EP0130433B1 - Turbo charger with an exhaust gas outlet valve - Google Patents

Turbo charger with an exhaust gas outlet valve Download PDF

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Publication number
EP0130433B1
EP0130433B1 EP84106843A EP84106843A EP0130433B1 EP 0130433 B1 EP0130433 B1 EP 0130433B1 EP 84106843 A EP84106843 A EP 84106843A EP 84106843 A EP84106843 A EP 84106843A EP 0130433 B1 EP0130433 B1 EP 0130433B1
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EP
European Patent Office
Prior art keywords
flap
exhaust gas
pressure wave
gas outlet
lever
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
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EP84106843A
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German (de)
French (fr)
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EP0130433A1 (en
Inventor
Andreas Mayer
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BBC Brown Boveri AG Switzerland
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BBC Brown Boveri AG Switzerland
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Priority to AT84106843T priority Critical patent/ATE23912T1/en
Publication of EP0130433A1 publication Critical patent/EP0130433A1/en
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    • 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
    • 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

Definitions

  • the present invention relates to a pressure wave charger with an exhaust gas relief valve according to the preamble of patent claim 1.
  • a pressure wave supercharger for such engines is designed in such a way that it generates a boost pressure under load at the maximum engine speed that is higher than the boost pressure required to generate the permissible peak pressure without exhaust gas being blown off.
  • a high permissible boost pressure and thus a favorable torque curve and fuel consumption can then be achieved over a wide operating range.
  • Such a motor is elastic and a vehicle equipped with it can be driven lazily.
  • Blowing off exhaust gas does not need to be used in commercial vehicle engines, since these allow higher boost pressures and operate in a narrower speed range than passenger car engines. For commercial vehicle engines, it is therefore sufficient to design the pressure wave charger so that it delivers the maximum boost pressure in the desired operating range at which the peak value of the combustion pressure is still permissible.
  • a regulating device for regulating the boost pressure by deliberately blowing off the engine exhaust gas upstream of the pressure wave charger is the subject of an earlier patent application, see EP-A-0 123 990.
  • the valve member used in the device described therein, with which the blow-off channel, referred to in specialist circles as wastegate, more or less is released or closed, is a spring-loaded poppet valve.
  • the valve member is likewise spring-loaded and mushroom-shaped in the area of the sealing elements.
  • the location and the design of the opening of the blow-off channel in the exhaust outlet connection are selected so that the blow-off flow exerts an ejector effect in the latter and thereby supports the purging of the relaxed exhaust gases from the cells of the rotor.
  • an exhaust gas blow-off valve which redirects the transfer of excess high-pressure exhaust gas before it enters the exhaust gas outlet connection and thus prevents impermissibly high charging pressures.
  • a flap in the overflow channel is controlled by a membrane which is acted upon by high pressure exhaust gas on the one hand and a constant pressure on the other hand.
  • the constant pressure is selected so that the blow-off occurs when driving uphill, i.e. in higher altitudes, where the air pressure is lower than in valleys, than would be the case if the atmospheric air pressure prevailing at the respective height on one side of the membrane would work.
  • the boost pressure limitation is therefore independent of the respective atmospheric pressure and a higher boost pressure is available even when driving uphill.
  • the springs of the valves used there are subject to high levels of heat due to the exhaust gases passing them and thereby change their spring rate over time, so that the valve opens earlier.
  • the blow-off pressure in the charger and thus also the combustion pressures decrease. There is therefore a loss of power in the operating range of the engine mentioned at the beginning.
  • a flap valve has been used which does not require a spring in the blow-off area and the exhaust pressure or, as described in the mentioned EP-A-0 123 990 , operated by another suitable process pressure.
  • the adjusting force acts on a lever which is connected to the valve shaft in a torsionally rigid manner.
  • Such a flap valve is much cheaper to produce than the two known valve types mentioned above.
  • the relaxed exhaust gases after they have done their compression work, together with the mixture of air and exhaust gas that has formed in the mixing zone, ie in the area of the interface between air and exhaust gas, must be completely in be flushed out the exhaust outlet.
  • This purging is supported by the intake air, which enters the rotor cells on the side opposite the exhaust openings, thereby cooling the rotor at the same time.
  • the rotor in order to achieve satisfactory compression efficiency, the rotor must be cooled even further.
  • the pressure wave charger has to draw in more air than it delivers compressed charge air to the engine. These additionally drawn in air is called purge air and the ratio of purge air flow to charge air flow is the "purge level" of the pressure wave charger. This degree of flushing decreases with increasing engine speed and decreasing engine load.
  • Blow-off by wastegate affects a pressure wave charger, primarily, like a turbocharger, the overall efficiency and thus the specific fuel consumption, but not the flushing level. Because the rinsing energy is reduced in proportion to the compression energy.
  • the transverse component of the flow into the exhaust duct does not represent a serious impairment of the exhaust flow and thus the degree of purge.
  • the purge is significantly impaired by the larger cross-component of the inlet speed, and thus the compression efficiency is also impaired.
  • the object of the present invention defined in claim 1 is to avoid these disadvantages of the flap valve which is superior to the known valve types in terms of cheap manufacture and simple construction
  • Fig. 1 denotes a rotor housing, 2 an air housing and 3 a gas housing of a pressure wave charger.
  • the air housing 2 as can be seen in FIG. 2, has a horizontal air inlet nozzle 6 through which air is sucked in from atmospheric pressure, and a vertical charge air outlet nozzle 7, see FIG.
  • FIG. 3 and 4 show the gas housing 3 with the exhaust gas relief valve 8 in a longitudinal section or in a side elevation.
  • the blow-off valve 8 has a flap 9 as the closing element.
  • This is provided with a rivet pin 10 which sits with axial and radial play in a bore in a plate-shaped flap lever 11 and is held therein by means of a washer 12 and a rivet head 13.
  • the flap lever 11 is rigidly connected to the lower end of a flap shaft 14, e.g. by welding.
  • This flap shaft is guided in a bearing bush 15 and extends obliquely upwards through the gas housing 3 to the outside, where it is connected in a torsionally rigid manner to a lever 16.
  • This carries at its free end a bolt 17 for connecting a linkage, not shown, which connects the flap 9 to a control device mentioned at the beginning.
  • a restriction screen 19 is provided at a distance around the flap 9.
  • the current threads which, when using a cheap flap instead of a more expensive, but axially symmetrically flowed plate or mushroom valve, impair the undisturbed outflow in the exhaust duct and thus the flushing of the rotor cells mentioned at the outset, immediately after passing through the annular gap released by the flap in a direction parallel to the axis of the exhaust outlet connection 5 is forced, as is indicated by the dash-dotted streamlines in FIG. 3.
  • the dash-dotted representation of the streamlines was chosen because the flap 9 is shown in the closed state. So it is the streamlines that would occur with the flap open.
  • This restriction screen 19 does not surround the entire circumference of the flap 9, but part of the same as a semicircular ring coaxial with the flap 9, only half of its circumference.
  • the two ends of this semicircular ring then run out into a tip, the inner boundaries of which, viewed radially inward, run parallel to the longitudinal edges of the flap lever 11.
  • the area of the restriction screen that is left blank for the flap lever 11 does not degrade its directionality, since the narrowest point of the flap gap and the flow are located there is also forced in the axially parallel direction by the adjacent wall part of the exhaust gas outlet connection 5.
  • the axis of the restriction screen 20 is eccentric to the axis of the associated flap 21 by the distance x. This gives a larger outflow cross section after the flap gap.
  • the exhaust gas inlet connection 4 is not arranged on the upper side, as in the pressure wave charger according to FIGS. 1 and 2, but on the lower side.
  • restriction screen is also possible to design the restriction screen as a full circular ring, which thus coaxially or eccentrically surrounds the entire circumference of the flap.
  • the flap lever must then be cranked accordingly.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)
  • Fluid-Driven Valves (AREA)
  • Exhaust Gas After Treatment (AREA)

Abstract

An exhaust gas blow-down valve of a pressure wave supercharger comprising a flap which is connected by a flap lever, a flap shaft and a second lever to a control device responsive to a process pressure of the pressure wave supercharger. In order to avoid deterioration of the scavenging coefficient of the pressure wave supercharger, a restraining screen is provided around part of the periphery of the flap at a distance from it, which restraining screen deflects the exhaust gas flowing out of the flap gap into the desired direction parallel to the axis of the exhaust gas outlet stub pipe.

Description

Die vorliegende Erfindung betrifft einen Druckwellenlader mit einem Abgasabblaseventil nach dem Oberbegriff des Patentanspruchs 1.The present invention relates to a pressure wave charger with an exhaust gas relief valve according to the preamble of patent claim 1.

Bei Motoren mit Druckwellenlader für Personenautos sollen in einem weiten Drehzahlbereich die Spitzendrücke in den Zylindern in der Nähe der zulässigen maximalen Verbrennungsdrücke liegen. Um dies zu erreichen, wird ein Druckwellenlader für solche Motoren so ausgelegt, dass er unter Last bei der maximalen Motordrehzahl einen Ladedruck erzeugt, der ohne Abblasen von Abgas höher ist als der Ladedruck, der zur Erzeugung des zulässigen Spitzendrucks erforderlich ist. Durch Abblasen von Abgas, gesteuert z.B. vom Ladedruck, kann dann über einen weiten Betriebsbereich ein hoher zulässiger Ladedruck und damit günstiger Drehmomentverlauf und Kraftstoffverbrauch erreicht werden. Ein solcher Motor ist elastisch und ein damit ausgerüstetes Fahrzeug kann schaltfaul gefahren werden.In engines with pressure wave superchargers for passenger cars, the peak pressures in the cylinders should be close to the permissible maximum combustion pressures over a wide speed range. In order to achieve this, a pressure wave supercharger for such engines is designed in such a way that it generates a boost pressure under load at the maximum engine speed that is higher than the boost pressure required to generate the permissible peak pressure without exhaust gas being blown off. By blowing off exhaust gas, controlled e.g. from the boost pressure, a high permissible boost pressure and thus a favorable torque curve and fuel consumption can then be achieved over a wide operating range. Such a motor is elastic and a vehicle equipped with it can be driven lazily.

Ein Abblasen von Abgas braucht bei Nutzfahrzeugmotoren nicht angewendt zu werden, da diese höhere Ladedrücke zulassen und in einem engeren Drehzahlbereich arbeiten als Personenwagenmotoren. Bei Nutzfahrzeugmotoren genügt es daher, den Druckwellenlader so auszulegen, dass er im gewünschten Betriebsbereich den maximalen Ladedruck liefert, bei dem der Spitzenwert des Verbrennungsdruckes noch zulässig ist.Blowing off exhaust gas does not need to be used in commercial vehicle engines, since these allow higher boost pressures and operate in a narrower speed range than passenger car engines. For commercial vehicle engines, it is therefore sufficient to design the pressure wave charger so that it delivers the maximum boost pressure in the desired operating range at which the peak value of the combustion pressure is still permissible.

Eine Regeleinrichtung zur Regelung des Ladedruckes durch gezieltes Abblasen des Motorabgases vor dem Druckwellenlader ist Gegenstand einer früherer Patentanmeldung, siehe EP-A- 0 123 990. Das bei der dort beschriebenen Einrichtung benutzte Ventilorgan, mit dem der in Fachkreisen als Wastegate bezeichnete Abblasekanal mehr oder weniger freigegeben oder verschlossen wird, ist ein federbelastetes Tellerventil. Bei einer weiteren, in der CH-A 398 185 beschriebenen Einrichtung zur Regelung des Ladedruckes durch Abblasen von Abgas, wobei zur Betätigung des Ventilorgans der Abgasdruck benützt wird, ist das Ventilorgan ebenfalls federbelastet und im Bereich der Dichtelemente pilzförmig gestaltet.A regulating device for regulating the boost pressure by deliberately blowing off the engine exhaust gas upstream of the pressure wave charger is the subject of an earlier patent application, see EP-A-0 123 990. The valve member used in the device described therein, with which the blow-off channel, referred to in specialist circles as wastegate, more or less is released or closed, is a spring-loaded poppet valve. In a further device described in CH-A 398 185 for regulating the boost pressure by blowing off exhaust gas, the exhaust gas pressure being used to actuate the valve member, the valve member is likewise spring-loaded and mushroom-shaped in the area of the sealing elements.

Der Ort und die Gestaltung der Einmündung des Abblasekanals in den Abgasaustrittsstutzen sind dabei so gewählt, dass der Abblasestrom in letzterem eine Ejektorwirkung ausübt und dadurch die Spülung der entspannten Abgase aus den Zellen des Rotors unterstützt.The location and the design of the opening of the blow-off channel in the exhaust outlet connection are selected so that the blow-off flow exerts an ejector effect in the latter and thereby supports the purging of the relaxed exhaust gases from the cells of the rotor.

Aus der EP-A-80 741 ist weiters ein Abgasabblaseventil bekannt, das den Uebertritt von überschüssigem Hochdruckabgas vor dessen Eintritt in den Abgasaustrittsstutzen umleitet und so unzulässig hohe Ladedrücke verhindert. Dabei wird eine Klappe im Ueberströmkanal durch eine einerseits vom Hochdruckabgas und andererseits von einem konstanten Druck beaufschlagte Membran gesteuert. Der konstante Druck ist so gewählt, dass das Abblasen bei Bergfahrten, also in höheren Lagen, wo der Luftdruck geringer ist als in Tälern, später auftritt als dies der Fall wäre, wenn auf die eine Seite der Membran der in der jeweiligen Höhe herrschende atmosphärische Luftdruck wirken würde. Die Ladedruckbegrenzung wird dadurch vom jeweiligen Atmosphärendruck unabhängig und es steht damit auch bei Bergfahrten ein höherer Ladedruck zur Verfügung.From EP-A-80 741 an exhaust gas blow-off valve is also known which redirects the transfer of excess high-pressure exhaust gas before it enters the exhaust gas outlet connection and thus prevents impermissibly high charging pressures. A flap in the overflow channel is controlled by a membrane which is acted upon by high pressure exhaust gas on the one hand and a constant pressure on the other hand. The constant pressure is selected so that the blow-off occurs when driving uphill, i.e. in higher altitudes, where the air pressure is lower than in valleys, than would be the case if the atmospheric air pressure prevailing at the respective height on one side of the membrane would work. The boost pressure limitation is therefore independent of the respective atmospheric pressure and a higher boost pressure is available even when driving uphill.

Bei dieser und den obenerwähnten Bauarten sind die Federn der dort verwendeten Ventile, insbesondere der Teller- und Pilzventile durch die an ihnen vorbeistreichenden Abgase stark wärmebelastet und verändern dadurch im Laufe der Zeit ihre Federkonstante, so dass sich das Ventil früher öffnet. Der Abblasedruck im Lader und damit auch die Verbrennungsdrücke verringern sich. Es kommt also zu einem Leistungsverlust im eingangs erwähnten Betriebsbereich des Motors.In this and the above-mentioned types, the springs of the valves used there, in particular the plate and mushroom valves, are subject to high levels of heat due to the exhaust gases passing them and thereby change their spring rate over time, so that the valve opens earlier. The blow-off pressure in the charger and thus also the combustion pressures decrease. There is therefore a loss of power in the operating range of the engine mentioned at the beginning.

Um diese Nachteile der vorerwähnten Abblaseeinrichtungen zu vermeiden, ist man dazu übergegangen, anstelle der erwähnten federbelasteten Teller- und Pilzventile ein Klappenventil zu verwenden, das im Abblasebereich keine Feder benötigt und vom Abgasdruck oder, wie in der erwähnten EP-A- 0 123 990 beschrieben, von einem anderen geeigneten Prozessdruck betätigt wird. Die Verstellkraft greift dabei an einem mit der Klappenwelle drehsteif verbundenen Hebel an. Ein solches Klappenventil ist wesentlich billiger zu produzieren als die beiden oben erwähnten, bekannten Ventilbauarten. Dazu kommt, dass bei einem solchen Klappenventil infolge Fortfalls der Feder keine Aenderung der Oeffnungscharakteristik auftritt. Im Gegensatz zu den genannten Teller- und Pilzventilen, bei denen die Abströmung der überschüssigen Abgase symmetrisch zur Ventil längsachse und im wesentlichen parallel zum Strom der Niederdruckabgase, d.h., der Auspuffgase im Abgasaustrittsstutzen verläuft, strömen aber die abblasenden Abgase bei einem Klappenventil mit einer Geschwindigkeitskomponente quer zur Strömungsrichtung der Auspuffgase in den Abgasaustrittsstutzen ein, woraus sich die im folgenden beschriebenen Nachteile ergeben.In order to avoid these disadvantages of the above-mentioned blow-off devices, instead of the spring-loaded plate and mushroom valves mentioned, a flap valve has been used which does not require a spring in the blow-off area and the exhaust pressure or, as described in the mentioned EP-A-0 123 990 , operated by another suitable process pressure. The adjusting force acts on a lever which is connected to the valve shaft in a torsionally rigid manner. Such a flap valve is much cheaper to produce than the two known valve types mentioned above. In addition, there is no change in the opening characteristics of such a flap valve due to the spring no longer operating. In contrast to the plate and mushroom valves mentioned, in which the outflow of the excess exhaust gases runs symmetrically to the longitudinal axis of the valve and essentially parallel to the flow of the low-pressure exhaust gases, i.e. the exhaust gases in the exhaust outlet connection, the exhaust gases flow transversely in a flap valve with a speed component to the direction of flow of the exhaust gases in the exhaust outlet, resulting in the disadvantages described below.

Für eine einwandfreie, effektive Funktion des Druckwellenladers müssen die entspannten Abgase, nachdem sie ihre Verdichtungsarbeit geleistet haben, mitsamt dem Gemisch aus Luft und Abgas, das sich in der Mischzone, d.h., im Bereich der Trennfläche von Luft und Abgas, gebildet hat, vollständig in den Abgasaustrittsstutzen ausgespült werden. Diese Spülung wird durch die Ansaugluft, die auf der den Auspufföffnungen gegenüberliegenden Seite in die Rotorzellen eintritt, unterstützt und dadurch gleichzeitig der Rotor gekühlt. Um befriedigende Verdichtungswirkungsgrade zu erzielen, ist aber eine noch weitergehende Kühlung des Rotors erforderlich. Dazu muss der Druckwellenlader mehr Luft ansaugen als er verdichtete Ladeluft an den Motor abgibt. Diese zusätzlich angesaugte Luft heisst Spülluft und das Verhältnis von Spülluftstrom zu Ladeluftstrom der "Spülgrad" des Druckwellenladers. Dieser Spülgrad sinkt mit steigender Motordrehzahl und abnehmender Motorbelastung.For perfect, effective functioning of the pressure wave charger, the relaxed exhaust gases, after they have done their compression work, together with the mixture of air and exhaust gas that has formed in the mixing zone, ie in the area of the interface between air and exhaust gas, must be completely in be flushed out the exhaust outlet. This purging is supported by the intake air, which enters the rotor cells on the side opposite the exhaust openings, thereby cooling the rotor at the same time. However, in order to achieve satisfactory compression efficiency, the rotor must be cooled even further. To do this, the pressure wave charger has to draw in more air than it delivers compressed charge air to the engine. These additionally drawn in air is called purge air and the ratio of purge air flow to charge air flow is the "purge level" of the pressure wave charger. This degree of flushing decreases with increasing engine speed and decreasing engine load.

Das Abblasen durch Wastegate beeinträchtigt bei einem Druckwellenlader, in erster Linie, wie bei einem Turbolader, den Gesamtwirkungsgrad und damit den spezifischen Kraftstoffverbrauch, nicht aber den Spülgrad. Denn die Spülenergie verringert sich angenähert proportional zur Verdichtungsenergie.Blow-off by wastegate affects a pressure wave charger, primarily, like a turbocharger, the overall efficiency and thus the specific fuel consumption, but not the flushing level. Because the rinsing energy is reduced in proportion to the compression energy.

Bei kleinen Abblaseströmen stellt die Querkomponente der Strömung in den Auspuffkanal hinein keine schwerwiegende Beeinträchtigung des Auspuffstromes und damit des Spülgrades dar. Bei grösseren Abblaseströmen aber wird durch die grössere Querkomponente der Eintrittsgeschwindigkeit die Spülung nennenswert verschlechtert und damit auch der Verdichtungswirkungsgrad beeinträchigt.In the case of small blow-off flows, the transverse component of the flow into the exhaust duct does not represent a serious impairment of the exhaust flow and thus the degree of purge. In the case of larger blow-off flows, however, the purge is significantly impaired by the larger cross-component of the inlet speed, and thus the compression efficiency is also impaired.

Die Aufgabe der vorliegenden, im Patentanspruch 1 definierten Erfindung besteht darin, diese Nachteile des an sich bezüglich billiger Herstellung und einfachen Aufbaus den bekannten Ventilbauarten überlegenen Klappenventils zu vermeidenThe object of the present invention defined in claim 1 is to avoid these disadvantages of the flap valve which is superior to the known valve types in terms of cheap manufacture and simple construction

Diese Aufgabe wird erfindungsgemäss mit den kennzeichnenden Merkmalen des Patentanspruch 1 gelöst.This object is achieved according to the invention with the characterizing features of patent claim 1.

Die Erfindung wird im folgenden anhand von in der Zeichnung dargestellten Ausführungsbeispielen näher beschrieben. Es stellen dar: Die

  • Fig. 1 und 2 einen Aufris 3eitenriss eines Druckwellenladers mit ein Abgasabblaseventil,
  • Fig. 3 einen Längsschnitt durch das Gasgehäuse eines Druckwellenladers nach den Fig. 1 und 2, mit einer ersten Ausführungsform eines Abgasabblaseventils,
  • Fig. 4 den zu Fig. 3 gehörigen Seitenriss, und
  • Fig. 5 einen Seitenriss eines Druckwellenladers mit einer zweiten Ausführungsform eines Abgasabblaseventils.
The invention is described below with reference to exemplary embodiments shown in the drawing. It shows: The
  • 1 and 2 a Aufris 3eitenriss of a pressure wave charger with an exhaust valve,
  • 3 shows a longitudinal section through the gas housing of a pressure wave charger according to FIGS. 1 and 2, with a first embodiment of an exhaust gas blow-off valve,
  • Fig. 4 shows the side elevation belonging to Fig. 3, and
  • Fig. 5 is a side elevation of a pressure wave supercharger with a second embodiment of an exhaust gas relief valve.

In Fig. 1 bezeichnet 1 ein Rotorgehäuse, 2 ein Luftgehäuse und 3 ein Gasgehäuse eines Druckwellenladers. Am Gasgehäuse 3 befindet sich an der Oberseite ein Abgaseintrittsstutzen 4, durch den das aus dem Motor kommende Abgas, symbolisiert durch den senkrechten schwarzen Pfeil, unter Druck eintritt. Nachdem es im Rotor die Verdichtungsarbeit geleistet hat, tritt es durch den Abgasaustrittsstutzen 5 parallel zur Rotorachse in eine nicht dargestellte Auspuffanlage aus, was durch den waagrechten schwarzen Pfeil angedeutet ist. Das Luftgehäuse 2 weist, wie aus Fig. 2 hervorgeht, einen waagrechten Lufteinlaßstutzen 6 auf, durch den Luft von Atmosphärendruck angesaugt wird, sowie einen senkrechten Ladeluftauslaßstutzen 7, siehe Fig. 1, durch den die in den Rotorzellen verdichtete Ladeluft austritt und von dort durch eine nicht dargestellte Ladeluftleitung einlasseitig dem Motor zugeführt wird. Ein- und Auslass der Luft sind durch die weissen Pfeile in den beiden Figuren dargestellt. Der Einlass kann nur in Fig. 2 dargestellt werden, da der lufteinlaßstutzen in Fig. 1 nicht sichtbar ist. Das im Gasgehäuse 3 befindliche Abgasabblaseventil 8 ist in stark vereinfachter Darstellung aus Fig. 2 zu ersehen.In Fig. 1, 1 denotes a rotor housing, 2 an air housing and 3 a gas housing of a pressure wave charger. On the top of the gas housing 3 there is an exhaust gas inlet connection 4, through which the exhaust gas coming from the engine, symbolized by the vertical black arrow, enters under pressure. After it has done the compression work in the rotor, it exits through the exhaust outlet connection 5 parallel to the rotor axis into an exhaust system, not shown, which is indicated by the horizontal black arrow. The air housing 2, as can be seen in FIG. 2, has a horizontal air inlet nozzle 6 through which air is sucked in from atmospheric pressure, and a vertical charge air outlet nozzle 7, see FIG. 1, through which the charge air compressed in the rotor cells emerges and from there through a charge air line, not shown, is fed to the engine on the inlet side. Air inlet and outlet are shown by the white arrows in the two figures. The inlet can only be shown in Fig. 2, since the air inlet port is not visible in Fig. 1. The exhaust gas blow-off valve 8 located in the gas housing 3 can be seen in a greatly simplified illustration from FIG. 2.

Die Fig. 3 und 4 zeigen das Gasgehäuse 3 mit dem Abgasabblaseventil 8 in einem Längsschnitt bzw. in einem Seitenriss. Das Abblaseventil 8 weist als Schliessorgan eine Klappe 9 auf. Diese ist mit einem Nietzapfen 10 versehen, der mit axialem und radialem Spiel in einer Bohrung eines plattenförmigen Klappenhebels 11 sitzt und darin mittels einer Scheibe 12 und eines Nietkopfes 13 gehalten ist. Der Klappenhebel 11 ist mit dem unteren Ende einer Klappenwelle 14 starr verbunden, z.B. durch Schweissung. Diese Klappenwelle ist in einer Lagerbüchse 15 geführt und erstreckt sich schräg nach oben durch das Gasgehäuse 3 nach aussen, wo sie mit einem Hebel 16 drehsteif verbunden ist. Dieser trägt an seinem freien Ende einen Bolzen 17 zum Anschluss eines nicht dargestellten Gestänges, das die Klappe 9 mit einer eingangs erwähnten Regeleinrichtung verbindet.3 and 4 show the gas housing 3 with the exhaust gas relief valve 8 in a longitudinal section or in a side elevation. The blow-off valve 8 has a flap 9 as the closing element. This is provided with a rivet pin 10 which sits with axial and radial play in a bore in a plate-shaped flap lever 11 and is held therein by means of a washer 12 and a rivet head 13. The flap lever 11 is rigidly connected to the lower end of a flap shaft 14, e.g. by welding. This flap shaft is guided in a bearing bush 15 and extends obliquely upwards through the gas housing 3 to the outside, where it is connected in a torsionally rigid manner to a lever 16. This carries at its free end a bolt 17 for connecting a linkage, not shown, which connects the flap 9 to a control device mentioned at the beginning.

Um nun die in der Einleitung erwähnte Querkomponente der Abblaseströmung, die durch den Abblasekanal 18 in die an den Abgasaustrittsstutzen 5 anschliessende Auspuffanlage eintritt, zu vermeiden oder mindestens entscheidend zu verkleinern, ist in einem Abstand um die Klappe 9 herum ein Striktionsschirm 19 vorgesehen. Durch ihn werden die Stromfäden, die bei Verwendung einer billigen Klappe anstelle eines teureren, aber axialsymmetrisch umströmten Teller- oder Pilzventils die ungestörte Abströmung im Auspuffkanal und damit die eingangs erwähnte Spülung der Rotorzellen beeinträchtigen, gleich nach dem Durchtritt durch den von der Klappe freigegebenen Ringspalt in eine zur Achse des Abgasaustrittsstutzens 5 parallele Richtung gezwungen, wie dies durch die strichpunktierten Stromlinien in Fig. 3 angedeutet ist. Die strichpunktierte Darstellung der Stromlinien wurde gewählt, weil die Klappe 9 im geschlossenen Zustand dargestellt ist. Es sind also die Stromlinien, wie sie bei offener Klappe auftreten würden.In order to avoid or at least decisively reduce the transverse component of the blow-off flow mentioned in the introduction, which enters through the blow-off channel 18 into the exhaust system adjoining the exhaust outlet connection 5, a restriction screen 19 is provided at a distance around the flap 9. Through it, the current threads, which, when using a cheap flap instead of a more expensive, but axially symmetrically flowed plate or mushroom valve, impair the undisturbed outflow in the exhaust duct and thus the flushing of the rotor cells mentioned at the outset, immediately after passing through the annular gap released by the flap in a direction parallel to the axis of the exhaust outlet connection 5 is forced, as is indicated by the dash-dotted streamlines in FIG. 3. The dash-dotted representation of the streamlines was chosen because the flap 9 is shown in the closed state. So it is the streamlines that would occur with the flap open.

Dieser Striktionsschirm 19 umgibt nicht den ganzen Umfang der Klappe 9, sondern ein Teil desselben als zur Klappe 9 koaxialer Halbkreisring nur deren halben Umfang. Die beiden Enden dieses Halbkreisringes laufen dort anschliessend in je eine Spitze aus, deren innere Begrenzungen, radial einwärts gesehen, parallel zu den Längskanten des Klappenhebels 11 verlaufen. Der auf diese Weise für den Klappenhebel 11 ausgesparte Bereich des Striktionsschirms verschlechtert seine Richtwirkung nicht, da sich dort die engste Stelle des Klappenspaltes befindet und die Strömung auch durch den benachbarten Wandteil des Abgasaustrittsstutzens 5 in die achsparallele Richtung gezwungen wird.This restriction screen 19 does not surround the entire circumference of the flap 9, but part of the same as a semicircular ring coaxial with the flap 9, only half of its circumference. The two ends of this semicircular ring then run out into a tip, the inner boundaries of which, viewed radially inward, run parallel to the longitudinal edges of the flap lever 11. The area of the restriction screen that is left blank for the flap lever 11 does not degrade its directionality, since the narrowest point of the flap gap and the flow are located there is also forced in the axially parallel direction by the adjacent wall part of the exhaust gas outlet connection 5.

Bei der Ausführung nach Fig. 5 liegt die Achse des Striktionsschirms 20 um die Strecke x exzentrisch zur Achse der zugehörigen Klappe 21. Man erhält dadurch einen grösseren Abströmungsquerschnitt nach dem Klappenspalt.In the embodiment according to FIG. 5, the axis of the restriction screen 20 is eccentric to the axis of the associated flap 21 by the distance x. This gives a larger outflow cross section after the flap gap.

Es bleibt noch nachzutragen, dass bei der Ausführung des Gasgehäuses nach den Fig. 3 bis 5 der Abgaseintrittsstutzen 4 nicht, wie bei dem Druckwellenlader gemäss den Fig. 1 und 2, auf der Oberseite, sondern auf der Unterseite angeordnet ist.It remains to be added that in the embodiment of the gas housing according to FIGS. 3 to 5, the exhaust gas inlet connection 4 is not arranged on the upper side, as in the pressure wave charger according to FIGS. 1 and 2, but on the lower side.

Es ist auch möglich, den Striktionsschirm als vollen Kreisring auszuführen, der also den ganzen Umfang der Klappe mit Abstand koaxial oder exzentrisch umschliesst. Der Klappenhebel muss dann entsprechend gekröpft ausgeführt sein.It is also possible to design the restriction screen as a full circular ring, which thus coaxially or eccentrically surrounds the entire circumference of the flap. The flap lever must then be cranked accordingly.

Claims (3)

1. Pressure wave supercharger with an exhaust gas blow-down valve, which pressure wave supercharger has a rotor casing (1) with a cell rotor in which the exhaust gas of an internal combustion engine compresses the combustion air required by the internal combustion engine, also having an air casing (2) through which atmospheric air is induced and, after compression in the cell rotor, is supplied as the supercharged air to the internal combustion engine, and having a gas casing (3) with an exhaust gas space via which the exhaust gas coming from the internal combustion engine reaches the cell rotor and, after its expansion in the cell rotor, is led via an exhaust gas outlet connection (5) into an exhaust receiver, the exhaust gas blow-down valve being located in a wall of the gas casing (3) separating the exhaust gas space mentioned from the exhaust gas outlet connection (5) and being designed as a flap valve, this flap (9) being actively connected via a flap lever (11), a flap shaft (14) and a lever (16) to a control device subjected to a process pressure of the pressure wave supercharger, characterised in that the shaft of the flap (9; 21) is located parallel to the axis of the exhaust gas outlet connection and that a restriction screen (19; 20) is provided in the exhaust gas outlet connnection (5), which screen surrounds at least part of the periphery of the flap (9; 21) at a distance from its periphery and whose wall extends into the exhaust gas outlet connection (5) substantially parallel to the axis of the latter.
2. Pressure wave supercharger according to Claim 1, characterised in that the flap (9) is designed as a circular disc with a rivet journal (10) which serves to provide the connection to the flap lever (11), and that the wall of the restriction screen (19) is coaxial with the flap (9).
3. Pressure wave supercharger according to Claim 1, characterised in that the flap (21) is designed as a circular disc with a rivet journal which acts to provide the connection to the flap lever, and that the wall of the restriction screen (20) is eccentrically located at a distance (x) from the axis of the flap (21) in such a way that the centre of the wall of the restriction screen (20) is further removed than the two ends of the wall of the restriction screen (20) from the periphery of the flap (21).
EP84106843A 1983-06-29 1984-06-15 Turbo charger with an exhaust gas outlet valve Expired EP0130433B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84106843T ATE23912T1 (en) 1983-06-29 1984-06-15 PRESSURE WAVE CHARGER WITH AN EXHAUST BLOW-OFF VALVE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH356183 1983-06-29
CH3561/83 1983-06-29

Publications (2)

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EP0130433A1 EP0130433A1 (en) 1985-01-09
EP0130433B1 true EP0130433B1 (en) 1986-11-26

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EP84106843A Expired EP0130433B1 (en) 1983-06-29 1984-06-15 Turbo charger with an exhaust gas outlet valve

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US (1) US4592330A (en)
EP (1) EP0130433B1 (en)
JP (1) JPS6013921A (en)
AT (1) ATE23912T1 (en)
DE (1) DE3461499D1 (en)

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Publication number Priority date Publication date Assignee Title
JPH0240269Y2 (en) * 1985-02-19 1990-10-26
JPS62174536A (en) * 1986-01-27 1987-07-31 Mazda Motor Corp Engine equipped with pressure wave supercharger
DE3922491A1 (en) * 1988-08-23 1990-03-01 Asea Brown Boveri GAS DYNAMIC PRESSURE WAVE CHARGER WITH EXHAUST BYPASS
US6055965A (en) * 1997-07-08 2000-05-02 Caterpillar Inc. Control system for exhaust gas recirculation system in an internal combustion engine
EP1007829B1 (en) * 1997-08-29 2004-04-07 Swissauto Engineering S.A. Gas-dynamic pressure wave machine
JP5939052B2 (en) * 2012-06-26 2016-06-22 株式会社Ihi Turbocharger
CN105143529B (en) 2013-03-12 2017-12-01 日本韦琳株式会社 Inorganic nano-fiber and preparation method thereof
US10344666B2 (en) 2014-09-01 2019-07-09 Garrett Transportation I Inc. Turbine wastegate

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EP0080741A1 (en) * 1981-11-30 1983-06-08 BBC Aktiengesellschaft Brown, Boveri & Cie. Aerodynamic pressure wave machine with exhaust by-pass

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US2800120A (en) * 1953-11-30 1957-07-23 Jendrassik Developments Ltd Pressure exchangers
GB775271A (en) * 1953-12-11 1957-05-22 Jendrassik Dev Ltd Improvements relating to pressure exchangers
US2836346A (en) * 1955-06-17 1958-05-27 Jendrassik Developments Ltd Pressure exchangers
CH349448A (en) * 1955-06-17 1960-10-15 Jendrassik Developments Limite Pressure exchanger
CH351141A (en) * 1956-03-29 1960-12-31 Brian Spalding Dudley Pressure exchanger
GB923368A (en) * 1961-01-30 1963-04-10 Power Jets Res & Dev Ltd Improvements in or relating to pressure exchangers
US4120156A (en) * 1977-06-08 1978-10-17 The Garrett Corporation Turbocharger control
JPS608936Y2 (en) * 1981-08-11 1985-03-30 三共理化学株式会社 Polymerized polished vane wheels
EP0123990B1 (en) * 1983-05-02 1986-12-30 BBC Brown Boveri AG Control device for a pressure-wave charger

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Publication number Priority date Publication date Assignee Title
EP0080741A1 (en) * 1981-11-30 1983-06-08 BBC Aktiengesellschaft Brown, Boveri & Cie. Aerodynamic pressure wave machine with exhaust by-pass

Also Published As

Publication number Publication date
JPS6013921A (en) 1985-01-24
DE3461499D1 (en) 1987-01-15
US4592330A (en) 1986-06-03
ATE23912T1 (en) 1986-12-15
JPH059618B2 (en) 1993-02-05
EP0130433A1 (en) 1985-01-09

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