EP0158013A1 - Silencieux à réflexion pour moteur à combustion - Google Patents

Silencieux à réflexion pour moteur à combustion Download PDF

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Publication number
EP0158013A1
EP0158013A1 EP85100933A EP85100933A EP0158013A1 EP 0158013 A1 EP0158013 A1 EP 0158013A1 EP 85100933 A EP85100933 A EP 85100933A EP 85100933 A EP85100933 A EP 85100933A EP 0158013 A1 EP0158013 A1 EP 0158013A1
Authority
EP
European Patent Office
Prior art keywords
reflection
shells
silencer according
tubes
housing
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
EP85100933A
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German (de)
English (en)
Other versions
EP0158013B1 (fr
Inventor
Kurt Ing. Grad. Schad
Hans-Joachim Dipl.-Ing. Gora
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.)
Adam Opel GmbH
Original Assignee
Adam Opel GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Adam Opel GmbH filed Critical Adam Opel GmbH
Publication of EP0158013A1 publication Critical patent/EP0158013A1/fr
Application granted granted Critical
Publication of EP0158013B1 publication Critical patent/EP0158013B1/fr
Expired legal-status Critical Current

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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
    • 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

Definitions

  • the invention relates to a reflection silencer for internal combustion engines, consisting of a closed housing provided with an inlet and an outlet connection, in which two at least partially overlapping pipes are arranged in the axial direction, one of which is connected to the inlet connection and on its circumference has a passage area through which the exhaust gases pass from the inlet connector into the interior of the housing, and of which the other is connected to the outlet connector and has a passage area on its circumference through which the exhaust gases pass from the housing to the outlet connector.
  • the principle of sound insulation with the aid of reflection is that a reflective obstacle is arranged in the sound line channel in such a way that the largest possible proportion of the sound wave is extinguished by interference between the reflected and the incident sound wave. It should be noted that walls arranged in the propagation path as well as changes in the cross-section of the sound-conducting channel represent an obstacle for sound waves. Therefore, the simplest version of a reflection silencer consists of a closed housing of relatively large diameter, to which an inlet connector and an outlet connector of smaller diameter are connected.
  • Mufflers for internal combustion engines also serve to smooth out the loud, pulsating gas flow that the internal combustion engine generates through its exhaust system and to reduce the muzzle noise, which primarily results from the ignition noise.
  • the sound insulation for internal combustion engines is so difficult because the critical noise spectrum is very broadband, namely in a range from about 50 to 1000 Hz, which is the reason why silencers for internal combustion engines are relatively complicated structures, or that several silencers in series have to be switched in order to cover the noise spectrum as completely as possible.
  • the damping effect of reflection mufflers can be further improved by controlling the exhaust gas flow leading to throttling effects.
  • a reflection silencer of the type specified is known from US-PS 3 191 715.
  • the tubes connected to the inlet and the outlet run transversely to the housing axis. This is intended to ensure that the inflowing exhaust gases pass through approximately three times the length of the housing before they leave the housing again.
  • the main flow of the exhaust gas runs along the pipe connected to the inlet, leaves it at its open end approximately in the middle of the housing, is reflected on the housing wall, between the drill and the housing wall, is directed back towards the entrance, whereupon it is reversed in the direction of the input open, near the middle of the housing end of the pipe connected to the outlet is introduced.
  • a much smaller part of the exhaust gas flow passes through a plurality of slots provided on the pipes from the housing inlet to the housing outlet in order to enable the pulsating exhaust gas flow to expand and the flow resistance to be reduced.
  • This known reflection silencer is sound-absorbing only in a relatively small, medium frequency range.
  • the smoothing of the pulsating exhaust gas flow is only incompletely guaranteed.
  • the inclusion of the entire housing wall has a detrimental effect on the insulation value of this silencer, since in this way a very considerable part of the exhaust noise is emitted to the surroundings via the housing wall.
  • Another reflection silencer for internal combustion engines is known from DE-PS 617 831.
  • the housing of this muffler has sloping boundary surfaces and is divided into a plurality of chambers connected to one another by pipes of different diameters, each of which insulates a different, relatively narrow limit range of the noise spectrum.
  • the arrangement of the pipes slightly improves the individual insulation range of each chamber above the chamber cut-off frequency, but a step-by-step course of the insulation is also retained by this measure.
  • This silencer also emits a significant proportion of the exhaust gas noise to the surroundings via the housing wall.
  • a subdivision into subchambers also characterizes the additional device for silencers known from DE-PS 626 321, in which two transversely extending pipes of different lengths are inserted in the single partition, one of which has one end at the level of the housing inlet in the Partition is used.
  • the pipe opposite the inlet should be sufficient to a lesser extent for a smooth passage of the exhaust gases, as a result of which the exhaust gases are forced to make a detour via the pipe arranged offset to the inlet opening, which is intended to make the sound insulation more uniform.
  • a disadvantage is the increasing flow resistance of this additional device for a silencer with increasing speed, which has unfavorable repercussions on the internal combustion engine itself.
  • the sound-absorbing effect of this additional device is limited to a very narrow frequency range.
  • the silencer known from US Pat. No. 3,469,652 is used primarily for smoothing the pulsating exhaust gas flow.
  • the damper housing itself is tuned to the low frequency part of the noise spectrum and acoustically coupled to a pair of curved tubes extending between the inlet and the outlet, which in turn are connected to the inlet and outlet with a curved tube connecting the inlet and the outlet.
  • the relatively good smoothing of the pulsating exhaust gas flow is opposed by a narrow-band noise damping in this silencer, whereby a considerable part of the noise spectrum is also radiated outwards via the damper housing.
  • the object of the present invention is to provide a reflection muffler of the type specified, which broadly attenuates the critical noise spectrum of the exhaust gases and at the same time smoothes the pulsating exhaust gas flow sufficiently, the structure being compact, the manufacture economically possible and the number of components required which are of simple design should be as small as possible.
  • the risk of corrosion and / or burnout of the housing is to be counteracted by the design according to the invention.
  • the pass-through areas are provided only on the sides opposite the respective other tube, that the pass-through areas are opposite first reflection shells, and in that the first reflection shells on the side of the tubes facing away from the pass-through areas two reflection bowls face each other.
  • the passage areas are preferably formed essentially over the entire length of the tubes and have the shape of rectangular windows.
  • the tubes are arranged overlapping substantially over the entire length between the housing end walls, which are preferably arranged parallel to one another, which ensures that the sound waves, even when largely open tubes are used, are conducted exclusively between the two tube reflection shell systems, so that no sound is emitted via the housing wall.
  • the tubes are each tightly connected with their ends facing away from the inlet connector or outlet connector, it is expedient to provide the tubes with circumferentially closed end regions, which are preferably relatively short.
  • the first reflection shells are preferably tubular and have on the side facing away from the passage areas of the tubes an approximately the entire length of the shell reflection window, which has a rectangular shape in plan view and its opening angle with respect to the shell axis between 45 ° and 90 °, in particular about 60 °.
  • the ends of the first reflection shells are expediently tightly connected to the housing end walls and have relatively short, circumferentially closed end regions, the length of which is preferably equal to the length of the end regions of the tubes.
  • both the first and the second reflection shells are at an acute angle to one another, the angle included by the first reflection shells being smaller than the angle included by the tubes, while the angle included by the second reflection shells is smaller than the angle enclosed by the first reflection shells.
  • the axes of the first reflection shell preferably coincide with the tube axes on the inlet side, while the axes of the second reflection shells essentially coincide with the axes of the first reflection shells on the outlet side.
  • the tubes are preferably located essentially within the first reflection shells.
  • the second reflection shells which are tightly connected at the end to the housing end walls have opening areas which are advantageously provided on their sides facing away from the assigned reflection shell windows, the opening angles of the second reflection shells with respect to their axes being less than 180 ° and in particular being about 90 °.
  • the first reflection shells are expediently only partially arranged within the second reflection shells and in such a way that between the first reflection shells and the longitudinal edges of the second ones delimiting the opening areas Reflective shells, each with two separate opening areas.
  • the flow path of the exhaust gases is indicated by arrows in FIG.
  • the exhaust gases pass through an inlet connection 6 inserted in the upper region of a flat inlet end wall 8 of the damper housing 10 into the interior of the reflection muffler, which they essentially have via an arranged in the lower region at a distance from the inlet end wall 6 parallel to the latter leave the same design, flat outlet end wall 9 used outlet port 7 again.
  • the damper housing 10 consists of two cylinder half-shells 10 ', 10 "with their open sides opposite one another, between which flat and parallel housing side walls 4, 5 extend.
  • a pipe 15 connected to the inlet connector 6 extends obliquely upward from the inlet end wall 8 through the damper housing 10 to the outlet end wall 9, with which it is tightly connected.
  • Another tube 16 is connected to the outlet nozzle 7 and also extends obliquely upwards from the outlet wall 9 to the inlet end wall 8, with which it is tightly connected.
  • the two pipes 15 and 16 thus overlap completely and run parallel to the housing side walls 4 and 5.
  • the pipe axes 15 'and 16' intersect to the left of the inlet wall 8 under a sharp one Angle ⁇ , which is approximately 30 °.
  • the distance between the tubes 15, 16 on the inlet end wall 8 is selected such that the first reflection shells 13, 14, which will be described below, can be accommodated.
  • Rectangular windows 11, 12 are provided on mutually facing sides of the tubes 15 and 16, which extend approximately over the entire tube length and have an opening angle t of approximately 60 ° with respect to the tube axes 15 ', 16'.
  • the tubes 15, 16, however, have a short, circumferentially closed end region.
  • Each of the two tubes 15 and 16 is surrounded at an increasing distance by a first reflection shell 13 and 14 and by a second reflection shell 21 and 22, which are tightly connected to the end walls 8, 9 on the end face.
  • the first reflection shells 13, 14 are tubular and surround the associated tube 15 or 16. They have rectangular windows 17, 18 on the side facing away from the windows 11, 12 of the tubes 15, 16, which are almost the entire length of the housing 10 extend and have an opening angle with respect to the shell axis 13 ', 14' of approximately 90 °.
  • the second reflection shells 21, 22 extend over an angle of approximately 270 ° and lie with their closed side radially opposite the windows 17, 18.
  • the first reflection shells 13, 14 extend through the open side of the second reflection shells 21, 22 at a distance from the longitudinal edges 21 ', 22' of the second reflection shells 21, 22. This creates axially continuous opening areas 19, 19 'and 20, 20' .
  • the axes of the first and second reflection shells 13, 14 and 21, 22 lie essentially in the same plane as the axes 15 ', 16' of the two pipes 15 and 16 and intersect to the left of the inlet end wall 8. That of the axes 13 ', 14' of the first reflection shells 13, 14 included angle ⁇ is smaller than the angle ⁇ enclosed by the tube axes 15 ', 16' and is approximately 25 °. In contrast, the second reflection shells 21, 22 run at an acute angle ⁇ to one another, which in turn is smaller than the angle enclosed by the first reflection shells 13, 14 and is approximately 10 °.
  • the exhaust gas stream entering the inlet connection 6 of the damper housing 10 flows into the tube 1 and exits the window 11. It is partially reflected back and forth between the tube 15 and the first reflection shell 13 while at the same time moving towards the outlet end wall 9, and partially directed through the first reflection shell 13 to its window 17, through which it reaches the second reflection shell 21, where it is reflected or redirected to the opening areas 19, 19 '.
  • the exhaust gases flow through the housing 10 into the open areas 20, 20' of the second reflection shell 22.
  • the exhaust gas flow passes through the window 18 and after deflection at the first Reflection bowl 14 through the window 12 into the tube 16, whereby multiple reflections occur again.
  • the exhaust gas flow then finally reaches the outlet connection 7 along the pipe 16.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust Silencers (AREA)
EP85100933A 1984-02-22 1985-01-30 Silencieux à réflexion pour moteur à combustion Expired EP0158013B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3406282 1984-02-22
DE3406282A DE3406282C2 (de) 1984-02-22 1984-02-22 Reflexionsschalldämpfer für Brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0158013A1 true EP0158013A1 (fr) 1985-10-16
EP0158013B1 EP0158013B1 (fr) 1989-01-11

Family

ID=6228419

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85100933A Expired EP0158013B1 (fr) 1984-02-22 1985-01-30 Silencieux à réflexion pour moteur à combustion

Country Status (3)

Country Link
US (1) US4623035A (fr)
EP (1) EP0158013B1 (fr)
DE (2) DE3406282C2 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5188998A (en) * 1990-03-19 1993-02-23 Basf Aktiengesellschaft Transition-metal catalyst component for a ziegler catalyst system, and the use of said system
DE102014101144A1 (de) 2014-01-30 2015-07-30 Smk Systeme Metall Kunststoff Gmbh & Co. Kg. Reflexionsschalldämpfer

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4747467A (en) * 1986-04-01 1988-05-31 Allied-Signal Inc. Turbine engine noise suppression apparatus and methods
US6296074B1 (en) 1998-11-19 2001-10-02 Charles W. Ridlen Noise reducing exhaust system and method
US6615576B2 (en) 2001-03-29 2003-09-09 Honeywell International Inc. Tortuous path quiet exhaust eductor system

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1567298A (en) * 1923-09-12 1925-12-29 Elmer F Reinhardt Muffler
GB276074A (en) * 1926-05-18 1927-08-18 Ole Solberg Bie Improvements in exhaust-silencers
DE476875C (de) * 1926-09-15 1929-05-31 Progress Ges Fuer Textilmaschi Auspuffdaempfer, insbesondere fuer Fahrzeugmotoren
GB376815A (en) * 1931-04-14 1932-07-14 Frederick Heather Improvements in and relating to silencers for gaseous currents
FR734813A (fr) * 1932-04-07 1932-10-28 Système de silencieux pour moteurs à explosions
US3181647A (en) * 1965-05-04 Apparatus for muffling noise and engine exhaust gases
US3665712A (en) * 1970-02-09 1972-05-30 William L Tenney Two-cycle engine resonance exhaust system

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE626321C (de) * 1931-11-05 1936-02-24 Daimler Benz Akt Ges Zusatzgeraet fuer Schalldaempfer, insbesondere an Brennkraftmaschinen von Kraftfahrzeugen
DE617831C (de) * 1932-10-01 1935-08-29 Martin Kluge Dr Ing Schalldaempfer fuer Brennkraftmaschinen
US3191715A (en) * 1963-05-27 1965-06-29 Walker Mfg Co Muffler
US3469652A (en) * 1968-06-17 1969-09-30 Gen Motors Corp Acoustic resonator with gas recirculation tubes
FR1596398A (fr) * 1968-12-26 1970-06-15
DE2612421C3 (de) * 1976-03-24 1979-11-29 Fa. J. Eberspaecher, 7300 Esslingen Abgasschalldämpfer
DE2715053A1 (de) * 1977-04-04 1978-10-12 Eberspaecher J Absorptions-schalldaempfer

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3181647A (en) * 1965-05-04 Apparatus for muffling noise and engine exhaust gases
US1567298A (en) * 1923-09-12 1925-12-29 Elmer F Reinhardt Muffler
GB276074A (en) * 1926-05-18 1927-08-18 Ole Solberg Bie Improvements in exhaust-silencers
DE476875C (de) * 1926-09-15 1929-05-31 Progress Ges Fuer Textilmaschi Auspuffdaempfer, insbesondere fuer Fahrzeugmotoren
GB376815A (en) * 1931-04-14 1932-07-14 Frederick Heather Improvements in and relating to silencers for gaseous currents
FR734813A (fr) * 1932-04-07 1932-10-28 Système de silencieux pour moteurs à explosions
US3665712A (en) * 1970-02-09 1972-05-30 William L Tenney Two-cycle engine resonance exhaust system

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5188998A (en) * 1990-03-19 1993-02-23 Basf Aktiengesellschaft Transition-metal catalyst component for a ziegler catalyst system, and the use of said system
DE102014101144A1 (de) 2014-01-30 2015-07-30 Smk Systeme Metall Kunststoff Gmbh & Co. Kg. Reflexionsschalldämpfer
DE102014101144B4 (de) * 2014-01-30 2016-10-06 Smk Systeme Metall Kunststoff Gmbh & Co. Kg. Reflexionsschalldämpfer

Also Published As

Publication number Publication date
DE3406282C2 (de) 1986-04-30
US4623035A (en) 1986-11-18
DE3567501D1 (en) 1989-02-16
EP0158013B1 (fr) 1989-01-11
DE3406282A1 (de) 1985-08-22

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