EP0307639A1 - Procédé d'atténuation de bruit dans des conduits de gaz à variation de pression dynamique dans l'écoulement, en particulier dans les dispositifs d'échappement des moteurs à combustion interne - Google Patents

Procédé d'atténuation de bruit dans des conduits de gaz à variation de pression dynamique dans l'écoulement, en particulier dans les dispositifs d'échappement des moteurs à combustion interne Download PDF

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Publication number
EP0307639A1
EP0307639A1 EP88113362A EP88113362A EP0307639A1 EP 0307639 A1 EP0307639 A1 EP 0307639A1 EP 88113362 A EP88113362 A EP 88113362A EP 88113362 A EP88113362 A EP 88113362A EP 0307639 A1 EP0307639 A1 EP 0307639A1
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EP
European Patent Office
Prior art keywords
throttle valve
internal combustion
exhaust
combustion engine
frequency
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
EP88113362A
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German (de)
English (en)
Other versions
EP0307639B1 (fr
Inventor
Raymond Dr. Freymann
Albrecht Keck
Anton Haas
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.)
Bayerische Motoren Werke AG
Original Assignee
Bayerische Motoren Werke AG
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Filing date
Publication date
Application filed by Bayerische Motoren Werke AG filed Critical Bayerische Motoren Werke AG
Publication of EP0307639A1 publication Critical patent/EP0307639A1/fr
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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
    • F01N1/16—Silencing apparatus characterised by method of silencing by using movable parts
    • F01N1/18—Silencing apparatus characterised by method of silencing by using movable parts having rotary movement
    • 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
    • F01N1/16—Silencing apparatus characterised by method of silencing by using movable parts
    • F01N1/165—Silencing apparatus characterised by method of silencing by using movable parts for adjusting flow area

Definitions

  • the invention relates to a working method for sound absorption in gas-carrying systems according to the type described in the preamble of claim 1.
  • a two-stroke internal combustion engine with an exhaust system in which a rotatable throttle valve is arranged.
  • the throttle valve is in drive connection with an actuator of a control device, the pre-compression pressure in the crankcase of the two-stroke engine serving as the control variable above the engine speed.
  • the throttle valve releases the flow cross-section more and more with increasing exhaust gas pulsation frequency until it is finally kept parallel to the flow of the exhaust gas.
  • a disadvantage of this working method is that, at higher exhaust gas pulsation frequencies, there is no longer a throttling for sound absorption.
  • the invention has for its object to improve a working method for sound attenuation in gas-carrying systems, especially in exhaust systems of internal combustion engines, by means of throttling so that an effective over a desired wide frequency range of dynamic pressure fluctuations in the flow medium when it emerges from the system into the free environment Sound attenuation is achieved without significantly increasing the flow resistance.
  • the essence of the invention is to change the flow cross-section of a gas-carrying system with pressure fluctuations that determine the sound level, and thus to reduce the sound excitation when the flow medium exits the system into the free environment.
  • Such a working method is particularly effective in exhaust systems of internal combustion engines.
  • it is advantageous that the flow cross section of the exhaust system is reduced or throttled only when positive pressure amplitudes occur, but otherwise the flow resistance associated with the throttling is reduced.
  • the throttling based on the frequency of the positive amplitude, with only a temporarily reduced flow cross section, furthermore results in effective sound damping in every speed range of the internal combustion engine over a desired broad frequency range of the exhaust gas pulsations without any significant power-reducing repercussions on the machine.
  • the invention offers further advantages in combination with a chamber provided upstream of the throttle point in the exhaust system, which can be provided, for example, by a conventional absorption and / or reflection damper. This is used to dampen pressure waves reflected in / at the throttle point, which may reduce their performance-reducing effects.
  • a conventional silencer of the type mentioned above the invention offers the essential advantage of an additional silencer. This can be retrofitted to existing exhaust systems to further reduce the exhaust noise level.
  • the muffler according to claim 1 of the invention can in a combined arrangement with a chamber or a muffler of conventional design by skillful division of the damping components (low and high frequencies) on both damper systems serve to significantly reduce the construction volume and construction costs of the conventional absorption and / or reflection dampers. This, in turn, is advantageous for the design of a smooth underside of the vehicle in passenger cars and for a low outlay on thermal insulation devices and soundproofing material.
  • the invention is preferably implemented by a throttle valve which is driven so as to be pivotable and / or rotatable, an electric motor (stepping motor) forming the actuator in a control device or in a control circuit.
  • the core of the control philosophy here is to regulate the instantaneous angular position of the throttle valve for synchronous assignments dependent on the frequencies of the positive pressure amplitudes via the angular position of the crankshaft based on the TDC of a reference cylinder of the internal combustion engine. From measured absolute angular positions of both devices, the relative angular positions can be regulated depending on the speed depending on the working method of the internal combustion engine, its number of cylinders and the number of exhaust systems assigned to an internal combustion engine.
  • a compensation network For a further, load-dependent synchronization of the silencer throttle valve with the frequencies of the positive pressure amplitudes, further signals are fed to the compensation network, preferably ignition pulse signals.
  • the throttle valve throttles the respective flow cross-section of the exhaust system most strongly at maximum pressure attenuation, at maximum pressure amplitudes.
  • a position that deviates more or less from the aforementioned vertical angular position relative to the pressure amplitude maximum can be favorable for a sound attenuation achieved in interaction of the throttle valve with a conventional silencer of a known type.
  • the compensation network can be equipped with a separate characteristic map, which receives ignition pulses and / or speed signals as input signals in connection with load signals.
  • a six-cylinder internal combustion engine 1 shown only schematically, comprises an exhaust system 2 with a manifold 6 divided into sections 3, 4 and 5, into the individual lines 7 provided for cylinder groups flow into.
  • Sections 3 and 4 connect a first chamber 8, which can be a combined absorption / reflection damper.
  • Sections 4 and 5 can also be connected to one another via a second chamber 9, in which a rear silencer or catalytic converter can be arranged.
  • a throttle valve 10 is provided in the section 4 of the manifold 6 and is arranged such that it can be rotated by an angle of rotation.
  • the throttle valve 10 is arranged in the pipe section 4, leaving a circumferential annular gap 11.
  • an electric motor (stepping motor) 12 is provided for the throttle valve 10 as an actuator of a control device 13 or a control circuit.
  • the control device 13 comprises a first rotary encoder 15 connected to the crankshaft 14 of the internal combustion engine 1 and a second rotary encoder 16 connected to the armature of the stepping motor 12. Both rotary encoders 15 and 16 transmit their signals ⁇ KW and ⁇ D to a compensation network 17 of the control device 13.
  • the compensation network 17 has further inputs 18 and 19 for ignition pulses and the TDC mark of a reference cylinder of the internal combustion engine 1. Control signals of the compensation network 17 go to the stepper motor 12 via an output 20.
  • the engine 12 is regulated in such a way that it throttles the throttle valve 10 substantially as large as possible when a positive pressure amplitude of an exhaust gas pressure wave arrives, position A in FIG. 2.
  • the flow loss caused by the free flow cross section of the annular gap 11 causes pressure loss in the exhaust gas.
  • Pressure wave results in a corresponding degree of sound absorption.
  • the motor 12 is further regulated so that the throttle valve 10 more or less releases the flow cross section of the pipe section 4 between two successive pressure amplitude values, positions B and C in FIG. 2 throttled only with positive pressure amplitudes of the dynamic exhaust gas pressure fluctuations and in synchronism with the frequency of these pressure amplitudes.
  • the frequency of the pressure amplitudes or the exhaust gas pressure fluctuations or the exhaust gas pulsations is in a fixed relationship with the frequency of the speed of the crankshaft 14 of the internal combustion engine 1.
  • the pressure amplitudes or Exhaust gas pulsations according to the third harmonic of the basic frequency given by the crankshaft speed.
  • this frequency dependency serves to determine or regulate the instantaneous angular position of the throttle valve 10 relative to the maximum of a pressure amplitude for a corresponding sound attenuation from the angular position of the crankshaft 14 related to the TDC of a reference cylinder via the compensation network 17.
  • the ignition pulses supplied to the compensation network 17 via the input 18 serve for an additional load-dependent control of the throttle valve 10.
  • the current angular position of the throttle valve 10 can thus be selected relative to the positive pressure amplitude maximum between positions A and B according to FIG. 2.
  • a separate map can be provided in the compensation network 17 for this operating point-dependent control.
  • This speed and load or operating point-dependent control of the sound damping by means of the throttle valve 10 can also serve to tune a muffler system formed from a throttle valve 10 and an upstream chamber 8 in such a way that the chamber 8 represented by an absorption and / or reflection damper can be of reduced construction volume and construction costs.
  • the required speed of the rotating throttle valve 10 results from half the frequency of the dominant exhaust gas pulsations occurring according to the number of cylinders per crankshaft revolution, the value of half the frequency taking into account twice the closing of the flow cross-section of section 4 of the manifold 6 with one revolution of the rotating throttle valve 10.
  • a relatively wide operating range of the internal combustion engine 1 can be covered with the rotational speeds of the throttle valve 10 derived from the fixed ratio of the frequencies mentioned above.
  • the ratio of the speed of the throttle valve 10 to half the frequency of the exhaust gas pulsations identical to the exhaust surges when the exhaust valves are opened can be selected variably.
  • the working method of sound damping according to the invention by means of a throttle valve 10 driven by the motor 12 in a vibration-dependent and / or rotationally movable manner can serve as an additional device for damping, especially for the exhaust sound level of critical exhaust gas pulsations.
  • the chamber 8 arranged upstream serves to dampen the reflected pulsations to further reduce power-reducing effects caused by pressure waves or exhaust gas pulsations reflected on the throttle valve 10.
  • the latter can drive the throttle valve 10 via a flexible shaft (not shown).
  • the compensation network 17 can be designed for analog or digital signal processing, the latter being supplied with the TDC signal from a motor system assigned to the internal combustion engine 1.
  • a further angle encoder can be arranged on the latter.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust Silencers (AREA)
  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
EP88113362A 1987-09-15 1988-08-17 Procédé d'atténuation de bruit dans des conduits de gaz à variation de pression dynamique dans l'écoulement, en particulier dans les dispositifs d'échappement des moteurs à combustion interne Expired - Lifetime EP0307639B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3730890 1987-09-15
DE3730890 1987-09-15

Publications (2)

Publication Number Publication Date
EP0307639A1 true EP0307639A1 (fr) 1989-03-22
EP0307639B1 EP0307639B1 (fr) 1992-05-06

Family

ID=6336010

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88113362A Expired - Lifetime EP0307639B1 (fr) 1987-09-15 1988-08-17 Procédé d'atténuation de bruit dans des conduits de gaz à variation de pression dynamique dans l'écoulement, en particulier dans les dispositifs d'échappement des moteurs à combustion interne

Country Status (3)

Country Link
EP (1) EP0307639B1 (fr)
DE (1) DE3870778D1 (fr)
ES (1) ES2031968T3 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1991009214A1 (fr) * 1989-12-12 1991-06-27 Group Lotus Plc Attenuation des fluctuations de pression dynamique dans les conduits
EP1282895A1 (fr) * 2000-05-11 2003-02-12 Jean-Laurent Peube Source et systeme electroaeroacoustiques pour controle actif du bruit
DE10030490B4 (de) * 2000-06-21 2005-07-21 Dr.Ing.H.C. F. Porsche Ag Abgasanlage für eine Brennkraftmaschine
WO2007005424A1 (fr) * 2005-07-05 2007-01-11 Emcon Technologies Llc Commande de vitesse de l'actionnement d'une soupape d'echappement

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR360413A (fr) * 1905-10-31 1906-04-21 Louis T Weiss Perfectionnements dans les pots d'échappement
US2320668A (en) * 1941-08-15 1943-06-01 Harry A Smith Mechanical exhaust silencer

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE447290B (sv) * 1985-03-19 1986-11-03 Volvo Ab Anordning for dempning av avgasljud medelst en av avgasflekt beroende reglerventil

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR360413A (fr) * 1905-10-31 1906-04-21 Louis T Weiss Perfectionnements dans les pots d'échappement
US2320668A (en) * 1941-08-15 1943-06-01 Harry A Smith Mechanical exhaust silencer

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1991009214A1 (fr) * 1989-12-12 1991-06-27 Group Lotus Plc Attenuation des fluctuations de pression dynamique dans les conduits
EP1282895A1 (fr) * 2000-05-11 2003-02-12 Jean-Laurent Peube Source et systeme electroaeroacoustiques pour controle actif du bruit
DE10030490B4 (de) * 2000-06-21 2005-07-21 Dr.Ing.H.C. F. Porsche Ag Abgasanlage für eine Brennkraftmaschine
WO2007005424A1 (fr) * 2005-07-05 2007-01-11 Emcon Technologies Llc Commande de vitesse de l'actionnement d'une soupape d'echappement
US7243623B2 (en) 2005-07-05 2007-07-17 Arvin Technologies, Inc. Velocity control of exhaust valve actuation
CN101198773B (zh) * 2005-07-05 2010-12-08 排放控制技术有限公司 排气阀致动的速度控制

Also Published As

Publication number Publication date
EP0307639B1 (fr) 1992-05-06
ES2031968T3 (es) 1993-01-01
DE3870778D1 (de) 1992-06-11

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