DE2544471B2 - Internal combustion engine that forms a working space with two or more exhaust gas turbochargers connected in series - Google Patents
Internal combustion engine that forms a working space with two or more exhaust gas turbochargers connected in seriesInfo
- Publication number
- DE2544471B2 DE2544471B2 DE2544471A DE2544471A DE2544471B2 DE 2544471 B2 DE2544471 B2 DE 2544471B2 DE 2544471 A DE2544471 A DE 2544471A DE 2544471 A DE2544471 A DE 2544471A DE 2544471 B2 DE2544471 B2 DE 2544471B2
- Authority
- DE
- Germany
- Prior art keywords
- internal combustion
- combustion engine
- exhaust gas
- pressure
- low
- 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
Links
- 238000002485 combustion reaction Methods 0.000 title claims description 39
- 239000007789 gas Substances 0.000 description 35
- 238000010521 absorption reaction Methods 0.000 description 3
- 230000001133 acceleration Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 239000000567 combustion gas Substances 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000001627 detrimental effect Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
Classifications
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- 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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
-
- 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
- F02B33/44—Passages conducting the charge from the pump to the engine inlet, e.g. reservoirs
- F02B33/443—Heating of charging air, e.g. for facilitating the starting
-
- 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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
-
- 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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/001—Engines characterised by provision of pumps driven at least for part of the time by exhaust using exhaust drives arranged in parallel
-
- 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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/004—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust drives arranged in series
-
- 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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/007—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust-driven pumps arranged in parallel, e.g. at least one pump supplying alternatively
-
- 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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/013—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust-driven pumps arranged in series
-
- 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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
-
- 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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/16—Control of the pumps by bypassing charging air
- F02B37/164—Control of the pumps by bypassing charging air the bypassed air being used in an auxiliary apparatus, e.g. in an air turbine
- F02B37/166—Control of the pumps by bypassing charging air the bypassed air being used in an auxiliary apparatus, e.g. in an air turbine the auxiliary apparatus being a combustion chamber, e.g. upstream of turbine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/02—EGR systems specially adapted for supercharged engines
- F02M26/08—EGR systems specially adapted for supercharged engines for engines having two or more intake charge compressors or exhaust gas turbines, e.g. a turbocharger combined with an additional compressor
-
- 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
- F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
- F02B29/04—Cooling of air intake supply
- F02B29/0406—Layout of the intake air cooling or coolant circuit
- F02B29/0412—Multiple heat exchangers arranged in parallel or in series
-
- 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
- F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
- F02B29/04—Cooling of air intake supply
- F02B29/0406—Layout of the intake air cooling or coolant circuit
- F02B29/0418—Layout of the intake air cooling or coolant circuit the intake air cooler having a bypass or multiple flow paths within the heat exchanger to vary the effective heat transfer surface
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
Description
Die Erfindung betrifft eine arbeitsraumbildende Brennkraftmaschine mit zwei oder mehreren in Reihe geschalteten Abgasturboladern, bei denen die Hochdruckturbine den Hochdrucklader und die Niederdruckturbine den Niederdrucklader antreibt und eine Abgasturbine von einer vorbestimmten Drehzahl der Brennkraftmaschine an durch eine regelbare Bypaßleitung teilweise derart umgehbar ist, daß der zugehörige Lader keine Störung für die Luftzuführung verursacht.The invention relates to an internal combustion engine that forms a working space and has two or more in series switched exhaust gas turbochargers, in which the high pressure turbine drives the high pressure charger and the low pressure turbine drives the low pressure charger and a Exhaust gas turbine is partially bypassed from a predetermined speed of the internal combustion engine through a controllable bypass line in such a way that the associated Charger does not cause any disturbance to the air supply.
Bei bekannten Brennkraftmaschinen der eingangs beschriebenen Art (DE-AS 13 01 608) durchströmt das Abgas ungeregelt die zur Hochdruckstufe gehörende Abgasturbine und wird erst danach entsprechend den Betriebsverhältnissen vor der Abgasturbine der Niederdruckstufe geregelt, indem im Vollastbereich der Brennkraftmaschine ein Teil des Abgases unter Umgehung der Niederdruckturbine ins Freie geleitet wird. In diesem Betriebsbereich trägt die Niederdruckstufe, die für eine niedrige Drehzahl der Brennkraftmaschine ausgelegt werden muß, praktisch nicht zur Druckerhöhung der Ladeluft bei Aufgrund des geringen Schluckvolumens der Brennkraftmaschine im optimalen Auslegungspunkt klein, so daß der Lader der Niederdruckstufe sehr klein gebaut werden muß. Bei hoher Drehzahl der Brennkraftmaschine steigt das Schluckvolumen entsprechend an, so daß der Lader der Hochdruckstufe, der in diesem Betriebsbereich seinen optimalen Auslegungspunkt aufweist und im wesentlichen die Druckerhöhung bewirkt, ein großes Volumen verarbeiten muß und dementsprechend groß ausgelegt wird. Das große Volumen wird aber über den kleinen Abgasturbolader der Niederdruckstufe angesaugt, der in diesem Betriebsbereich für das durchgesetzte Volumen einen sehr schlechten Wirkungsgrad aufweist. Ferner muß die Abgasturbine der Niederdruckstufe für den Teillastbereich der Brennkraftmaschine ausgelegt werden. In diesem Betriebsbereich ist die Abgasenergie relativ gering. Die Verluste, die in der vorgeschalteten Hochdruckgasturbine und den Zuleitungen auftreten,In known internal combustion engines of the type described above (DE-AS 13 01 608) flows through the Exhaust gas unregulated the exhaust gas turbine belonging to the high pressure stage and is only then according to the Operating conditions upstream of the exhaust gas turbine of the low-pressure stage are regulated by the Internal combustion engine diverted part of the exhaust gas into the open, bypassing the low-pressure turbine will. In this operating range, the low pressure stage, which must be designed for a low speed of the internal combustion engine, practically does not contribute Pressure increase of the charge air due to the low absorption volume of the internal combustion engine in the optimal Design point small, so that the supercharger of the low-pressure stage has to be built very small. At high Speed of the internal combustion engine increases the absorption volume accordingly, so that the charger of the High pressure stage, which has its optimal design point in this operating range and essentially causes the pressure increase, a large volume must process and is designed accordingly large. The large volume, however, is greater than the small The exhaust gas turbocharger of the low-pressure stage is sucked in, in this operating range for the enforced Volume has a very poor efficiency. Furthermore, the exhaust gas turbine must be of the low pressure stage for the partial load range of the internal combustion engine can be designed. The exhaust gas energy is in this operating range relatively low. The losses that occur in the upstream high-pressure gas turbine and the supply lines wirken sich in diesem Betriebsbereich besonders nachteilig aus. Vor allem ist das Beschleunigungsvermögen der Brennkraftmaschine durch die Verluste und die ungünstigen Trägheitsmoment der Hochdruckstufe unzureichend.have a particularly detrimental effect in this operating range. Above all, the ability of the internal combustion engine to accelerate is due to the losses and the unfavorable moment of inertia of the high pressure stage insufficient.
Dei Erfindung liegt die Aufgabe zugrunde, den Wirkungsgrad, das Beschleunigungsverhalten und die Regelbarkeit der Brennkraftmaschine in bezug auf ein gewünschtes Betriebskennfeld zu verbessern. DieseThe invention is based on the object, the efficiency, the acceleration behavior and the To improve controllability of the internal combustion engine in relation to a desired operating map. These
ic Aufgabe wird erfindungsgemäß bei einer Brennkraftmaschine der eingangs beschriebenen Art dadurch gelöst, daß der Niederdrucklader für den vollen Luftgewichtsdurchsatz bei etwa 80 bis 100% der Nenndrehzahl der Brennkraftmaschine und der HochAccording to the invention, the object is thereby achieved in an internal combustion engine of the type described at the outset solved that the low pressure charger for the full air weight throughput at about 80 to 100% of the Nominal speed of the internal combustion engine and the high druckfeder für einen dem gewünschten Drehmoment verlauf entsprechenden Luftgewichtsdurchsatz bei niedriger Drehzahl der Brennkraftmaschine ausgelegt ist und die Hochdruckturbine regelbar umgehbar ist Bei der erfindungsgemäßen Gestaltung arbeitet dercompression spring for a desired torque course is designed corresponding air weight throughput at low speed of the internal combustion engine and the high pressure turbine can be bypassed in a controllable manner In the design according to the invention, the works Abgasturbolader der Hochdruckstufe im Teildrehzahlbereich der Brennkraftmaschine bei kleinem Schluckvolumen optimal. Der Abgasturbolader der Niederdruckstufe arbeitet dagegen bei Nenndrehzahl der Brennkraftmaschine im Auslegungspunkt entsprechend demExhaust gas turbocharger of the high pressure stage is optimal in the partial speed range of the internal combustion engine with a small absorption volume. The exhaust gas turbocharger of the low-pressure stage, on the other hand, works at the rated speed of the internal combustion engine in the design point according to the gestiegenen Luftdurchsatz. Der Lader baut daher größer. Da dem Lader der Hochdruckstufe bei Nenndrehzahl bereits verdichtete Ladelufi zugeführt wird, die ggf. durch einen Zwischenkühler gekühlt wurde, ist das durchgesetzte Luftvolumen relativ klein,increased air flow. The loader is therefore bigger. Since the loader of the high pressure stage Nominal speed already compressed charge air is supplied, which may be cooled by an intercooler the air volume passed through is relatively small, so daß es mit gutem Wirkungsgrad jedoch ohne nennenswerte Druckerhöhung den kleineren Lader der Hochdruckstufe durchströmen kann. Die Hochdruckgasturbine ist für den Teildrehzahlbereich ausgelegt. In diesem Betriebsbereich trägt die Niederso that it is with good efficiency but without significant pressure increase can flow through the smaller charger of the high pressure stage. the High pressure gas turbine is designed for the partial speed range. In this operating area, the Nieder druckstufe nur wenig zur Druckerhöhung der Ladeluft bei, jedoch ist der Volumenstrom aufgrund der niedrigen Drehzahl der Brennkraftmaschine relativ gering, so daß die Ansaugluft ohne besondere Verluste die Niederdruckstufe durchströmt und von derpressure level only a little to increase the pressure of the charge air at, however, the volume flow is relative due to the low speed of the internal combustion engine low, so that the intake air flows through the low-pressure stage and from the Hochdruckstufe auf den erforderlichen Druck verdichtet wird. Aufgrund der kleinen Baugröße der Hochdruckstufe sind die Trägheitsmomente in dieser Stufe sehr klein, so daß sie schnell einer Drehzahländerung folgen kann. Ferner kann sie mit dem für denHigh pressure stage is compressed to the required pressure. Due to the small size of the high pressure stage, the moments of inertia are in this stage very small, so they change speed quickly can follow. It can also be used for the Teildrehzahlbereich günstigeren Stoßverfahren betrieben werden, so daß insgesamt ein gutes Beschleunigungsverhalten und ein guter Wirkungsgrad der Brennkraftmaschine erzielt wird. In Ausgestaltung der Erfindung wird ferner vorgePartial speed range more favorable impact processes are operated, so that overall good acceleration behavior and good efficiency of the Internal combustion engine is achieved. In an embodiment of the invention is also provided schlagen, daß der Hochdrucklader bei etwa 40 bis 60% der Nenndrehzahl der Brennkraftmaschine das gleiche Druckverhältnis von ungefähr 1,6 bis 2,6 hat wie der Niederdlrucklader bei 80 bis 100% der NenndrehzahL Es ist dadurch möglich, über einen weiten Betriebsbereichsuggest that the high pressure charger at about 40 to 60% the rated speed of the internal combustion engine has the same pressure ratio of about 1.6 to 2.6 as the Low-pressure supercharger at 80 to 100% of the nominal speed. It is therefore possible over a wide operating range einen annähernd konstanten Ladedruck zu fahren.to drive an approximately constant boost pressure.
In der Zeichnung sind Ausführungsbeispiele der Erfindung dargestelltExemplary embodiments of the invention are shown in the drawing
A b b. 1 zeigt eine schematische Darstellung einer erfindungsgemäßen Brennkraftmaschine mit jeweilsA b b. 1 shows a schematic representation of an internal combustion engine according to the invention, each with einem Abgasturbolader in der Niederdruck- und Hochdruckstufe.an exhaust gas turbocharger in the low-pressure and high-pressure stage.
A b b. 2 zeigt ebenfalls schematisch eine erfindungsgemäße Brennkraftmaschine mit jeweils mehreren Abgasturboladern in der Niederdruck- und HochdruckA b b. 2 likewise schematically shows an internal combustion engine according to the invention, each with several Exhaust gas turbochargers in the low and high pressure stufe.step.
Mit 1 ist eine arbeitsraumbildende Brennkraftmaschine, z. B. eine Hubkolben- oder Rotationskolben-Brennkraftmaschine bezeichnet An der Brennkraftmaschine 1With 1 is a workspace-forming internal combustion engine, z. B. a reciprocating or rotary piston internal combustion engine referred to on the internal combustion engine 1
ist ein Aufladeaggregat angeschlossen, das aus einem Niederdruckteil 2 mit einer Abgasturbine 3 und einem Lader 4 sowie eine Hochdruckstufe 5 mit einer Abgasturbine 6 und einem Lader 7 besteht. Die Niederdruckstufe 4 ist beispielsweise für ein Druckverhältnis von 1,6 bis 2,6 und einem Luftgewichtsdurchsatz von 160 bis 200% des Saugbetriebs bei 80 bis 100% der Nenndrehzahl der Brennkraftmaschine ausgelegt. Der Auslegepunkt der Hochdruckstufe 5 liegt bei gleichem Druckverhältnis und ungefähr einem entsprechenden Luftgewichtsdurchsatz bei 40 bis 60% der Nenndrehzahl der Brennkraftmaschine.a charging unit is connected, which consists of a low-pressure part 2 with an exhaust gas turbine 3 and a Loader 4 and a high pressure stage 5 with an exhaust gas turbine 6 and a loader 7 consists. the Low pressure level 4 is for example for a pressure ratio of 1.6 to 2.6 and an air weight throughput from 160 to 200% of the suction operation at 80 to 100% of the Rated speed of the internal combustion engine designed. The design point of the high pressure stage 5 is the same Pressure ratio and approximately a corresponding air weight throughput at 40 to 60% of the nominal speed the internal combustion engine.
Beim Anfahren der Brennkraftmaschine 1 wird die Niederdruckstufe mittels einer Bypaßleitung 8 umgangen, die von einem Steuerventil 9 beherrscht wird. Erst wenn die Niederdruckstufe 2 einen Überdruck liefert, wird die Bypaßleitung 8 geschlossen. Zwischen der Niederdruckstufe 2 und der Hochdruckstufe 5 ist ein Zwischenkühler 10 angeordnet Die Hochdruckstufe 5 kann abgasseitig durch eine Bypaßleitung 1 ί umgangen werden, die von einem Absteuerventil 12 beherrscht wird. Dadurch wird im oberen Drehzahlbereich so viel Abgas abgezweigt und direkt in die Niederdruckstufe 2 geleitet, daß die Niederdruck-Turbine annähernd mit der vollen Abgasenergie beaufschlagt wird. In der Hochdruckstufe wird nun so viel Abgasenergie verbraucht, wie zur Aufrechterhaltung des Ladeluftdruckes erforderlich isL Der Luftdurchsatz durch die Hochdruckstufe 5 soll also nicht behindert werden, aber der Ladedruck auch nicht oder nur geringfügig steigen. In diesem Betriebsbereich wird der Ladedruck im wesentlichen von der Niederdruckstufe 2 erzeugt. Zwischen der Brennkraftmaschine 1 und der Hochdruckstufe 5 ist ein Abgaswärmetauscher 13 und parallel dazu ein Ladeluftkühler 14 angeordnet. Ein Schaltventil 15 leitet in Abhängigkeit von der Ladelufttemperatur die Ladeluft mehr oder weniger durch den Abgaswärmetauscher 13 oder den Ladeluftkühler 14, so daß über weite Betriebsbereiche der Brennkraftmaschine 1 die Ladelufttemperatur annähernd konstant gehalten werden kann.When starting the internal combustion engine 1, the low-pressure stage is bypassed by means of a bypass line 8, which is controlled by a control valve 9. Only when the low pressure stage 2 supplies an overpressure, the bypass line 8 is closed. Between the low pressure stage 2 and the high pressure stage 5 is a Intercooler 10 is arranged. The high pressure stage 5 can be bypassed on the exhaust gas side by a bypass line 1 which is controlled by a shut-off valve 12. As a result, there is so much in the upper speed range Exhaust gas branched off and passed directly into the low pressure stage 2 that the low pressure turbine approximately with the full exhaust gas energy is applied. So much exhaust gas energy is now consumed in the high pressure stage, as required to maintain the charge air pressure isL the air throughput through the high pressure stage 5 should therefore not be hindered, but the boost pressure should not or only slightly rise either. In this operating range is the boost pressure essentially generated by the low pressure stage 2. Between the internal combustion engine 1 and the high pressure stage 5 is an exhaust gas heat exchanger 13 and a charge air cooler 14 arranged parallel thereto. A switching valve 15 conducts Depending on the charge air temperature, the charge air flows more or less through the exhaust gas heat exchanger 13 or the intercooler 14, so that over wide operating ranges of the internal combustion engine 1 the Charge air temperature can be kept approximately constant.
Die Brennkraftmaschine nach A b b. 2 unterscheidet sich im wesentlichen von der Ausführung nach A b b. 1 dadurch, daß je Ladestufe mehrere parallel geschaltete Turbolader vorgesehen sind. So weist die Niederdruckstufe 2 vier parallel geschaltete Abgasturbinen 3 auf, die durch selbststeuernde Klappenventile 16 entsprechend den Betriebsverhältnissen zu- und abgeschaltet werden.The internal combustion engine according to A b b. 2 differs essentially from the version according to A b b. 1 in that a plurality of turbochargers connected in parallel are provided for each charging stage. So shows the low pressure stage 2 four exhaust gas turbines 3 connected in parallel, which are controlled by self-regulating flap valves 16 accordingly can be switched on and off depending on the operating conditions.
ίο Ebenfalls sind vier Lader 4 vorhanden, die mit K-lappenventilen 17 zu- und abschaltbar sind.ίο There are also four loaders 4 available with K-flap valves 17 can be switched on and off.
In der Hochdruckstufe 5 sind jeweils zwei parallel geschaltete Abgasturbinen 6 und Lader 7 vorhanden. Für jede Abgasturbine 6 ist eine Bypaßleitung 11 mit einem Abstellventil 12 vorgesehen. Von der Hochdruckstufe 5 gelangt die verdichtete Luft durch Schaltventile 15 in Abgaswärmetauscher 13 oder Ladeluftkühler 14. Zwischen der Niederdruckstufe 2 und der Hochdruckstufe 5 sind Zwischenkühler 10 vorgesehen.In the high pressure stage 5 there are two exhaust gas turbines 6 and supercharger 7 connected in parallel. A bypass line 11 with a shut-off valve 12 is provided for each exhaust gas turbine 6. From the high pressure stage 5, the compressed air passes through switching valves 15 into exhaust gas heat exchanger 13 or charge air cooler 14. Intercoolers 10 are provided between the low-pressure stage 2 and the high-pressure stage 5.
Zu der Erhöhung der Abgasenergie im niedrigen Drehzahl- und Lastbereich wird hinter der Hochdruckstufe
5 ein Teil der verdichteten Luft einer Brennkammer 18 zugeführt, deren Brenngase die Abgasturbinen
der Niederdruckstufe beaufschlagen. Der Luftdurchsatz durch die Brennkammer wird durch ein Regelventil 19
bestimmt, und kann so bemessen sein, daß beim Start der Brennkraftmaschine 1 ein Abgasturbolader betrieben
werden kann.
Zur Verbesserung der Abgasqualität sind Abgasrückrohrleitungen 20 bzw. 21 vorgesehen, die das Abgassystem
mit dem Frischluftsystem verbinden und von Regelventilen 22 und 23 beherrscht werden. Die
Abgasrückführungen in der Niederdruck- und in der Hochdruckstufe können alternativ angewendet werden,
wobei die Abgasrückführung in der Hochdruckstufe 5 zwischen den Zwischenkühlern 10 und den Verdichtern
7 den Vorteil hat, daß die Zwischenkühler 10 durch die Abgase nicht verschmutzt werden.To increase the exhaust gas energy in the low speed and load range, some of the compressed air is fed to a combustion chamber 18 downstream of the high pressure stage 5, the combustion gases of which act on the exhaust gas turbines of the low pressure stage. The air throughput through the combustion chamber is determined by a control valve 19 and can be dimensioned such that an exhaust gas turbocharger can be operated when the internal combustion engine 1 is started.
To improve the exhaust gas quality, exhaust gas return pipes 20 and 21 are provided, which connect the exhaust system with the fresh air system and are controlled by control valves 22 and 23. The exhaust gas recirculation in the low pressure and in the high pressure stage can be used alternatively, the exhaust gas recirculation in the high pressure stage 5 between the intercoolers 10 and the compressors 7 having the advantage that the intercoolers 10 are not contaminated by the exhaust gases.
Hierzu 2 Blatt ZeichnungenFor this purpose 2 sheets of drawings
Claims (2)
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE2544471A DE2544471C3 (en) | 1975-10-04 | 1975-10-04 | Internal combustion engine that forms a working space with two or more exhaust gas turbochargers connected in series |
| FR7625875A FR2326581A1 (en) | 1975-10-04 | 1976-08-26 | INTERNAL COMBUSTION ENGINE WITH SUPERCHARGING |
| GB37177/76A GB1551833A (en) | 1975-10-04 | 1976-09-08 | Supercharged internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE2544471A DE2544471C3 (en) | 1975-10-04 | 1975-10-04 | Internal combustion engine that forms a working space with two or more exhaust gas turbochargers connected in series |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| DE2544471A1 DE2544471A1 (en) | 1977-04-07 |
| DE2544471B2 true DE2544471B2 (en) | 1978-07-06 |
| DE2544471C3 DE2544471C3 (en) | 1979-03-22 |
Family
ID=5958309
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| DE2544471A Expired DE2544471C3 (en) | 1975-10-04 | 1975-10-04 | Internal combustion engine that forms a working space with two or more exhaust gas turbochargers connected in series |
Country Status (3)
| Country | Link |
|---|---|
| DE (1) | DE2544471C3 (en) |
| FR (1) | FR2326581A1 (en) |
| GB (1) | GB1551833A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3818241A1 (en) * | 1987-05-29 | 1988-12-08 | Usui Kokusai Sangyo Kk | TURBOCHARGER ENGINE SYSTEM |
| DE3824373C1 (en) * | 1988-07-19 | 1989-05-18 | Mtu Friedrichshafen Gmbh | Supercharged piston internal combustion engine with a plurality of exhaust turbochargers functioning in parallel |
| DE19837978B4 (en) * | 1998-04-16 | 2006-05-18 | Borgwarner Turbo Systems Gmbh | Air-flow controller in twin stage turbocharged internal combustion engine |
Families Citing this family (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2965419D1 (en) * | 1979-02-19 | 1983-07-07 | Bbc Brown Boveri & Cie | Exhaust-gas driven turbocharger having two stages |
| DE3046875A1 (en) * | 1980-12-12 | 1982-07-15 | Mtu Motoren- Und Turbinen-Union Friedrichshafen Gmbh, 7990 Friedrichshafen | "INTERNAL COMBUSTION ENGINE" |
| DE3046876C2 (en) * | 1980-12-12 | 1987-05-14 | Mtu Motoren- Und Turbinen-Union Friedrichshafen Gmbh, 7990 Friedrichshafen | Internal combustion engine with turbocharger |
| DE3214205A1 (en) * | 1982-04-17 | 1983-10-20 | Klöckner-Humboldt-Deutz AG, 5000 Köln | Internal combustion engine with at least one exhaust gas turbocharger |
| DE3903563C1 (en) * | 1988-07-19 | 1990-03-22 | Mtu Friedrichshafen Gmbh | |
| CA2448458C (en) * | 1994-05-25 | 2008-08-19 | Man B&W Diesel Ltd. | Turbocharged internal combustion engine |
| US5577900A (en) * | 1994-05-25 | 1996-11-26 | Gec- Alsthom Diesels Ltd. | Turbocharged internal combustion engine |
| DE19514572C2 (en) * | 1995-04-20 | 1997-04-30 | Man Nutzfahrzeuge Ag | Supercharged internal combustion engine |
| DE19547994A1 (en) * | 1995-12-21 | 1997-06-26 | Bayerische Motoren Werke Ag | Internal combustion engine with two exhaust gas turbochargers acting in parallel |
| DE19709879A1 (en) | 1997-03-11 | 1998-09-24 | Man Nutzfahrzeuge Ag | Control device for a supercharged internal combustion engine |
| US6062026A (en) * | 1997-05-30 | 2000-05-16 | Turbodyne Systems, Inc. | Turbocharging systems for internal combustion engines |
| DE19835978C1 (en) * | 1998-08-08 | 1999-11-25 | Daimler Chrysler Ag | Motor vehicle twin turbocharger internal combustion engine with exhaust gas recycling |
| US6324848B1 (en) * | 2000-09-21 | 2001-12-04 | Caterpillar Inc. | Turbocharger system to inhibit surge in a multi-stage compressor |
| US7975478B2 (en) | 2007-06-26 | 2011-07-12 | International Engine Intellectual Property Company, Llc | Internal combustion engine having compressor with first and second tributary inlets |
| DE102008048035A1 (en) * | 2008-09-19 | 2010-03-25 | Man Nutzfahrzeuge Ag | Internal combustion engine with exhaust gas recirculation |
| DE102012011227A1 (en) | 2012-06-05 | 2013-12-05 | Daimler Ag | Internal combustion engine for passenger car, has first and second liquid-gas heat exchangers arranged downstream of compressor arranged with air intake, where each of liquid-gas heat exchangers comprises bypass device |
| US9010117B2 (en) * | 2013-03-15 | 2015-04-21 | Cummins Inc. | Multi-stage turbocharger system with intercooling and aftercooling |
| DE102015203621A1 (en) * | 2015-03-02 | 2016-09-29 | Bayerische Motoren Werke Aktiengesellschaft | Two-stage turbocharger charging device for an internal combustion engine |
-
1975
- 1975-10-04 DE DE2544471A patent/DE2544471C3/en not_active Expired
-
1976
- 1976-08-26 FR FR7625875A patent/FR2326581A1/en active Granted
- 1976-09-08 GB GB37177/76A patent/GB1551833A/en not_active Expired
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3818241A1 (en) * | 1987-05-29 | 1988-12-08 | Usui Kokusai Sangyo Kk | TURBOCHARGER ENGINE SYSTEM |
| DE3824373C1 (en) * | 1988-07-19 | 1989-05-18 | Mtu Friedrichshafen Gmbh | Supercharged piston internal combustion engine with a plurality of exhaust turbochargers functioning in parallel |
| DE19837978B4 (en) * | 1998-04-16 | 2006-05-18 | Borgwarner Turbo Systems Gmbh | Air-flow controller in twin stage turbocharged internal combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| FR2326581A1 (en) | 1977-04-29 |
| DE2544471C3 (en) | 1979-03-22 |
| FR2326581B1 (en) | 1978-11-03 |
| DE2544471A1 (en) | 1977-04-07 |
| GB1551833A (en) | 1979-09-05 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C3 | Grant after two publication steps (3rd publication) | ||
| 8339 | Ceased/non-payment of the annual fee |