EP0899434A1 - Aerodyamic pressure wave machine - Google Patents

Aerodyamic pressure wave machine Download PDF

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Publication number
EP0899434A1
EP0899434A1 EP97810614A EP97810614A EP0899434A1 EP 0899434 A1 EP0899434 A1 EP 0899434A1 EP 97810614 A EP97810614 A EP 97810614A EP 97810614 A EP97810614 A EP 97810614A EP 0899434 A1 EP0899434 A1 EP 0899434A1
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EP
European Patent Office
Prior art keywords
pressure
wave machine
duct
pressure wave
charge air
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
EP97810614A
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German (de)
French (fr)
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EP0899434B1 (en
Inventor
Roger Martin
Urs Wenger
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Swissauto Engineering SA
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Swissauto Engineering SA
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Filing date
Publication date
Priority to EP97810614A priority Critical patent/EP0899434B1/en
Application filed by Swissauto Engineering SA filed Critical Swissauto Engineering SA
Priority to ES97810614T priority patent/ES2225946T3/en
Priority to DE59711832T priority patent/DE59711832D1/en
Priority to AT97810614T priority patent/ATE272788T1/en
Priority to AU95334/98A priority patent/AU728535B2/en
Priority to KR1020007002046A priority patent/KR20010023404A/en
Priority to JP2000508894A priority patent/JP4190726B2/en
Priority to US09/486,452 priority patent/US6314951B1/en
Priority to PCT/EP1998/005379 priority patent/WO1999011915A1/en
Publication of EP0899434A1 publication Critical patent/EP0899434A1/en
Application granted granted Critical
Publication of EP0899434B1 publication Critical patent/EP0899434B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F02B33/02—Engines with reciprocating-piston pumps; Engines with crankcase pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F13/00—Pressure exchangers
    • 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
    • F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
    • F01N3/08—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous
    • F01N3/10—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust
    • F01N3/18—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by methods of operation; Control
    • F01N3/22—Control of additional air supply only, e.g. using by-passes or variable air pump drives
    • 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
    • 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
    • F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
    • F01N3/08—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous
    • F01N3/10—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust
    • F01N3/24—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by constructional aspects of converting apparatus
    • F01N3/30—Arrangements for supply of additional air

Definitions

  • the present invention relates to a gas dynamic pressure wave machine according to the preamble of independent claim.
  • Pressure wave machine is known from the prior art for example from CH-A-681 738.
  • the standard pressure wave machine is for high boost pressures and good efficiencies strongly dependent on filling. At deep Internal combustion engine throughput decreases the filling in the rotor Pressure wave machine and thus also the boost pressure. The The machine is actually too big in this map area. With a high internal combustion engine throughput, the filling increases strongly and the compression efficiency deteriorates yourself. The pressure wave machine is in this map area actually too small.
  • FIG. 1 For the sake of simplicity, the processing according to FIG. 1 a pressure wave cycle is shown and described while a two-cycle machine is shown in FIGS is.
  • the invention is based on the number of pressure wave cycles regardless, it can be used for pressure wave machines with only one cycle or with two or more cycles become.
  • Figure 1 shows a development of the rotor Pressure wave machine according to the prior art and you can see the internal combustion engine 1, the gas dynamic Pressure wave machine 2, the high pressure exhaust duct 3 and Low-pressure exhaust duct 4 including the purge air S, the rotor 6 with the individual cells 18, the fresh air inlet 8, or low-pressure fresh air supply duct 14, the high-pressure charge air duct 10, which merges into the charge air duct 11 and leads to the internal combustion engine 1.
  • FIG. 2 and 3 is an inventive Gas dynamic pressure wave machine shown on the one Plenty of improvements have been made to to increase the overall efficiency significantly.
  • the Pressure wave machine 30 is via the high-pressure exhaust duct 31 and the high pressure charge air duct 32 with the schematic shown internal combustion engine 33 connected.
  • in the Gas housing 34 is also the low pressure exhaust duct 35, and it can be seen from this figure that the two channels, d. H. the high pressure exhaust duct and the Low-pressure exhaust duct, in the gas housing on the rotor side as sector-shaped openings, each with an opening edge 36, or 37 lead.
  • the rotor 40 can also be seen with its Cells 41, the rotor being arranged in a jacket 42 and driven, for example, by a belt drive 43 becomes.
  • the pressure wave machine is an open system, and that means that between the exhaust part and the Fresh air section a direct connection via the rotor consists. This also causes the engine pressure pulsations from the exhaust gas high pressure section to the fresh air high pressure section transfer.
  • the connecting line 46, the High-pressure charge air duct 32 into the high-pressure exhaust duct 31 leads.
  • the connecting line contains a Check valve 47, optionally with a electronic control is provided. It works Check valve as a regulation in the sense that only Pressure surges are transmitted, their energetic level is higher than the current pressure in the high-pressure exhaust duct.
  • the negative pressure pulses i. H.
  • Branch that in Figure 2 or 3 somewhere between the High pressure charge air duct edge and the engine intake is arranged, directly after the opening edge of the high-pressure charge air duct is arranged.
  • This variant is the Not shown for clarity.
  • the pressure wave machine is after State of the art heavily dependent on filling.
  • Reduction of pressure pulsations as described above allows the provision of a connecting line Return of charge air to the high-pressure exhaust side of the Pressure wave machine, thereby increasing the Mass throughput of the machine and thus an increase in Filling levels, which results in a significant increase in pressure noticeable.
  • An additional regulation of the returned Fresh air high pressure volume by means of the regulated Check valve can therefore be used to control the charge pressure in the general and in addition to the Otto engine Power control can be used.
  • the pressure wave machine to improve compression efficiency at higher Engine throughputs can be dimensioned somewhat larger, without increasing the boost pressure at lower engine throughputs to lose.
  • This can also be done, for example, by that the cross section of the connecting channel by means of a suitable, known device is regulated, wherein either the regulated check valve or one additional cross-sectional control can be used. This is particularly effective in the lower to middle Speed, temperature and load range of the Internal combustion engine.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Health & Medical Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Toxicology (AREA)
  • Supercharger (AREA)
  • Characterised By The Charging Evacuation (AREA)
  • Motor Or Generator Frames (AREA)
  • Mechanical Treatment Of Semiconductor (AREA)

Abstract

The pressure wave machine has a rotor (40) with cells (41), a low-pressure fresh air input channel (38), a high-pressure air charging channel (32), a high-pressure exhaust channel (31) and a low-pressure exhaust channel (35). The two exhaust channels are in a gas casing (34) and the high-pressure air charging channel is in an air casing (39). A direct connection line (46) is fitted between the high-pressure air charging channel and the high-pressure exhaust channel. There should preferably be a non-return valve (47) in this line.

Description

Die vorliegende Erfindung bezieht sich auf eine gasdynamische Druckwellenmaschine gemäss dem Oberbegriff des unabhängigen Patentanspruchs. Eine solche Druckwellenmaschine ist aus dem Stand der Technik bekannt, beispielsweise aus der CH-A-681 738.The present invention relates to a gas dynamic pressure wave machine according to the preamble of independent claim. Such Pressure wave machine is known from the prior art for example from CH-A-681 738.

Da die Druckwellenmaschine nach Stand der Technik konzeptbedingt nur mit einem möglichst pulsationsfreien Gleichdrucksystem gute Wirkungsgrade liefert, wird vor der Druckwellenmaschine ein Volumen in den Abgassammler integriert, um die Motorpulsationen zu dämpfen. Ohne diese Dämpfung würden die harten Motorpulsationen vor allem bei tieferen Motordrehzahlen durch den Abgaskanal des Gasgehäuses der Druckwellenmaschine in den Rotor eindringen und den eigentlichen Druckwellenprozess der Druckwellenmaschine stören, was sich in einer deutlichen Verschlechterung der Wirkungsgrade und erhöhter Rezirkulation bemerkbar macht. Das im Abgassammler vor der Druckwellenmaschine integrierte, relativ grosse Volumen vermag nur einen Teil dieser Pulsationen zu dämpfen, nicht aber zu beseitigen. Ebenso hat ein solches Abgassammler-Volumen den Nachteil des grösseren Bauvolumens und der grösseren Wärmekapazität.Because the pressure wave machine according to the prior art conceptually only with a pulsation-free as possible Equilibrium pressure system delivers good efficiencies before Pressure wave machine a volume in the exhaust manifold integrated to dampen the engine pulsations. Without these The hard engine pulsations would dampen above all lower engine speeds through the exhaust duct of the Penetrate the gas casing of the pressure wave machine into the rotor and the actual pressure wave process of Pressure wave machine interfere, which can be seen in a clear Degradation of efficiency and increased Recirculation noticeable. That in the exhaust collector in front of the Pressure wave machine integrated, relatively large volume can only dampen part of these pulsations, not but to eliminate. Such an exhaust manifold volume also has the disadvantage of the larger volume and the greater heat capacity.

Die Standard-Druckwellenmaschine ist für hohe Ladedrücke und gute Wirkungsgrade stark füllungsabhängig. Bei tiefem Verbrennungsmotor-Durchsatz sinkt die Füllung im Rotor der Druckwellenmaschine und somit auch der Ladedruck. Die Maschine ist in diesem Kennfeldbereich eigentlich zu gross. Bei hohem Verbrennungsmotor-Durchsatz steigt die Füllung stark an und der Kompressionswirkungsgrad verschlechtert sich. In diesem Kennfeldbereich ist die Druckwellenmaschine also eigentlich zu klein. The standard pressure wave machine is for high boost pressures and good efficiencies strongly dependent on filling. At deep Internal combustion engine throughput decreases the filling in the rotor Pressure wave machine and thus also the boost pressure. The The machine is actually too big in this map area. With a high internal combustion engine throughput, the filling increases strongly and the compression efficiency deteriorates yourself. The pressure wave machine is in this map area actually too small.

Es ist von diesem Stand der Technik ausgehend Aufgabe der vorliegenden Erfindung eine Druckwellenmaschine anzugeben, die bei kleinerem Abgassammler-Volumen die schädlichen Pulsationen beseitigt und den Kompressions-Wirkungsgrad erhöht. Diese Aufgabe wird mit einer Druckwellenmaschine nach Anspruch 1 gelöst.Starting from this prior art, it is the task of present invention to provide a pressure wave machine, which are harmful when the volume of the exhaust manifold is smaller Pulsations are eliminated and compression efficiency elevated. This task is done with a pressure wave machine solved according to claim 1.

Weitere Vorteile und Ausführungsbeispiele der erfindungsgemässen Druckwellenmaschine sind in den abhängigen Ansprüchen definiert.Further advantages and embodiments of the Pressure wave machine according to the invention are in the dependent claims defined.

Die Erfindung wird im folgenden anhand einer Zeichnung von Ausführungsbeispielen näher erläutert.

Figur 1
zeigt schematisch einen abgewickelten zylindrischen Schnitt durch die Zellen eines Rotors einer Druckwellenmaschine gemäss Stand der Technik,
Figur 2
zeigt eine allgemeine Darstellung einer erfindungsgemässen gasdynamischen Druckwellenmaschine, und
Figur 3
zeigt in perspektivischer Sicht die gasdynamische Druckwellenmaschine gemäss Figur 2.
The invention is explained in more detail below with reference to a drawing of exemplary embodiments.
Figure 1
schematically shows a developed cylindrical section through the cells of a rotor of a pressure wave machine according to the prior art,
Figure 2
shows a general representation of a gas dynamic pressure wave machine according to the invention, and
Figure 3
shows a perspective view of the gas dynamic pressure wave machine according to FIG. 2.

Der Einfachheit halber ist in der Abwicklung gemäss Figur 1 ein Druckwellen-Zyklus dargestellt und beschrieben, während in den Figuren 2 und 3 eine Zwei-Zyklusmaschine dargestellt ist. Die Erfindung ist jedoch von der Anzahl Druckwellen-Zyklen unabhängig, sie kann für Druckwellenmaschinen mit nur einem Zyklus oder aber mit zwei oder mehr Zyklen angewandt werden. For the sake of simplicity, the processing according to FIG. 1 a pressure wave cycle is shown and described while a two-cycle machine is shown in FIGS is. However, the invention is based on the number of pressure wave cycles regardless, it can be used for pressure wave machines with only one cycle or with two or more cycles become.

Figur 1 zeigt eine Abwicklung des Rotors einer Druckwellenmaschine gemäss Stand der Technik und man erkennt die Verbrennungsmaschine 1, die gasdynamische Druckwellenmaschine 2, den Hochdruck-Abgaskanal 3 und den Niederdruck-Abgaskanal 4 inklusive der Spülluft S, den Rotor 6 mit den einzelnen Zellen 18, den Frischlufteintritt 8, bzw. Niederdruck-Frischluftzufuhrkanal 14, den Hochdruck-Ladeluftkanal 10, der in den Ladeluftkanal 11 übergeht und zur Verbrennungsmaschine 1 führt.Figure 1 shows a development of the rotor Pressure wave machine according to the prior art and you can see the internal combustion engine 1, the gas dynamic Pressure wave machine 2, the high pressure exhaust duct 3 and Low-pressure exhaust duct 4 including the purge air S, the rotor 6 with the individual cells 18, the fresh air inlet 8, or low-pressure fresh air supply duct 14, the high-pressure charge air duct 10, which merges into the charge air duct 11 and leads to the internal combustion engine 1.

In den Figuren 2 und 3 ist eine erfindungsgemässe gasdynamische Druckwellenmaschine dargestellt, an der eine Vielzahl von Verbesserungen durchgeführt worden sind, um insgesamt den Wirkungsgrad wesentlich zu erhöhen. Die Druckwellenmaschine 30 ist über den Hochdruck-Abgaskanal 31 und den Hochdruck-Ladeluftkanal 32 mit der schematisch dargestellten Verbrennungsmaschine 33 verbunden. Im Gasgehäuse 34 befindet sich ferner der Niederdruck-Abgaskanal 35, und es ist aus dieser Figur ersichtlich, dass die beiden Kanäle, d. h. der Hochdruck-Abgaskanal und der Niederdruck-Abgaskanal, im Gasgehäuse rotorseitig als sektorförmige Oeffnungen mit je einer Oeffnungskante 36, bzw. 37 münden. Man erkennt ferner den Rotor 40 mit seinen Zellen 41, wobei der Rotor in einem Mantel 42 angeordnet ist und beispielsweise durch einen Riemenantrieb 43 angetrieben wird.In Figures 2 and 3 is an inventive Gas dynamic pressure wave machine shown on the one Plenty of improvements have been made to to increase the overall efficiency significantly. The Pressure wave machine 30 is via the high-pressure exhaust duct 31 and the high pressure charge air duct 32 with the schematic shown internal combustion engine 33 connected. in the Gas housing 34 is also the low pressure exhaust duct 35, and it can be seen from this figure that the two channels, d. H. the high pressure exhaust duct and the Low-pressure exhaust duct, in the gas housing on the rotor side as sector-shaped openings, each with an opening edge 36, or 37 lead. The rotor 40 can also be seen with its Cells 41, the rotor being arranged in a jacket 42 and driven, for example, by a belt drive 43 becomes.

Wie bereits eingangs erwähnt, muss das für die vorbekannten Druckwellenmaschinen verwendete Abgassammler-Volumen zur Dämpfung der Motorpulsationen relativ gross sein und vermag trotzdem nicht die schädlichen Pulsationen zu beseitigen. Die Druckwellenmaschine stellt ein offenes System dar, und das heisst, dass zwischen dem Abgasteil und dem Frischluftteil eine direkte Verbindung über den Rotor besteht. Dadurch werden aber auch die Motordruckpulsationen vom Abgas-Hochdruckteil auf den Frischluft-Hochdruckteil übertragen.As already mentioned at the beginning, this has to be done for the previously known Pressure wave machines used exhaust gas collector volume for Damping of the motor pulsations can be relatively large and capable still not eliminate the harmful pulsations. The pressure wave machine is an open system, and that means that between the exhaust part and the Fresh air section a direct connection via the rotor consists. This also causes the engine pressure pulsations from the exhaust gas high pressure section to the fresh air high pressure section transfer.

Durch eine direkte Frischluftzuführung in den Abgaskanal kann nun dieser Nachteil behoben werden. Man erkennt in den Figuren 2 und 3 die Verbindungsleitung 46, die vom Hochdruck-Ladeluftkanal 32 in den Hochdruck-Abgaskanal 31 führt. Dadurch werden die positiven Druckstösse im Hochdruck-Ladeluftkanal auf den Hochdruck-Abgaskanal übertragen. Die Verbindungsleitung enthält ein Rückschlagventil 47, das gegebenenfalls mit einer elektronischen Regelung versehen ist. Dabei wirkt das Rückschlagventil als Regelung in dem Sinne, dass nur Druckstösse übertragen werden, deren energetisches Niveau höher liegt als der momentane Druck im Hochdruck-Abgaskanal. Damit werden vor allem die negativen Druckpulse, d. h. der Zustand des Quasi-Unterdruckes im Hochdruck-Abgaskanal, angehoben und das gesamte Druckniveau sowohl innerhalb des Hochdruck-Abgaskanals als auch des Hochdruck-Ladeluftkanals durch die Glättung der negativen Druckpulse angehoben. Dadurch kann das Druckniveau im Rotor vor dem Öffnen des Hochdruck-Abgaskanals deutlich angehoben werden, und die von dort eintreffenden Pulsationen werden gedämpft. Ausserdem verringert diese Massnahme die Einströmverluste des heissen Abgases in den Rotor, da der ganze Prozess gedämpft wird.Through a direct fresh air supply into the exhaust duct this disadvantage can now be eliminated. One recognizes in the Figures 2 and 3, the connecting line 46, the High-pressure charge air duct 32 into the high-pressure exhaust duct 31 leads. The positive pressure surges in the High-pressure charge air duct on the high-pressure exhaust duct transfer. The connecting line contains a Check valve 47, optionally with a electronic control is provided. It works Check valve as a regulation in the sense that only Pressure surges are transmitted, their energetic level is higher than the current pressure in the high-pressure exhaust duct. In particular, the negative pressure pulses, i. H. of the State of the quasi-negative pressure in the high-pressure exhaust duct, raised and the total pressure level both within the High pressure exhaust duct as well as the high pressure charge air duct raised by smoothing the negative pressure pulses. This allows the pressure level in the rotor to open before opening High-pressure exhaust duct can be raised significantly, and that of Pulsations arriving there are dampened. Furthermore this measure reduces the inflow losses of the hot Exhaust gas in the rotor, since the whole process is damped.

Eine weitere Verbesserung kann erzielt werden, falls die Abzweigung, die in Figur 2 oder 3 irgendwo zwischen der Hochdruck-Ladeluftkanal-Kante und dem Motoreinlass angeordnet ist, direkt nach der Öffnungskante des Hochdruck-Ladeluftkanals angeordnet wird. Diese Variante ist der Übersichtlichkeit halber nicht eingezeichnet. A further improvement can be achieved if the Branch that in Figure 2 or 3 somewhere between the High pressure charge air duct edge and the engine intake is arranged, directly after the opening edge of the high-pressure charge air duct is arranged. This variant is the Not shown for clarity.

Wie bereits erwähnt wurde, ist die Druckwellenmaschine nach Stand der Technik stark füllungsabhängig. Zusätzlich zur Reduzierung der Druckpulsationen, wie oben beschrieben, erlaubt das Vorsehen einer Verbindungsleitung die Rückführung von Ladeluft auf die Hochdruck-Abgasseite der Druckwellenmaschine, dadurch eine Erhöhung des Massendurchsatzes der Maschine und somit eine Erhöhung des Füllgrades, was sich in einer deutlichen Drucksteigerung bemerkbar macht. Eine zusätzliche Regelung der rückgeführten Frischluft-Hochdruckmenge mittels dem geregelten Rückschlagventil kann somit zur Ladedruckregelung im allgemeinen und beim Otto-Motor zusätzlich zur Leistungsregelung verwendet werden.As already mentioned, the pressure wave machine is after State of the art heavily dependent on filling. In addition to Reduction of pressure pulsations as described above allows the provision of a connecting line Return of charge air to the high-pressure exhaust side of the Pressure wave machine, thereby increasing the Mass throughput of the machine and thus an increase in Filling levels, which results in a significant increase in pressure noticeable. An additional regulation of the returned Fresh air high pressure volume by means of the regulated Check valve can therefore be used to control the charge pressure in the general and in addition to the Otto engine Power control can be used.

Das heisst mit anderen Worten, dass die Druckwellenmaschine zur Verbesserung des Kompressionswirkungsgrades bei höheren Motordurchsätzen etwas grösser dimensioniert werden kann, ohne bei tieferen Motordurchsätzen an Ladedruck zu verlieren. Dies kann beispielsweise auch dadurch geschehen, dass der Querschnitt des Verbindungskanals mittels einer geeigneten, bekannten Vorrichtung geregelt wird, wobei entweder das geregelte Rückschlagventil oder eine zusätzliche Querschnittsregelung eingesetzt werden kann. Dies ist besonders wirksam im unteren bis mittleren Drehzahl-, Temperatur- und Lastbereich des Verbrennungsmotors.In other words, the pressure wave machine to improve compression efficiency at higher Engine throughputs can be dimensioned somewhat larger, without increasing the boost pressure at lower engine throughputs to lose. This can also be done, for example, by that the cross section of the connecting channel by means of a suitable, known device is regulated, wherein either the regulated check valve or one additional cross-sectional control can be used. This is particularly effective in the lower to middle Speed, temperature and load range of the Internal combustion engine.

Claims (5)

Gasdynamische Druckwellenmaschine, die bestimmt ist, einer Verbrennungsmaschine Ladeluft zuzuführen, mit einem Zellen (18, 41) aufweisenden Rotor (6, 40), einem Niederdruck-Frischluftzufuhrkanal (14, 38), einem zur Verbrennungsmaschine (1, 33) führenden Hochdruck-Ladeluftkanal (10, 32), einem von der Verbrennungsmaschine herkommenden Hochdruck-Abgaskanal (3, 31) und einem Niederdruck-Abgaskanal (4, 35), wobei der Niederdruck-Abgaskanal (4, 35) und der Hochdruck-Abgaskanal (3, 31) in einem Gasgehäuse (5, 34) und der Niederdruck-Frischluftzufuhrkanal (14, 38) und der Hochdruck-Ladeluftkanal (10, 32) in einem Luftgehäuse (15, 39) angeordnet sind, dadurch gekennzeichnet, dass sie eine Verbindungsleitung (46) zwischen dem Hochdruck-Ladeluftkanal (32) und dem Hochdruck-Abgaskanal (31) aufweist.Gas dynamic pressure wave machine which is intended to supply charge air to an internal combustion engine, with a Cells (18, 41) having a rotor (6, 40), one Low-pressure fresh air supply duct (14, 38), one for Internal combustion engine (1, 33) leading high-pressure charge air duct (10, 32), one from the internal combustion engine coming high pressure exhaust duct (3, 31) and one Low-pressure exhaust duct (4, 35), the low-pressure exhaust duct (4, 35) and the high-pressure exhaust duct (3, 31) in a gas housing (5, 34) and the low pressure fresh air supply duct (14, 38) and the high pressure charge air duct (10, 32) in an air housing (15, 39) are arranged, characterized in that they are a Connection line (46) between the high pressure charge air duct (32) and the high-pressure exhaust duct (31). Gasdynamische Druckwellenmaschine nach Anspruch 1, dadurch gekennzeichnet, dass die Verbindungsleitung (46) ein Rückschlagventil (47) aufweist, um zu verhindern, dass Abgas in die Ladeluft gelangt, und um die schädlichen Druckstösse auszufiltern.Gas dynamic pressure wave machine according to claim 1, characterized in that the connecting line (46) Check valve (47) to prevent exhaust gets into the charge air and around the harmful pressure surges to filter out. Gasdynamische Druckwellenmaschine nach Anspruch 2, dadurch gekennzeichnet, dass das Rückschlagventil (47) über eine elektronische Schaltung gesteuert ist.Gas dynamic pressure wave machine according to claim 2, characterized in that the check valve (47) over an electronic circuit is controlled. Gasdynamische Druckwellenmaschine nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass der Querschnitt der Verbindungsleitung (46) durch eine Regeleinrichtung veränderbar ist.Gas dynamic pressure wave machine according to one of the Claims 1 to 3, characterized in that the Cross section of the connecting line (46) through a Control device is changeable. Gasdynamische Druckwellenmaschine nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass die Verbindungsleitung (46) nahe der Oeffnungskante des Hochdruck-Ladeluftkanals (32) abzweigt.Gas dynamic pressure wave machine according to one of the Claims 1 to 4, characterized in that the Connection line (46) near the opening edge of the High-pressure charge air duct (32) branches.
EP97810614A 1997-08-29 1997-08-29 Aerodyamic pressure wave machine Expired - Lifetime EP0899434B1 (en)

Priority Applications (9)

Application Number Priority Date Filing Date Title
ES97810614T ES2225946T3 (en) 1997-08-29 1997-08-29 GASODYNAMIC PRESSURE WAVE MACHINE.
DE59711832T DE59711832D1 (en) 1997-08-29 1997-08-29 Gas dynamic pressure wave machine
AT97810614T ATE272788T1 (en) 1997-08-29 1997-08-29 GAS-DYNAMIC PRESSURE WAVE MACHINE
EP97810614A EP0899434B1 (en) 1997-08-29 1997-08-29 Aerodyamic pressure wave machine
AU95334/98A AU728535B2 (en) 1997-08-29 1998-08-25 Gas-dynamic pressure wave machine
KR1020007002046A KR20010023404A (en) 1997-08-29 1998-08-25 Gas-dynamic pressure wave machine
JP2000508894A JP4190726B2 (en) 1997-08-29 1998-08-25 Aerodynamic pressure wave machine
US09/486,452 US6314951B1 (en) 1997-08-29 1998-08-25 Gas-dynamic pressure-wave machine
PCT/EP1998/005379 WO1999011915A1 (en) 1997-08-29 1998-08-25 Gas-dynamic pressure-wave machine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP97810614A EP0899434B1 (en) 1997-08-29 1997-08-29 Aerodyamic pressure wave machine

Publications (2)

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EP0899434A1 true EP0899434A1 (en) 1999-03-03
EP0899434B1 EP0899434B1 (en) 2004-08-04

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US (1) US6314951B1 (en)
EP (1) EP0899434B1 (en)
JP (1) JP4190726B2 (en)
KR (1) KR20010023404A (en)
AT (1) ATE272788T1 (en)
AU (1) AU728535B2 (en)
DE (1) DE59711832D1 (en)
ES (1) ES2225946T3 (en)
WO (1) WO1999011915A1 (en)

Cited By (1)

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WO2011100958A1 (en) * 2010-02-17 2011-08-25 Benteler Automobiltechnik Gmbh Method for adjusting a charge pressure in an internal combustion engine having a pressure-wave supercharger

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DE10210358B4 (en) * 2002-03-08 2013-08-22 General Motors Llc ( N. D. Ges. D. Staates Delaware ) A fuel cell system with compressor and method for operating such a fuel cell system
EP1375859B1 (en) 2002-06-28 2007-07-18 Swissauto Engineering S.A. Method for controlling an internal combustion engine with a gas-dynamic pressure-wave machine
ES2250605T3 (en) 2002-06-28 2006-04-16 Swissauto Engineering S.A. METHOD FOR CONTROLLING AN INTERNAL COMBUSITON ENGINE WITH A GASODYNAMIC PRESSURE WAVE COMPRESSOR.
US7497666B2 (en) * 2004-09-21 2009-03-03 George Washington University Pressure exchange ejector
FR2879250A1 (en) * 2004-12-09 2006-06-16 Renault Sas AIR SUPPLY DEVICE FOR INTERNAL COMBUSTION ENGINE WITH EXHAUST GAS RECYCLING, AND ASSOCIATED METHOD.
FR2879249A1 (en) * 2004-12-09 2006-06-16 Renault Sas RECYCLED EXHAUST GAS SUPPLY AND STRATIFICATION DEVICE FOR INTERNAL COMBUSTION ENGINE, IN PARTICULAR FOR MOTOR VEHICLE, AND ASSOCIATED METHOD.
US20130037008A1 (en) * 2010-04-20 2013-02-14 Toyota Jidosha Kabushiki Kaisha Pressure wave supercharger

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JPS6128717A (en) * 1984-07-19 1986-02-08 Mazda Motor Corp Engine with supercharger
CH681738A5 (en) 1989-11-16 1993-05-14 Comprex Ag
US5284123A (en) * 1993-01-22 1994-02-08 Pulso Catalytic Superchargers Pressure wave supercharger having a stationary cellular member
WO1997020134A1 (en) * 1995-11-30 1997-06-05 Otto Blank Supercharging arrangement for the charge air of an internal combustion engine

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US4702218A (en) * 1984-07-24 1987-10-27 Mazda Motor Corporation Engine intake system having a pressure wave supercharger
ATE70894T1 (en) * 1986-10-29 1992-01-15 Comprex Ag PRESSURE WAVE CHARGER.
US4910959A (en) * 1988-10-11 1990-03-27 Pulso Catalytic Superchargers Corporation Pulsed catalytic supercharger silencer

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JPS6128717A (en) * 1984-07-19 1986-02-08 Mazda Motor Corp Engine with supercharger
CH681738A5 (en) 1989-11-16 1993-05-14 Comprex Ag
US5284123A (en) * 1993-01-22 1994-02-08 Pulso Catalytic Superchargers Pressure wave supercharger having a stationary cellular member
WO1997020134A1 (en) * 1995-11-30 1997-06-05 Otto Blank Supercharging arrangement for the charge air of an internal combustion engine

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011100958A1 (en) * 2010-02-17 2011-08-25 Benteler Automobiltechnik Gmbh Method for adjusting a charge pressure in an internal combustion engine having a pressure-wave supercharger
EP2562381A1 (en) * 2010-02-17 2013-02-27 Benteler Automobiltechnik GmbH Method for controlling the boost pressure in an internal combustion engine with a pressure wave supercharger

Also Published As

Publication number Publication date
EP0899434B1 (en) 2004-08-04
DE59711832D1 (en) 2004-09-09
AU9533498A (en) 1999-03-22
ES2225946T3 (en) 2005-03-16
US6314951B1 (en) 2001-11-13
JP4190726B2 (en) 2008-12-03
JP2001515172A (en) 2001-09-18
AU728535B2 (en) 2001-01-11
KR20010023404A (en) 2001-03-26
WO1999011915A1 (en) 1999-03-11
ATE272788T1 (en) 2004-08-15

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