EP0164515B1 - Internal combustion engine with a comprex pressure wave machine and an exhaust gas reservoir - Google Patents

Internal combustion engine with a comprex pressure wave machine and an exhaust gas reservoir Download PDF

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Publication number
EP0164515B1
EP0164515B1 EP85104198A EP85104198A EP0164515B1 EP 0164515 B1 EP0164515 B1 EP 0164515B1 EP 85104198 A EP85104198 A EP 85104198A EP 85104198 A EP85104198 A EP 85104198A EP 0164515 B1 EP0164515 B1 EP 0164515B1
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EP
European Patent Office
Prior art keywords
internal combustion
combustion engine
exhaust gas
plenum chamber
pressure wave
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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
Application number
EP85104198A
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German (de)
French (fr)
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EP0164515A1 (en
Inventor
Jakob Dr. Keller
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BBC Brown Boveri AG Switzerland
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BBC Brown Boveri AG Switzerland
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    • 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
    • F01N13/10—Other arrangements or adaptations of exhaust conduits of exhaust manifolds
    • 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
    • F01N1/20—Silencing apparatus characterised by method of silencing by using movable parts having oscillating or vibrating 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
    • F01N1/22—Silencing apparatus characterised by method of silencing by using movable parts the parts being resilient walls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/32—Engines with pumps other than of reciprocating-piston type
    • F02B33/42—Engines with pumps other than of reciprocating-piston type with driven apparatus for immediate conversion of combustion gas pressure into pressure of fresh charge, e.g. with cell-type pressure exchangers

Description

Die Erfindung betrifft eine mittels gasdynamischer Druckwellenmaschine aufgeladene Brennkraftmaschine mit Abgassammelbehälter.The invention relates to an internal combustion engine with an exhaust gas collector that is charged by means of a gas dynamic pressure wave machine.

Ein solcher Abgassammelbehälter dient einerseits dazu, die Abgasmassenströme, welche von den einzelnen Zylindern eines Motors abgegeben werden, zusammenzufassen. Andererseits schwächt ein Abgasreceiver die vom Motor verursachten Pulsationen ab. Diese Abschwächungswirkung ist von besonderer Bedeutung, wenn ein Motor von einer gasdynamischen Druckwellenmaschine aufgeladen wird. Zu starke Abgaspulsationen können den Aufladungsprozess in der Druckwellenmaschine empfindlich beeinträchtigen, weil sie zu Schwankungen der Wellenlaufzeiten führen. Zur Funktionsweise einer Druckwellenmaschine wird auf die CH-A-378 595 oder auf die Druckschrift CH-T 123 143 der Anmelderin verwiesen.Such an exhaust gas collector serves on the one hand to combine the exhaust gas mass flows which are emitted by the individual cylinders of an engine. On the other hand, an exhaust gas receiver weakens the pulsations caused by the engine. This weakening effect is of particular importance when an engine is being charged by a gas dynamic pressure wave machine. Excessive exhaust gas pulsations can severely impair the charging process in the pressure wave machine because they lead to fluctuations in the wave travel times. For the functioning of a pressure wave machine, reference is made to CH-A-378 595 or to CH-T 123 143 of the applicant.

Nun stellt jedoch die Wahl des Volumens eines Abgasreceivers in jedem Fall einen Kompromiss dar. Einerseits ist ein grosses Volumen vorteilhaft, weil die Abschwächung der Pulsationen mit zunehmendem Volumen stärker wird. Andererseits führt ein grosses Volumen aber zu einem verzögerten Ansprechen des Laders auf Last- und Drehzahländerungen, weil die Zeit für die Spülung des Abgassammelbehälters mit grösser werdendem Volumen zunimmt. Besonders schwierig wird ein solcher Kompromiss bei schwach aufgeladenen Motoren mit kleiner Zylinderzahl. Bei kleiner Zylinderzahl ist die Glättungswirkung auf die Abgaspulsationen durch das Zusammenfassen der von den einzelnen Zylindern abgegebenen Teilmassenströme schwach oder gar nicht vorhanden. Ausserdem ist die Pulsationsfrequenz niedrig und macht ein entsprechend grosses Receivervolumen für eine wirksame Abschwächung erforderlich. Hinzu kommt noch, dass die Wirksamkeit des Abgassammelbehälters mit abnehmender Aufladung schwächer wird. Bei einem schwach aufgeladenen Zweizylinder-Dieselmotor ist man beispielsweise bei dieser Kompromissfindung vor ein fast unlösbares Problem gestellt.However, the choice of the volume of an exhaust gas receiver is always a compromise. On the one hand, a large volume is advantageous because the weakening of the pulsations increases with increasing volume. On the other hand, a large volume leads to a delayed response of the charger to changes in load and speed, because the time for purging the exhaust gas collector increases with increasing volume. Such a compromise becomes particularly difficult with weakly charged engines with a small number of cylinders. If the number of cylinders is small, the smoothing effect on the exhaust gas pulsations is weak or nonexistent due to the combination of the partial mass flows emitted by the individual cylinders. In addition, the pulsation frequency is low and requires a correspondingly large receiver volume for an effective attenuation. In addition, the effectiveness of the flue gas collector becomes weaker as the charge decreases. With a weakly charged two-cylinder diesel engine, for example, this compromise is faced with an almost insoluble problem.

Hier will die Erfindung Abhilfe schaffen.The invention seeks to remedy this.

Ausgehend von der Erkenntnis, dass die von einem Abgassammelbehälter bewirkte Abschwächung von Druckpulsationen nicht in einem direkten Zusammenhang mit der Grösse seines Volumens steht, sondern mit der Federwirkung des Behälterinhaltes, liegt der Erfindung, wie sie in den Ansprüchen definiert ist, die Aufgabe zugrunde, die Wirksamkeit eines kleinen Abgassammelbehälters insbesondere bei Brennkraftmaschinen mit niedriger Zylinderzahl und/oder schwachem Aufladegrad zu verbessern.Based on the knowledge that the attenuation of pressure pulsations caused by an exhaust gas collection container is not directly related to the size of its volume, but rather to the spring action of the contents of the container, the invention as defined in the claims is based on the object To improve the effectiveness of a small exhaust gas collector, in particular in internal combustion engines with a low number of cylinders and / or a weak degree of charging.

Der Vorteil der Erfindung ist darin zu sehen, dass durch die Verbesserung der Federwirkung mittels mechanischen Federmitteln das Sammelbehältervolumen klein gehalten werden kann.The advantage of the invention can be seen in the fact that by improving the spring action by means of mechanical spring means, the volume of the collecting container can be kept small.

In der Zeichnung sind zwei Ausführungsbeispiele der Erfindung in ihrer Anwendung für einen zweizylindrigen Motor schematisch dargestellt.In the drawing, two exemplary embodiments of the invention are shown schematically in their application for a two-cylinder engine.

Es zeigt :

  • Fig. 1 einen ersten Abgassammelbehälter mit eingebauter Feder,
  • Fig. 2 eine zweite Ausführungsvariante.
It shows :
  • 1 shows a first exhaust gas collector with a built-in spring,
  • Fig. 2 shows a second embodiment.

Alle für das Verständnis der Erfindung unwesentlichen Elemente wie beispielsweise der Verbrennungsmotor, die Druckwellenmaschine sowie zugehörige Leitungen sind fortgelassen. Die Strömungsrichtung der Motorabgase ist mit Pfeilen bezeichnet.All elements that are not essential for understanding the invention, such as, for example, the internal combustion engine, the pressure wave machine and associated lines have been omitted. The direction of flow of the engine exhaust is indicated by arrows.

Gemäss Fig. 1 besteht der Abgassammelbehälter im wesentlichen aus einer inneren Kammer 1, die vom Gas durchströmt ist und einer äusseren Schallabschirmung 2. Sehr vereinfacht dargestellt sind die Zuströmkanäle 6', 6" von den Zylindern sowie der Abströmkanal 7 zur Druckwellenmaschine. Die mechanischen Federmittel sind hier eine gewellte Federstahlmembran 3', die sich über die ganze aktive Länge des Behälters erstreckt und an dessen Stirnseiten eingespannt ist. Die Einspannung ist gasdicht. Die Membran 3' verläuft zwischen der strömungsbegrenzenden Wand 4 der Kammer 1 und der Schallabschirmung 2 und bildet mit letzterer ein Totvolumen 5. Die Tatsache, dass zwischen der Kammer 1 und der Membran 3' ein weiterer nicht durchströmter Raum besteht, ist im vorliegenden Zusammenhang erfindungsunwesentlich.1, the exhaust gas collection container essentially consists of an inner chamber 1 through which the gas flows and an outer sound shield 2. The inflow ducts 6 ', 6 "from the cylinders and the outflow duct 7 to the pressure wave machine are shown in very simplified form. The mechanical spring means Here are a corrugated spring steel membrane 3 ', which extends over the entire active length of the container and is clamped on the end faces. The clamping is gas-tight. The membrane 3' runs between the flow-limiting wall 4 of the chamber 1 and the sound shield 2 and forms the latter a dead volume 5. The fact that there is another space through which there is no flow between the chamber 1 and the membrane 3 'is not essential to the invention in the present context.

Die zugrundeliegende Idee ist nun, das Gesamtvolumen des Sammelbehälters möglichst klein zu halten aufgrund der Massnahme, die Federwirkung des Behälterinhaltes zu vergrössern.The basic idea is now to keep the total volume of the collecting container as small as possible due to the measure to increase the spring effect of the container contents.

Wird der aus den Kanälen 6', 6" eintretende Massenstrom mit 01 und der in den Kanal 7 austretende Massenstrom mit O2 bezeichnet, so lautet die quasi-stationäre Kontinuitätsgleichung

Figure imgb0001
worin VR das Behältervolumen und p die Gasdichte im Behälter bedeuten.If the mass flow entering channels 6 ', 6 "is denoted by 0 1 and the mass flow exiting channel 7 is denoted by O 2 , then the quasi-stationary continuity equation is
Figure imgb0001
 where V R is the container volume and p is the gas density in the container.

Der zweite Term auf der rechten Seite dieser Gleichung wäre auf eine mechanische Federwirkung des Volumens zurückzuführen. Ist die Eigenfrequenz dieser Feder wesentlich grösser als die Pulsationsfrequenz, dann ist

Figure imgb0002
worin k eine dimensionslose « Federkonstante ist •. Für den beispielsweisen Zwei-Zylinder-Motor sollte k mindestens dem zwei- bis vier-fachen Wert von VHNR entsprechen, wobei VH das Hubvolumen des Motors bezeichnet.The second term on the right side of this equation would be due to a mechanical spring action of the volume. If the natural frequency of this spring is significantly greater than the pulsation frequency, then
Figure imgb0002
 where k is a dimensionless «spring constant •. For the two-cylinder engine, for example, k should correspond to at least two to four times the value of V H N R , where V H denotes the displacement of the engine.

Bei der in Fig. 2 gezeigten Variante, bei welcher die gleichen Elemente dieselben Bezugszeichen wie in Fig. 1 tragen, werden die strömungsbegrenzenden Wände 4 durch die federnden Mittel selbst gebildet. Es handelt sich hierbei um Federstahlbleche 3", welche an der Eintrittsseite des Sammelbehälters eingespannt sind. Austrittsseitig streifen die Blechenden mit geringem Spiel an der stirnseitigen Behälterbegrenzung vorbei, die hierzu entsprechend gekrümmt ist. Spielbedingte Leckagen, die um das Federblech herum in das Totvolumen 5 strömen, verursachen aufgrund der relativ hohen Pulsationsfrequenz nur unwesentliche Störungen.In the variant shown in Fig. 2, in which the same elements have the same reference numerals as in Fig. 1, the flow-limiting walls 4 are formed by the resilient means themselves. These are spring steel sheets 3 ", which are clamped on the entry side of the collecting container. On the exit side, the sheet ends graze past the end of the container with little play, which is curved accordingly. Leakages due to play that flow around the spring plate into the dead volume 5 , cause only insignificant interference due to the relatively high pulsation frequency.

Claims (3)

1. Internal combustion engine supercharged by means of gas-dynamic pressure-wave machine and with exhaust plenum chamber, characterized in that, to increase the spring effect of the plenum chamber volume, mechanical spring means (3', 3") are arranged, which subdivide the inside of the plenum chamber into a flow chamber (1) and a dead volume (5)..
2. Internal combustion engine according to Claim 1, characterized in that the spring means are formed by a corrugated spring steel diaphragm (3'), which extends substantially over the entire length of the exhaust plenum chamber and is fastened, preferably gas-tightly, at the faces of the latter.
3. Internal combustion engine according to Claim 1, characterized in that the spring means are formed by spring steel plates (3"), which are restrained at one side, preferably the intake side, on the plenum chamber and at their other end skirt past the plenum chamber limitation.
EP85104198A 1984-04-19 1985-04-06 Internal combustion engine with a comprex pressure wave machine and an exhaust gas reservoir Expired EP0164515B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH198684 1984-04-19
CH1986/84 1984-04-19

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EP0164515A1 EP0164515A1 (en) 1985-12-18
EP0164515B1 true EP0164515B1 (en) 1988-01-20

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EP (1) EP0164515B1 (en)
JP (1) JPS60237120A (en)
DE (1) DE3561480D1 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4932372A (en) * 1988-05-02 1990-06-12 Pacific Diesel Brake Co. Apparatus and method for retarding a turbocharged engine
DE102004034206B4 (en) * 2004-07-14 2007-02-22 J. Eberspächer GmbH & Co. KG Silencer for an exhaust system
US20080264719A1 (en) * 2007-04-27 2008-10-30 Denso Corporation Silencer
US8221073B2 (en) * 2008-12-22 2012-07-17 Pratt & Whitney Canada Corp. Exhaust gas discharge system and plenum
US9422843B2 (en) * 2013-09-08 2016-08-23 Michael Wayne Barrett Resonance generating muffler
CN108843435A (en) * 2018-06-12 2018-11-20 蒙城县傲尊电子科技有限公司 A kind of potent noise reduction automobile exhaust pipe

Family Cites Families (13)

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Publication number Priority date Publication date Assignee Title
US1975483A (en) * 1931-09-22 1934-10-02 Semple S Scott Muffler
US2110986A (en) * 1933-08-01 1938-03-15 Kadenacy Michel Exhaust device for explosion or internal combustion engines
DE815867C (en) * 1949-07-09 1951-10-04 Tydens Patenter Ab Device on sound absorbers for internal combustion engines, compressors, etc. like
US2841237A (en) * 1953-12-14 1958-07-01 Slayter Games Muffler structure
US2875787A (en) * 1956-03-27 1959-03-03 Westinghouse Air Brake Co Pulsation dampener device
US3237715A (en) * 1959-09-15 1966-03-01 Joseph J Mascuch Flexible hose structures
US3180077A (en) * 1962-03-20 1965-04-27 Ite Circuit Breaker Ltd Wave machine to initiate scavenging of internal combustion
FR1321931A (en) * 1962-05-12 1963-03-22 Quiet
DE1228857B (en) * 1965-03-27 1966-11-17 Maschf Augsburg Nuernberg Ag Exhaust gas turbine for piston internal combustion engines
DE2831889A1 (en) * 1978-07-20 1980-02-07 Bbc Brown Boveri & Cie METHOD AND DEVICE FOR CHARGING A MULTI-CYLINDER PISTON COMBUSTION ENGINE
US4314621A (en) * 1979-03-07 1982-02-09 Caterpillar Tractor Co. Fluidborne noise attenuator
JPS5618017A (en) * 1979-07-19 1981-02-20 Mitsubishi Motors Corp Exhaust pipe for vehicle
JPS58158312A (en) * 1982-03-17 1983-09-20 Nissan Motor Co Ltd Premuffler

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JPS60237120A (en) 1985-11-26
DE3561480D1 (en) 1988-02-25
US4763471A (en) 1988-08-16
EP0164515A1 (en) 1985-12-18

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