the exhaust system or by large impedance jumps in components of an exhaust system directly in the structure.
- Impedance jumps are achieved according to DE 10 2006 040 980 Al with a damping element having radial extensions of the cross section, which are placed in the manner of a pipe clamp on the pipe.
- a single-walled and self-supporting acoustic insulation element is integrated into the exhaust system, wherein the acoustic insulation element min ⁇ least one inner nozzle and at least one in ra ⁇ Dialer direction To a central axis outwardly staggered ⁇ th outer nozzle, in each case one arranged between the two nozzles, the two nozzles verbin ⁇ dendes, is provided in the direction of the central axis in the length compressed central part, which in cross-section a U or a S-beat forms.
- tubular acoustic insulating element in the direction of the central axis as short as possible and thus to achieve a sufficient bending stiffness in order to be able to be used as a self-supporting acoustic insulating element.
- the acoustic insulation element In the area where the acoustic insulation element is tegriert into the exhaust system in ⁇ , it does not have the function of a mechanical ⁇ -decoupling meet and can be made relatively rigid.
- the insertion depth is between 5 mm and 16 mm, maximum 30 mm.
- the insulation property can be further improved according to the invention, when the acoustic insulation element is immediacy ⁇ bar is connected in front of or to the component which generates the resonances in the continued leading ultimately 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 by the amount of 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 is so ⁇ probably involve the provided between the inner radius and the outer radius of tube part and the two radii themselves in the measurement of 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 Schwingungsverhal ⁇ th, which would be achieved if the inner neck as the inlet nozzle have the same degree would like the outer neck as outlet.
- 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 pipe wall of the tubular part is parallel or is arranged at an angle a between 2.5 ° and 15 ° to the central axis.
- This further possibility of influencing the Dämmwir ⁇ kung also has the advantage that with existing connection geometry for the inner or the outer nozzle, the size of the two radii can be varied, that is, for very small radii of this pipe part an increasingly larger angle a Central axis includes.
- Another advantage is that the connection geometry can be increased or decreased by varying the angle a for both the inner nozzle and the outer nozzle.
- the single-walled acoustic insulating element is formed from sheet metal or metal casting and the insulating element increases continuously or suddenly in one direction along the workpiece Wall thicknesses 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 a beneficial effect especially in the frequency range above 2000 to 6000 Hz. This is advantageous in that thinner in calibrating the diameter of the outer Stut ⁇ zen from a smaller to a larger extent, the wall ⁇ strength 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.
- the acoustic insulation element in the flow direction S after the inner nozzle has a relation to the Grund twist ⁇ diameter reduced inner 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 ka ⁇ libr striving for the present inven tion ⁇ tion, when the acoustic insulation element is formed from a ka ⁇ libr conducting pipe section with a decidedssei- term base diameter between 45 mm and 85 mm and an output side diameter between 55 mm and 115 mm and one in the direction the central axis absolute 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 plugged into an end wall of a sheet metal housing for a NEN filter or a converter or a muffler is integrated, wherein at least a part of the end wall in the radial direction to the central axis of the inner nozzle and / or connects to the outer nozzle.
- 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 the outer nozzle calibrated larger diameter easier to integrate into the geometry of an exhaust system, because this outer nozzle connects directly to the Ge ⁇ housing and a possibly necessary Re ⁇ production of the diameter again to the extent of the measures provided for the other exhaust pipes diameter of the inner nozzle does not necessary is.
- the use of a mechanical decoupling element for an exhaust system for acoustic insulation of an exhaust system in the frequency range between 600 Hz and 6 kHz may be advantageous if the acoustic insulation element at least one inner socket and at least one in the radial direction to a central axis to the outside staggered outer neck has, in each case one arranged between the two stubs, connecting the two stubs compressed center part is provided which forms a U-shaped or S-shaped in cross section.
- FIG. 1 shows an exhaust system connected to an engine
- Figure 2 shows a cross section of an insulating element which is integrated between two components of an exhaust system
- FIG. 3 shows a top part of a section of an insulation ⁇ elements having a relation to the base diameter smaller inner diameter
- FIG. 4 shows a cross-section of an insulating element with a tube part set in relation to the central axis
- Figure 5 shows the integration of a Dämmelements in an end face of a housing
- Figure 6 shows a construction according to Figure 5, in which the insulating element is arranged in the radial direction centered to the front side;
- Figure 7 shows an arrangement according to Figure 6, in which the insulating element has a U-stroke
- FIG 8 shows the integration of a Dämmelements in a conical end face of a sheet metal housing.
- an exhaust system 4 is shown consisting of a first portion 41 and a second portion 42.
- 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 pre see ⁇ , 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 Dämm ⁇ element 1 to an outlet opening of a turbocharger 5 to ⁇ , which further connects the exhaust system 4 via the manifold 3 with the engine 2.
- the introduced into the exhaust system 4 via the exhaust gas stream and the turbocharger 5 oscillations to be insulated significantly over the akusti ⁇ cal insulation element 1 is in the range between 600 Hz and 6 kHz, so that the body emissions of the converter 45, the particulate filter 44 and the Schalldämp ⁇ fers 46 reduces are.
- FIG. 2 shows a schematic cross section of an acoustic insulating element 1 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 tubular member 14 and the two Ra ⁇ dien 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
- an exhaust gas pipe 47 adjoins the inner connecting piece 10 upstream of the insulating element 1 in the direction of flow S.
- a schematically illustrated exhaust element 48 In the flow direction S after the insulating element 1 is a schematically illustrated exhaust element 48, connected to the insulating element 1.
- examples of such exhaust elements 48 are shown by sheet metal housing 43.
- the S-impact 120 can in various embodiments, not shown, an input-side basic diameter 101 between 45 mm and 85 mm and an output-side diameter 151 between 55 mm and 115 mm and an absolute length L between 230 mm and 420 mm in the direction of the central axis 13, wherein the ratio of the diameters 101, 151 'and the length L can be selected so that the natural frequency at a mean input frequency of a) 350 Hz is a medium axial transmission loss of at least -18 dB; and b) 600 Hz, a mean axial transmission loss of at least 0 dB and c) 1000 Hz, a mean axial transmission loss of at least 8 dB and d) 3000 Hz, a mean axial transmission loss of at least 20 dB.
- 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-impact 120, in which the tube part 14 provided between the two radii 102, 152 is set at an angle ⁇ with respect to the central axis 13. It can be seen that the tube part 14 is thus not arranged parallel to the central axis 13, as shown for example in FIG.
- the angle a may be as well ⁇ a bottom diameter 101 of the inner nozzle 10 and the diameter 151 of the outer nozzle 15 to each other can be varied.
- 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 shows an embodiment modified from FIG. 3, in which, in the region of the inner radius 102, the inner diameter 103 is reduced relative to the basic diameter 101 of the inner connecting piece 10. In the flow direction S, 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 exemplary embodiment, in which the acoustic insulating element 1 is integrated in 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 shows a similar embodiment as in FIG. 5 with respect 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 shows an exemplary embodiment similar to FIG. 6, 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 shows an exemplary embodiment in which the insulating element 1 forms a connection between an exhaust gas 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.
Landscapes
- 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)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009030258 | 2009-06-23 | ||
PCT/EP2010/058952 WO2010149723A1 (de) | 2009-06-23 | 2010-06-23 | Rohrförmiges akustisches dämmelement |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2446128A1 true EP2446128A1 (de) | 2012-05-02 |
EP2446128B1 EP2446128B1 (de) | 2015-05-06 |
Family
ID=42670407
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20100728196 Not-in-force EP2446128B1 (de) | 2009-06-23 | 2010-06-23 | Rohrförmiges akustisches dämmelement |
Country Status (5)
Country | Link |
---|---|
US (1) | US8443933B2 (de) |
EP (1) | EP2446128B1 (de) |
CN (1) | CN102482979A (de) |
BR (1) | BRPI1010067A2 (de) |
WO (1) | WO2010149723A1 (de) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010041666A1 (de) * | 2010-09-29 | 2012-05-03 | Röchling Automotive AG & Co. KG | Kfz-Abgasführungsvorrichtung mit einem Funktionsgehäuse und einem Abgas-Kanal |
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 |
Family Cites Families (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1441742A (en) * | 1972-08-15 | 1976-07-07 | Smiths Industries Ltd | Tubing |
JPS5670111U (de) * | 1979-11-01 | 1981-06-10 | ||
DE3211027C2 (de) * | 1982-03-25 | 1984-08-30 | Gustav Wahler Gmbh U. Co, 7300 Esslingen | Wellrohr |
JPS60247005A (ja) * | 1984-05-19 | 1985-12-06 | Imakou Seisakusho:Kk | 内燃機関用消音装置 |
US4867269A (en) * | 1987-06-30 | 1989-09-19 | Titeflex Corporation | Tuned self-damping convoluted conduit |
ES2027741T3 (es) | 1987-09-01 | 1992-06-16 | Iwk Regler Und Kompensatoren Gmbh | Elementos de conduccion para sistemas de gas de escape. |
CN2151259Y (zh) * | 1993-02-09 | 1993-12-29 | 北京市劳动保护科学研究所 | 汽车排气***辅助降噪装置 |
JPH0989173A (ja) | 1995-09-25 | 1997-03-31 | Calsonic Corp | 管継手およびその製造方法と装置 |
CN2245668Y (zh) * | 1996-01-30 | 1997-01-22 | 南昌赣中金属波纹管厂 | 汽车排气管专用金属波纹软管 |
CN1046577C (zh) * | 1996-01-30 | 1999-11-17 | 南昌赣中金属波纹管厂 | 汽车排气管专用金属波纹软管及其生产工艺 |
JPH11153267A (ja) * | 1997-09-23 | 1999-06-08 | Witzenmann Gmbh Metallschlauchfab Pforzheim | チューブ・エレメント |
DE19812611C2 (de) | 1998-03-23 | 2002-11-14 | Gillet Heinrich Gmbh | Entkopplungselement in Rohrleitungen |
FR2833312A1 (fr) * | 2001-12-11 | 2003-06-13 | Qualetude | Dispositif de recyclage de gaz d'echappement pour moteur a combustion interne |
DE10164036A1 (de) | 2001-12-28 | 2003-07-17 | Emitec Emissionstechnologie | Flexibles Leitungselement |
JP2003239717A (ja) * | 2002-02-18 | 2003-08-27 | Nissan Motor Co Ltd | 消音装置 |
EP1431538B2 (de) | 2002-12-20 | 2009-08-05 | Senior Flexonics Automotive Limited | Flexibles Leitungselement für Abgasleitungen |
JP3944183B2 (ja) * | 2004-04-01 | 2007-07-11 | 本田技研工業株式会社 | 車両の排気系支持構造 |
DE202004005526U1 (de) | 2004-04-08 | 2004-07-01 | Heinrich Gillet Gmbh | Vorrichtung zur Reduzierung der Übertragung von Vibrationen und/oder Körperschall |
DE102006040980B4 (de) | 2006-08-31 | 2009-04-02 | Heinrich Gillet Gmbh | Körperschallsenkende Vorrichtung |
-
2010
- 2010-06-23 BR BRPI1010067A patent/BRPI1010067A2/pt not_active IP Right Cessation
- 2010-06-23 US US13/380,067 patent/US8443933B2/en not_active Expired - Fee Related
- 2010-06-23 CN CN201080037129XA patent/CN102482979A/zh active Pending
- 2010-06-23 WO PCT/EP2010/058952 patent/WO2010149723A1/de active Application Filing
- 2010-06-23 EP EP20100728196 patent/EP2446128B1/de not_active Not-in-force
Non-Patent Citations (1)
Title |
---|
See references of WO2010149723A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2010149723A1 (de) | 2010-12-29 |
US8443933B2 (en) | 2013-05-21 |
EP2446128B1 (de) | 2015-05-06 |
US20120160600A1 (en) | 2012-06-28 |
BRPI1010067A2 (pt) | 2016-03-15 |
CN102482979A (zh) | 2012-05-30 |
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