EP1318281B1 - Aktiver Schalldämpfer für Abgasanlagen - Google Patents
Aktiver Schalldämpfer für Abgasanlagen Download PDFInfo
- Publication number
- EP1318281B1 EP1318281B1 EP20020018051 EP02018051A EP1318281B1 EP 1318281 B1 EP1318281 B1 EP 1318281B1 EP 20020018051 EP20020018051 EP 20020018051 EP 02018051 A EP02018051 A EP 02018051A EP 1318281 B1 EP1318281 B1 EP 1318281B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- silencer according
- machine
- drive device
- sound
- 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.)
- Expired - Lifetime
Links
- 230000003584 silencer Effects 0.000 title claims description 31
- 238000002485 combustion reaction Methods 0.000 claims description 23
- 230000033001 locomotion Effects 0.000 claims description 12
- 230000008878 coupling Effects 0.000 claims description 7
- 238000010168 coupling process Methods 0.000 claims description 7
- 238000005859 coupling reaction Methods 0.000 claims description 7
- 230000005540 biological transmission Effects 0.000 claims description 6
- 230000001419 dependent effect Effects 0.000 claims description 5
- 238000000034 method Methods 0.000 claims description 5
- 230000008569 process Effects 0.000 claims description 5
- 230000002457 bidirectional effect Effects 0.000 claims description 2
- 230000002596 correlated effect Effects 0.000 claims description 2
- 230000030279 gene silencing Effects 0.000 claims 1
- 230000006698 induction Effects 0.000 claims 1
- 238000013016 damping Methods 0.000 description 10
- 230000007246 mechanism Effects 0.000 description 5
- 230000000875 corresponding effect Effects 0.000 description 3
- 239000012528 membrane Substances 0.000 description 3
- 238000011161 development Methods 0.000 description 2
- 230000018109 developmental process Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000008033 biological extinction Effects 0.000 description 1
- 150000001875 compounds Chemical class 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000003292 diminished effect Effects 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
Images
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
- F01N1/06—Silencing apparatus characterised by method of silencing by using interference effect
- F01N1/065—Silencing apparatus characterised by method of silencing by using interference effect by using an active noise source, e.g. speakers
Definitions
- the present invention relates to an active silencer for damping airborne sound, a machine with a rotating drive shaft generated as a function of their speed, with the features of the preamble of claim 1.
- Mufflers of this type are mainly used in exhaust systems of internal combustion engines, in particular of motor vehicles, used to control the noise emissions of internal combustion engines or the vehicles into the environment. It is also known, silencer in the intake to arrange the internal combustion engines.
- Such active silencers are for example from the US 5,336,856, US 5,432,857, EP 0 916 817 A2, DE 196 10 292 A1 and DE 197 51 596 A1 and have a hollow body, the at least one movable wall for generating Contains counter sound and via a connection with a to Guiding the airborne sound to be damped is acoustically coupled. Furthermore, a drive device provided for moving the movable wall. at the known devices is the movable wall respectively formed by a diaphragm of a loudspeaker that with Help of an electromagnetic actuator for generating the desired Schmidtalls is excitable.
- the well-known silencers each have a sensor e.g.
- the present invention deals with the problem for an active silencer of the type mentioned to provide an improved embodiment, in particular a reduced susceptibility to those in an internal combustion engine owns operating conditions.
- the invention is based on the general idea, the Generation of the counter sound used moving wall to form a bottom of a piston in a cylinder space Hubver fost arranged or stored. hereby results in a robust construction which makes it possible in particular the silencer according to the invention in the exhaust system to arrange an internal combustion engine. Of special Significance here is that the inventive active Silencer without speaker manages.
- the drive means moves the piston so that the Stroke frequency of the piston in a constant ratio to Speed or rotation frequency of the machine stands.
- This embodiment based on the knowledge that in a machine with a rotating drive shaft to be damped airborne sound one dependent on the speed of the drive shaft Main noise frequency possesses, with the help of the silencer should be damped. Due to the phase-locked coupling of Stroke frequency of the piston to the rotational frequency of the drive shaft it is ensured that the pressure waves of the counter sound show the same frequency behavior as the pressure waves of the Kleinstörfrequenz. This can ensure that the counter-sound generated by the piston at any speed automatically exactly the required for damping the main noise frequency Owns frequency. In contrast to the known ones Silencers do not need complicated algorithms be evaluated, since only the simple Relationship between speed and interference frequency for generation the required counter sound is used. Such Control can therefore be comparatively inexpensive, robust and stable.
- the stroke movement of the piston so to design that only a single counter-sound frequency is generated. It is expedient to have a further training the stroke movement is designed so that the piston at least stimulates two different counter-sound frequencies, thereby two different interference frequencies can be damped.
- the second disturbance frequency forms a harmonic the first interference frequency.
- an amplitude control device provided for adjusting the amplitude of the counter sound be, which has a control element, depending his operation the acoustic coupling through the connection between the cylinder chamber and the airborne sound Lead more or less damped.
- the amplitude controller can then the damper power to the moment required power to be adjusted in which the two mutually acting sound fields stronger or weaker be coupled.
- the amplitude control means the control member depending on the engine speed and / or the Press machine power.
- the piston via the drive device with the drive shaft of the machine be connected to drive.
- the piston via the drive device with the drive shaft of the machine be connected to drive.
- this embodiment is on dispenses with vulnerable electronics to control the piston, whereby the silencer according to the invention particularly easy and robust builds.
- the stroke frequency of the piston is appropriate chosen so that it is n times the rotational frequency of the drive shaft is.
- the ignition processes are symmetrical distributed over the drive shaft rotation angle, so that this embodiment automatically to a counter-sound frequency leads, which are equal to those generated by the ignition processes Interference frequency is.
- a 4-cylinder four-stroke engine comes it during a crankshaft revolution to two ignitions, so that the stroke frequency thus twice the rotational frequency the crankshaft is.
- For a 6-cylinder four-stroke engine find three ignition processes per crankshaft revolution, so that the stroke frequency of the piston accordingly three times Crankshaft frequency is.
- FIG. 1 shows a much simplified schematic representation a silencer according to the invention.
- a preferred application of an inventive active muffler 1 explained in more detail, namely for Attenuation of airborne noise in an exhaust line 2 of an internal combustion engine 3.
- the silencer 1 has at least a hollow body which forms a cylinder space 4.
- a piston 5 is mounted in a liftable manner, which is indicated by a double arrow 6.
- a floor 7 of the piston 5 forms a movable in the cylinder chamber 4 Wall.
- the hollow body 4 and the cylinder chamber 4 is acoustically coupled via a connection 8 with a line 9.
- This line 9 forms a line of the exhaust system 2 and leads during operation of the internal combustion engine 3 the airborne sound to be damped.
- the muffler 1 has a drive device 10 for Moving the piston 5.
- the drive device contains 10 a crank mechanism 12, the incoming rotary motion the drive shaft 11 in an outgoing bidirectional Stroke movement of the piston 5 converts.
- the drive device 10 contains the drive device 10, a transmission 13, the incoming Speed of the drive shaft 11 in an outgoing speed translated to the crank mechanism 12 and thus to the Piston 5 is transmitted.
- the gear ratio of the transmission 13 at all engine speeds constant. Accordingly results for the stroke frequency of the piston 5 is a constant ratio to the rotational frequency or rotational speed of the drive shaft 11 or the machine 3.
- the drive device 10 moves the piston 5 at all stroke frequencies with a constant Hub. Appropriately, this stroke is on the maximum damping performance the muffler 1 designed. However, if that too dampening background noise has only relatively small amplitudes, e.g. during idle operation of the internal combustion engine 3, this may cause a noise pollution by the Lead silencer 1.
- an amplitude control device 14 for adjusting the amplitude of the piston 5 generated counter sound.
- This amplitude control device 14 has a control member 15, here in the form of a butterfly flap is designed.
- the control member 15 can with Help an actuator 16 are actuated.
- the control member 15th is arranged in the region of the connection 8 and can depend on his operation the sound fields in the cylinder chamber 4 and more or less couple in the line 9.
- the control member 15 is appropriate depending on the engine speed and / or engine power.
- the amplitude controller 14 includes a Control 17, which has a corresponding control line 18 actuates the Steuergliedaktuator 16.
- a pedal angle 20 of an accelerator pedal 21st be tapped, as the pedal position usually with the power requirement of the internal combustion engine 3 correlated.
- a throttle 22 tap in an intake tract 23 of the internal combustion engine 3 is arranged.
- the control member 15 via a corresponding linkage directly to the throttle valve 22 to couple one of the Engine power dependent operation of the control member 15th to reach.
- the Steuergliedaktuator 16 can as electrical or electromagnetic or hydraulic or pneumatic or mechanical actuator 16 is formed be in the proper way with the control member 15 is drive connected.
- the control member 15 is comparatively low temperature loads exposed as it is not from the exhaust of the internal combustion engine 3 is flowed through. Furthermore, must it only reacts relatively slowly, as it only and load changes, but not the time course of the sound pressure level must follow. Thus, known and proven Control members 15 and actuators 16 are used.
- the Internal combustion engine 3 for example, a 4-cylinder four-stroke engine, the two ignitions per revolution its drive shaft 11 has.
- the transmission 13 is then like this designed that the piston 5 has a stroke frequency, the twice as high as the rotational frequency of the drive shaft eleventh is.
- This relationship remains at all speeds of the machine 3 obtained, which by the ignition in the Internal combustion engine 3 generated major noise at each Speed automatically damped with the correct counter sound can be. It is clear that this is the positioning the connection 8 and the forced coupling between the Drive shaft 11 and the piston 5 so matched are that in the field of coupling of the counter sound in the line 9 an opposite-phase superposition of the counter sound with the noise to be damped results, which the background noise can be damped more or less strongly.
- the mechanical power required to drive the piston 5 is relatively low, since the piston 5 only comparatively must produce low pressures. Furthermore, the seal must of the piston 5 with respect to the cylinder chamber 4 is not high Requirements met. For example, a possibly existing Annular gap between the piston 5 and cylinder space 4 though cause an acoustic short circuit, but this is on limited to very low frequencies, reducing the mode of action the silencer according to the invention not or only slightly is impaired. These reduced requirements to the tightness allow friction losses between To reduce piston 5 and cylinder chamber 4.
- a the crank mechanism 12 and the cylinder 4 containing Crankcase be built of sheet metal.
- moving parts such as e.g. the piston and a connecting rod 24 made of plastic getting produced.
- connection is 8 formed open between the cylinder chamber 4 and the conduit 9, to realize an intensive acoustic coupling. If the ambient conditions permit, the Compound 8, for example, with a flexible membrane be sealed gas-tight. The generated by the piston 5 Vibrations can then via the membrane in the line. 9 be coupled. The actuator 15 can influence the coupling then expediently interact with the membrane.
- the silencer according to the invention for the damping of airborne noise in the exhaust line 2 of particular importance is, the muffler 1 in principle also for damping be used by airborne sound in the intake tract 23.
- the muffler 1 for example several cylinder chambers 4 and piston 5 may be provided, the work in parallel.
- different pistons with different Hub frequencies work to different frequencies to dampen in airborne sound.
- crank mechanism leads 12 to a sinusoidal lifting movement of the piston 5.
- This sinusoidal piston movement can always only one interference frequency be damped.
- the drive device 10 may also have a different lifting movement be represented for the piston 5, which for example allows two or more jamming frequencies simultaneously attenuate.
- the drive means 10 a driven independently of the drive shaft 11 Piston actuator may have, the lifting operation the piston 5 is drivingly connected thereto.
- a appropriate control e.g. the controller 17, operated then this piston actuator as a function of the speed of the Drive shaft 11.
- the drive device 10 via a suitable sensor the determine the instantaneous speed of the drive shaft 11.
- the muffler 1 in the embodiment shown here for damping the airborne sound of an internal combustion engine 3 is used is the invention Silencer 1 basically on any machine usable with a rotating drive shaft, depending on their speed produces the airborne sound to be damped.
- the muffler 1 according to the invention therefore with a pump, a compressor or a Compressor are used.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Exhaust Silencers (AREA)
Description
- 1
- Schalldämpfer
- 2
- Abgasstrang
- 3
- Verbrennungskraftmaschine
- 4
- Zylinderraum/Hohlkörper
- 5
- Kolben
- 6
- Hubrichtung
- 7
- Boden/Wand
- 8
- Verbindung
- 9
- Leitung
- 10
- Antriebseinrichtung
- 11
- Antriebswelle
- 12
- Kurbeltrieb
- 13
- Getriebe
- 14
- Amplitudensteuereinrichtung
- 15
- Steuerglied
- 16
- Steuergliedaktuator
- 17
- Steuerung
- 18
- Steuerleitung
- 19
- Signalleitung
- 20
- Pedalwinkel
- 21
- Gaspedal
- 22
- Drosselklappe
- 23
- Ansaugstrang
- 24
- Pleuelstange
Claims (15)
- Aktiver Schalldämpfer zum Dämpfen von Luftschall, den eine Maschine (3) mit einer rotierenden Antriebswelle (11) in Abhängigkeit ihrer Drehzahl erzeugt, mit wenigstens einem Hohlkörper (4), der wenigstens eine bewegliche Wand (6) zur Erzeugung von Gegenschall enthält und über eine Verbindung (8) mit einer zur Führung des zu dämpfenden Luftschalls geeigneten Leitung (9) akustisch gekoppelt ist, und mit einer Antriebseinrichtung (10) zum Bewegen der beweglichen Wand (6),
dadurch gekennzeichnet, daß die bewegliche Wand durch einen Boden (6) eines Kolbens (5) gebildet ist und daß der Hohlkörper durch einen Zylinderraum (4) gebildet ist, in dem der Kolben (5) bewegbar angeordnet ist. - Schalldämpfer nach Anspruch 1,
dadurch gekennzeichnet, daß die Antriebseinrichtung (10) den Kolben (5) so bewegt, daß die Hubfrequenz des Kolbens (5) in einem konstanten Verhältnis zur Drehzahl oder Drehfrequenz der Maschine (3) steht. - Schalldämpfer nach Anspruch 1 oder 2,
dadurch gekennzeichnet, daß die Antriebseinrichtung (10) den Kolben (5) so bewegt, daß die Hubbewegung des Kolbens (5) Gegenschall zur Bedämpfung einer oder mehrerer von der Maschinendrehzahl abhängigen Störfrequenz(en) erzeugt. - Schalldämpfer nach einem der Ansprüche 1 bis 3,
dadurch gekennzeichnet, daß die Antriebseinrichtung (10) den Kolben (5) bei allen Hubfrequenzen mit einem konstanten Hub bewegt. - Schalldämpfer nach einem der Ansprüche 1 bis 4,
dadurch gekennzeichnet, daß eine Amplitudensteuereinrichtung (14) zum Einstellen der Amplitude des Gegenschalls vorgesehen ist, die ein Steuerglied (15) aufweist, das in Abhängigkeit seiner Betätigung die beiden gegeneinander wirkenden Schallfelder über die Verbindung (8) mehr oder weniger akustisch koppelt. - Schalldämpfer nach Anspruch 5,
dadurch gekennzeichnet, daß die Amplitudensteuereinrichtung (14) das Steuerglied (15) in Abhängigkeit der Maschinendrehzahl und/oder der Maschinenleistung betätigt. - Schalldämpfer nach Anspruch 5 oder 6,
dadurch gekennzeichnet, daß zur Betätigung des Steuerglieds (15) ein elektrischer oder elektromagnetischer oder hydraulischer oder pneumatischer oder mechanischer Steuergliedaktuator (16) vorgesehen ist, der mit dem Steuerglied (15) antriebsverbunden ist. - Schalldämpfer nach einem der Ansprüche 1 bis 7,
dadurch gekennzeichnet, daß der Kolben (5) über die Antriebseinrichtung (10) mit der Antriebswelle (11) der Maschine (3) antriebsverbunden ist. - Schalldämpfer nach Anspruch 8,
dadurch gekennzeichnet, daß die Antriebseinrichtung (10) ein Getriebe (13) enthält, das die Maschinendrehzahl bei allen Maschinendrehzahlen mit einem konstanten Übersetzungsverhältnis in die Hubfrequenz des Kolbens (5) übersetzt. - Schalldämpfer nach Anspruch 8 oder 9,
dadurch gekennzeichnet, daß die Antriebseinrichtung (10) einen Kurbeltrieb (12) aufweist, der eine von der Antriebswelle (11) abgenommene eingangsseitige Drehbewegung in eine ausgangsseitige bidirektionale Hubbewegung des Kolbens (5) umwandelt. - Schalldämpfer nach einem der Ansprüche 1 bis 7,
dadurch gekennzeichnet, daß die Antriebseinrichtung (10) einen elektrischen oder elektromagnetischen oder hydraulischen oder pneumatischen Kolbenaktuator aufweist, der mit dem Kolben (5) antriebsverbunden ist, und daß die Antriebseinrichtung (10) eine Steuerung aufweist, die den Kolbenaktuator in Abhängigkeit der Maschinendrehzahl betätigt. - Schalldämpfer nach Anspruch 11,
dadurch gekennzeichnet, daß die Antriebseinrichtung (10) eine Sensorik aufweist, die ein mit der Maschinendrehzahl korreliertes Signal ermittelt. - Schalldämpfer nach einem der Ansprüche 1 bis 12,
dadurch gekennzeichnet, daß bei einer als Kolbenmotor ausgebildeten Maschine (3) mit n Zündvorgängen pro Umdrehung der Antriebswelle (11) die Hubfrequenz des Kolbens (5) das n-fache der Drehfrequenz der Antriebswelle (11) ist. - Schalldämpfer nach einem der Ansprüche 1 bis 13,
dadurch gekennzeichnet, daß die Maschine (3) eine Verbrennungskraftmaschine, ein Kompressor, eine Pumpe oder ein Verdichter ist. - Schalldämpfer nach einem der Ansprüche 1 bis 14,
dadurch gekennzeichnet, daß bei einer als Verbrennungskraftmaschine ausgebildeten Maschine (3) die zur Führung des zu bedämpfenden Luftschalls geeignete Leitung (9) durch den Abgasstrang (2) oder den Ansaugstrang (23) der Verbrennungskraftmaschine (3) gebildet ist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE2001159487 DE10159487C1 (de) | 2001-12-04 | 2001-12-04 | Aktiver Schalldämpfer für Abgasanlagen |
DE10159487 | 2001-12-04 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1318281A2 EP1318281A2 (de) | 2003-06-11 |
EP1318281A3 EP1318281A3 (de) | 2004-01-07 |
EP1318281B1 true EP1318281B1 (de) | 2005-08-31 |
Family
ID=7707965
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20020018051 Expired - Lifetime EP1318281B1 (de) | 2001-12-04 | 2002-08-13 | Aktiver Schalldämpfer für Abgasanlagen |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP1318281B1 (de) |
DE (2) | DE10159487C1 (de) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102005011747B3 (de) * | 2005-03-11 | 2006-06-29 | Benteler Automobiltechnik Gmbh | Aktiver Abgasschalldämpfer |
DE102005019459B3 (de) * | 2005-04-25 | 2006-07-13 | Benteler Automobiltechnik Gmbh | Aktiver Ansaugschalldämpfer |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
SU850875A1 (ru) * | 1979-10-01 | 1981-07-30 | За витель | Устройство дл глушени шума в воздуховоде |
US5319165A (en) | 1990-04-25 | 1994-06-07 | Ford Motor Company | Dual bandpass secondary source |
GB2253076B (en) * | 1991-02-21 | 1994-08-03 | Lotus Car | Method and apparatus for attenuating acoustic vibrations in a medium |
JP2820347B2 (ja) * | 1992-02-26 | 1998-11-05 | 日立造船株式会社 | ダクト内騒音の消音用音圧発生装置 |
US5336856A (en) | 1992-07-07 | 1994-08-09 | Arvin Industries, Inc. | Electronic muffler assembly with exhaust bypass |
JPH08246969A (ja) | 1995-03-15 | 1996-09-24 | Unisia Jecs Corp | 自動車用アクティブ騒音制御装置 |
DE19751596A1 (de) * | 1997-11-21 | 1999-06-02 | Leistritz Abgastech | Aktiver Schalldämpfer |
EP0916817B1 (de) | 1997-11-18 | 2006-02-08 | Faurecia Abgastechnik GmbH | Aktiver Schalldämpfer |
JP2000130145A (ja) * | 1998-10-29 | 2000-05-09 | Osaka Gas Co Ltd | 能動消音装置 |
-
2001
- 2001-12-04 DE DE2001159487 patent/DE10159487C1/de not_active Expired - Fee Related
-
2002
- 2002-08-13 EP EP20020018051 patent/EP1318281B1/de not_active Expired - Lifetime
- 2002-08-13 DE DE50204073T patent/DE50204073D1/de not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
DE50204073D1 (de) | 2005-10-06 |
DE10159487C1 (de) | 2003-02-20 |
EP1318281A2 (de) | 2003-06-11 |
EP1318281A3 (de) | 2004-01-07 |
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