DE2544471A1 - CHARGED, WORK SPACE-FORMING COMBUSTION ENGINE - Google Patents
CHARGED, WORK SPACE-FORMING COMBUSTION ENGINEInfo
- Publication number
- DE2544471A1 DE2544471A1 DE19752544471 DE2544471A DE2544471A1 DE 2544471 A1 DE2544471 A1 DE 2544471A1 DE 19752544471 DE19752544471 DE 19752544471 DE 2544471 A DE2544471 A DE 2544471A DE 2544471 A1 DE2544471 A1 DE 2544471A1
- Authority
- DE
- Germany
- Prior art keywords
- combustion engine
- internal combustion
- pressure stage
- exhaust gas
- speed
- 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 41
- 238000000034 method Methods 0.000 claims description 3
- 230000001105 regulatory effect Effects 0.000 claims description 2
- 230000001419 dependent effect Effects 0.000 claims 1
- 239000007789 gas Substances 0.000 description 29
- 230000006978 adaptation Effects 0.000 description 1
- 239000000567 combustion gas Substances 0.000 description 1
- 230000000994 depressogenic effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000000446 fuel Substances 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
-
- 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
Kiöckner-Humboicft-DeutzAG AM^JTIUf t Köln CO, dan 24. September 1975 Kiöckner-Humboicft-DeutzAG AM ^ JTIUf t Cologne CO, on September 24, 1975
Aufgeladene, arbeitsraumbildende BrennkraftmaschineSupercharged internal combustion engine that creates workspace
Die Erfindung betrifft eine aufgeladen«f arbeitsraumbildende Brennkraftmaschine mit zwei oder mehreren In Reihe geschalteten Turboladern, die breite Betriebslcennfelder und gute Wirkungsgrade bei niedrigen Drucfcverhälthissen aufweisen.The invention relates to a charged "f working space-forming internal combustion engine having two or more series-connected turbochargers having wide Betriebslcennfelder and high efficiencies at low Drucfcverhälthissen.
Bei einfach aufgeladenen Brennkraftmaschinen ist es mit Rücksicht auf das Drehmoment im unteren Drehsahlbereich üblich, den Abgasturbolader auf eine mittlere Drehzahl auszulegen. Dies hat zur Folge, daß im oberen Drehzahlbereich die Ladedrücke unnötig hoch ansteigen und eine hohe Belastung des Triebwerkes und der Bauteile bewirken. Als Abhilfe wird von einer Bypaßregelung Gebrauch gemacht, bei der zum Teil das Abgas die Turbine umgeht. Dieses Vorgehen ist unwirtschaftlich, da es zu höherem Kraftstoffverbrauch führt. Diese Nachtelle werden um so größer, je höher der Aufladegrad ist.In the case of simply charged internal combustion engines, it is common, with regard to the torque in the lower speed range, to to design the exhaust gas turbocharger for a medium speed. This has the consequence that the boost pressures in the upper speed range increase unnecessarily high and cause a high load on the engine and the components. As a remedy, use is made of a bypass control in which the exhaust gas bypasses the turbine in part. This approach is uneconomical because it is too leads to higher fuel consumption. These detriments are all the greater, the higher the charge level.
Brennkraftmaschinen der eingangs beschriebenen Art sind bekannt (MTZ 1964, Seite 497). Der Erfindung liegt die AufgabeInternal combustion engines of the type described above are known (MTZ 1964, page 497). The invention has the task
7098U/01787098U / 0178
Klöckner-HumbddtMDeutzAG i/Arm^i»·!' - $ - 24.9.1975Klöckner-HumbddtMDeutzAG i / Arm ^ i »·! ' - $ - 9/24/1975
D 75/70D 75/70
zugrunde, den Aufladegrad der Brennkraftmaschine zu erhöhen und die Anpassung der Abgasturbolader an das gewünschte Betriebskennfeld der Brennkraftmaschine mit einfachen Mittein zu verbessern. Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß die Niederdruckstufe für den vollen Luftgewichtsdurchsatz bei hoher Drehzahl der Brennkraftmaschine und die Hochdruckstufe für einen dem gewünschten Drehmoment verlauf entsprechenden Luftgewichtsdurchsatz bei niedriger Drehzahl der Brennkraftmaschine ausgelegt ist und die Hochdruckstufe oberhalb einer vorgebbaren Drehzahl oder eittem vorgebbaren Drück abgasseitig1 teilweise und- regelbar umgehbar ist.based on increasing the degree of charging of the internal combustion engine and improving the adaptation of the exhaust gas turbocharger to the desired operating map of the internal combustion engine with simple means. This object is achieved according to the invention in that the low pressure stage is designed for the full air weight throughput at a high speed of the internal combustion engine and the high pressure stage for an air weight throughput corresponding to the desired torque profile at a low speed of the internal combustion engine, and the high pressure stage is designed above a specifiable speed or eittem specifiable pressure on the exhaust side 1 is partially and controllably bypassed.
Durch die erfindungsgemäße Auslegung erreicht man, daß die Hochdruckstufe im unteren und mittleren Drehzahlbereich bereits einen ausreichenden Ladedruck liefert, wobei beim Start und Hochfahret der Maschin· «Si« Niederdruckstufe in bekannter Weise zunächst uwgea^en werden k*nn. Bei höheren Drehzahlen wird die Hochdruck stuf« abgassei t ig1 iA»$*ngen, so daß ihr Druckverhältnis immer mehr abfällt, bis sie schließlich bei ErreichenThe design according to the invention ensures that the high-pressure stage already supplies sufficient boost pressure in the lower and middle speed range, and when the machine is started and started up, the low-pressure stage can initially be checked in a known manner. At higher speeds, the high pressure stage “exhaust side t ig 1 iA” $ * so that its pressure ratio drops more and more until it is finally reached when it is reached
der Nenndrehzahl der Brennkraftmaschine den Ladedruck nur noch geringfügig oder gar nicht erhöht· Bei Nenndrehzahl der Brennkraftmaschine arbeitet die Niederdruckstuf· des Abgastur-the nominal speed of the internal combustion engine increases the boost pressure only slightly or not at all Internal combustion engine works the low pressure stage of the exhaust gas
7098U/01787098U / 0178
Klöckner-Humboldt-DeutzAG AMIkFf Lf -^- 24.9.1975Klöckner-Humboldt-DeutzAG AMIkFf Lf - ^ - 24.9.1975
D 75/70D 75/70
boladers in ihrem Auslegungspunkt und erzeugt das gewünschte Druckverhältnis. Durch die erfindungsgemäße Gestaltung verschlechtert sich zwar der Spitzenwirkungsgrad der gesamten Aufladung, jedoch erreicht man für einen breiten Betriebsbereich einen guten Durchschnittswirkungsgrad mit einem guten Drehmomentverhalten der Brennkraftmaschine.boladers in their design point and generates the desired Pressure ratio. The design according to the invention admittedly worsens the peak efficiency of the entire charging, however, a good average efficiency is achieved for a wide operating range a good torque behavior of the internal combustion engine.
In Ausgestaltung der Erfindung wird vorgeschlagen, daß die Niederdruckstufe vornehmlich für «in Druekverhältnis awischen 1,6 und 2,6 bei 80 bis 100 % der Nenndrehzahl der Brennkraftmaschine und die Hochdruck stufe für ungefähr das gleiche Druckverhältnis bei 40 bis 60 % der Henndrehzahl der Brennkraftmaschine ausgelegt ist. Die Regelung der Rochdruckstufe erfolgt gemäß einer Ausgestaltung der Erfindung dadurch, daß die Hochdruckstufe abgasseitig einen Bypafl aufweist, durch den bei etwa 65 bis 100 % der Nenndrehzahl der Brennkraftmaschine der Abgasdurchsatz soweit verringert wird, daß der Luftdurchsatz durch die Hochdruckstufe nicht behindert, aber der Ladedruck auch nicht oder nur geringfügig erhöht wird. Sie kann in diesem Fall in Ausgestaltung der Erfindung luft- und abgasseitig umgangen werden. Eine andere Möglichkeit der RegelungIn an embodiment of the invention, it is proposed that the low pressure stage primarily for «in pressure ratio awischen 1.6 and 2.6 at 80 to 100% of the rated speed of the internal combustion engine and the high pressure stage for approximately the same pressure ratio at 40 to 60 % of the engine speed is designed. According to one embodiment of the invention, the high pressure stage is regulated in that the high pressure stage has a bypass on the exhaust gas side, by means of which the exhaust gas throughput is reduced at around 65 to 100 % of the nominal speed of the internal combustion engine so that the air throughput through the high pressure stage is not hindered, but the boost pressure also not or only slightly increased. In this case, in an embodiment of the invention, it can be bypassed on the air and exhaust gas sides. Another way of regulation
70 9 8 U/0 17870 9 8 U / 0 178
AliMtlAliMtl
D 75/70D 75/70
besteht gemäß einer weiteren Ausgestaltung der Erfindung darin, daß für jede Verdichterstufe mehrere parallel geschaltete Abgasturbolader angeordnet sind, die einsein in Abhängigkeit maßgeblicher Kenngrößen, z. B. Ladeluftdruck, Drehzahl und Last der Brennkraftmaschine, zu» und abschaltbar sind. Im Bereich des maximalen Drehmoments bei mittleren Drehsahlen ist dann beispielsweise in der Niederdruckstufe ein Turbolader abzuschalten. Im Bereich zwischen dem Zu- und Abschalten von Turboladern kann zweckmäßig eine Bypaßregelung wirksam werden.According to a further embodiment of the invention, several exhaust gas turbochargers connected in parallel are arranged for each compressor stage and are single depending on relevant parameters, e.g. B. charge air pressure, speed and load of the internal combustion engine, to »and can be switched off. In the range of the maximum torque at medium speeds is then, for example, in the Switch off a turbocharger in the low-pressure stage. In the area between switching turbochargers on and off, expediently a bypass control become effective.
Durch die Verwendung mehrerer kleiner Turbolader ist ein schnelleres Anfahren der Brennkraftmaschine möglich, da die kleineren Turbolader geringere Trägheitsmomente haben. Ferner wird durch die erfindungsgemäße Gestaltung erreicht, daß die Spitzendr ticke im gesamten Vollastbereich niedrig gehalten werden und geringe Abgasgegendrücke im Teillastbereich herrschen.By using several small turbochargers, the internal combustion engine can be started up more quickly, since the smaller turbochargers have lower moments of inertia. Furthermore, it is achieved by the design according to the invention that the peak pressures are kept low in the entire full load range and low exhaust back pressures in the partial load range to rule.
70981 4/017870981 4/0178
254U71 Λ KHB 254U71 Λ KHB
D 75/70D 75/70
Um die Regelvorgänge optimal dem gewünschten Betriebskennfeld der Brennkraftmaschine anzupassen, ist es vorteilhaft, in Ausgestaltung der Erfindung die Zu- und Abschaltvorgänge durch elektrische, hydraulische oder pneumatische Schaltelemente in Abhängigkeit der maßgebenden Einflußgrößen entsprechend dem Arbeitspunkt der Brennkraftmaschine im Betriebskennfeld elektronisch zu regeln.In order to optimize the control processes to the desired operating map to adapt the internal combustion engine, it is advantageous in an embodiment of the invention, the connection and disconnection processes by electrical, hydraulic or pneumatic switching elements depending on the relevant influencing variables to regulate electronically the operating point of the internal combustion engine in the operating map.
Die Regelung ist so auszulegen, daß jeweils nur 1 Lader zu oder abgeschaltet wird, um Sprünge im Druckverlauf zu vermeiden. The regulation is to be designed in such a way that only 1 charger is switched on or off in order to avoid jumps in the pressure curve.
In der Zeichnung sind Ausführungsbeispiele der Erfindung dargestellt. Exemplary embodiments of the invention are shown in the drawing.
Abb. 1 zeigt eine schematische Darstellung einer erfindungsgemKßen Brennkraftmaschine mit jeweils einem Abgasturbolader in der Niederdruck- und Hochdrucketufe.Fig. 1 shows a schematic representation of a K according to the invention Internal combustion engine with one exhaust gas turbocharger each in the low-pressure and high-pressure stages.
Abb. 2 zeigt ebenfalls echematisch eine erfindungsgemäße Brennkraftmaschine mit jeweils mehreren. Abgasturboladern in der Niederdruckstufe und Hochdruckstufe.Fig. 2 also shows a schematic diagram of one according to the invention Internal combustion engine, each with several. Exhaust gas turbochargers in the low pressure stage and high pressure stage.
70981 4/017870981 4/0178
Klöckner+tanboldt-OeulzAG U*\Ι%ΠO^ -JT-. 24.9.1975Klöckner + tanboldt-OeulzAG U * \ Ι% ΠO ^ -JT-. 9/24/1975
D 75/70D 75/70
Mit 1 Xmt~eine arbeltsraumbildende Brennkraftmaschine,ζ. Β. eine Hubkolben- oder Rotationskolben-Brennkraftmaschine bezeichnet, An der Brennkraftmaschine 1 ist ein Aufladeaggregat angeschlossen, das aus einem Niederdrückten & 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 Ϋ%$ bis 2r>,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.With 1 Xmt ~ a working space-forming internal combustion engine, ζ. Β. denotes a reciprocating or rotary piston internal combustion engine, a charging unit is connected to the internal combustion engine 1, which consists of a depressed unit with an exhaust gas turbine 3 and a charger 4 and a high pressure stage 5 with an exhaust gas turbine 6 and a charger 7. The low pressure stage 4 is designed, for example, for a pressure ratio of Ϋ% $ to 2r>, 6 and an air weight throughput of 160 to 200% of the suction operation at 80 to 100 % of the nominal speed of the internal combustion engine. The design point of the high pressure stage 5 is at the same pressure ratio and approximately a corresponding air weight throughput at 40 to 60 % of the nominal speed of 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 Bypaöleitung 8 geschlossen. Zwischen der Niederdruckstufe 2 und der Hochdruckstufe 5 ist ein Zwischenkühler 10 angeordnet. Die Hochdruckstufe 5 kann abgassei tig durch eine Bypaßleitung 11 umgangen werden, die von einemWhen the internal combustion engine 1 is started up, 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 is the bypass line 8 closed. An intermediate cooler 10 is arranged between the low-pressure stage 2 and the high-pressure stage 5. The high pressure stage 5 can be bypassed exhaust gas tig by a bypass line 11, which is of a
7098U/01787098U / 0178
Klöckner-Humboldt-DeutzAG ^iCH ΈλΜ -^- 24.9.1975Klöckner-Humboldt-DeutzAG ^ iCH ΈλΜ - ^ - 9/24/1975
D 75/70D 75/70
Absteuerventil 12 beherrscht wird. Dadurch tfrd im .oberen Drehzahlbereich soviel 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 soviel Abgasenergie verbraucht, wie zur Aufrechterhaltung des Ladeluftdruckes erforderlich ist. Der Luftdurchsatz durch die Hochdruckstufe 5 soll also nicht behindert werde», aber der Ladedruck- auch nicht oder nur geringfügig steigen. In diesem Betriebsbereich wird dar Ladedruck im wesentlichen von der Niederdruckstufe 2 erzeugt. Zwischen der Brennkraftmaschine 1 und der Hochdruck stufe 5 ist ein Abgaswärmetauscher 13 und parallel dazu ein Ladeluftkühler 14 angeordnet. Ein Schaltventil 15 leitet in Abhängigkeit von der Ladelufttetnperatur die LadeIuft 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.Shut-off valve 12 is mastered. As a result, tfrd in the .upper Speed range branched off as much exhaust gas and directly into the. Low pressure stage 2 passed that the low pressure turbine is applied approximately with the full exhaust gas energy. In the high pressure stage, as much exhaust gas energy is consumed as is necessary to maintain the charge air pressure is. The air throughput through the high pressure stage 5 should therefore not be hindered », but so should the boost pressure not or only slightly increase. In this operating range, the boost pressure is essentially from the low-pressure stage 2 generated. Between the internal combustion engine 1 and the high pressure stage 5, an exhaust gas heat exchanger 13 and a charge air cooler 14 is arranged in parallel. On-off valve 15 conducts depending on the charge air temperature the charge air more or less through the exhaust gas heat exchanger 13 or the charge air cooler 14, so that the charge air temperature approximately over wide operating ranges of the internal combustion engine 1 can be kept constant.
Die Br«nnfcraf tmaschin* nach Aßb» 1 uttt»ree&eide€' sicti* im wesentlichen van der Ausführung nach Abb. 1 dadurch, daß 3« LadestufeThe Br "nnfcraf tmaschin * according to Aßb" 1 uttt "ree & eide € 'sicti * essentially of the design according to Fig. 1 in that 3" loading stage
709814/0178709814/0178
Klöckner-Humboklt-Deutz AG A\I%P1IW -ST- 24.9.1975Klöckner-Humboklt-Deutz AG A \ I% P1IW -ST- 9/24/1975
D 75/70D 75/70
ΛΑΛΑ
mehrere parallel geschaltete Turbolader vorgesehen sind· So weist die Niederdruckstufe 2 vier parallel geschaltete Abgasturbinen 3 auf, die durch selbststeuernde Klappenventil 16 entsprechend den Betriebsverhältnissen zu- und abgeschaltet werden. Ebenfalls sind vier Lader 4 vorhanden, die mit Klappenventil en 17 ssu- und abschaltbar aind.several turbochargers connected in parallel are provided. Thus, the low-pressure stage 2 has four exhaust gas turbines 3 connected in parallel, which are switched on and off by self-controlling flap valve 16 according to the operating conditions. There are also four loaders 4, which can be switched on and off with flap valves 17.
In der Hochdruckstufe 5 sind jeweils zwei parallel geschaltete Abgasturbinen 6 und Lader 7 vorhanden. Für jede Abgasturbine 6 ist eine BypaBleitung 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, two are connected in parallel Exhaust gas turbines 6 and 7 superchargers are available. 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 the exhaust gas heat exchanger 13 or charge air cooler 14. Between the low pressure stage 2 and the high pressure stage 5 intercoolers 10 are provided.
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 19To increase the exhaust energy in the low speed and The load range is a part of the compressed after the high pressure stage 5 Air is supplied to a combustion chamber 18, the combustion gases of which act on the exhaust gas turbines of the low-pressure stage. The air flow through the combustion chamber is controlled by a control valve 19
709814/0178709814/0178
A KHDA KHD
Klöckner-Humboldt-Deutz AG A\ W\Wulrff - J/ - 24 . 9 . 19 75Klöckner-Humboldt-Deutz AG A \ W \ Wu lrff - J / - 24. 9. 19 75
D 75/70D 75/70
KLKL
bestimmt, und kann so bemessen sein, daß beim Start der BrennJcraftmaschine 1 ein Abgasturbolader betrieben werden kann.determined, and can be so dimensioned that when starting the BrennJcraftmaschine 1 an exhaust gas turbocharger are operated can.
Zur Verbesserung der Abgasqualität sind Abgasrückfuhrleitungen 20 bzw. 21 vorgesehen, die das Abgassystem mit dem Frischluftsystem verbinden und von Regelventilen 22 und 23 beherrscht werden. Die AbgasrückfOhrungen in der Niederdruckund 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.Exhaust gas recirculation lines are used to improve the exhaust gas quality 20 and 21, respectively, which connect the exhaust system with the fresh air system and control valves 22 and 23 be mastered. The exhaust gas recirculations in the low-pressure and in the high pressure stage can alternatively be used The exhaust gas recirculation in the high pressure stage 5 between the intercoolers 10 and the compressors 7 has the advantage that the intercoolers 10 are not contaminated by the exhaust gases.
7098U/01787098U / 0178
LeerseiteBlank page
Claims (7)
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 true DE2544471A1 (en) | 1977-04-07 |
DE2544471B2 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 (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2496165A1 (en) * | 1980-12-12 | 1982-06-18 | Mtu Friedrichshafen Gmbh | INTERNAL COMBUSTION ENGINE SUPERCHARGED BY EXHAUST GAS TURBOCHARGERS |
FR2496164A1 (en) * | 1980-12-12 | 1982-06-18 | Mtu Friedrichshafen Gmbh | INTERNAL COMBUSTION ENGINE SUPERCHARGED BY EXHAUST GAS TURBOCHARGERS |
US5069194A (en) * | 1988-07-19 | 1991-12-03 | Mtu Motoren-Und Turbine-Union | Control of a charged, piston internal combustion engine having a plurality of exhaust gas turbochargers |
DE19514572A1 (en) * | 1995-04-20 | 1996-10-24 | Man Nutzfahrzeuge Ag | Charged combustion engine with high pressure stage |
EP0864737A1 (en) | 1997-03-11 | 1998-09-16 | Man Nutzfahrzeuge Ag | Control device for a pressure-charged internal combustion engine |
EP2166211A1 (en) * | 2008-09-19 | 2010-03-24 | MAN Nutzfahrzeuge Aktiengesellschaft | 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 |
WO2016139009A1 (en) * | 2015-03-02 | 2016-09-09 | Bayerische Motoren Werke Aktiengesellschaft | Two-stage exhaust-gas turbocharging device for an internal combustion engine |
EP2971637A4 (en) * | 2013-03-15 | 2016-10-26 | Cummins Inc | Intercooling and aftercooling multi-stage turbocharger system |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0014778B1 (en) * | 1979-02-19 | 1983-05-18 | BBC Aktiengesellschaft Brown, Boveri & Cie. | Exhaust-gas driven turbocharger having two stages |
DE3214205A1 (en) * | 1982-04-17 | 1983-10-20 | Klöckner-Humboldt-Deutz AG, 5000 Köln | Internal combustion engine with at least one exhaust gas turbocharger |
US4930315A (en) * | 1987-05-29 | 1990-06-05 | Usui Kokusai Sangyo Kabushiki Kaisha | Turbo-charger 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 |
CA2124264C (en) * | 1994-05-25 | 2004-07-27 | John Nigel Ramsden | Turbocharged internal combustion engine |
US5577900A (en) * | 1994-05-25 | 1996-11-26 | Gec- Alsthom Diesels Ltd. | Turbocharged 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 |
US6062026A (en) * | 1997-05-30 | 2000-05-16 | Turbodyne Systems, Inc. | Turbocharging systems for internal combustion engines |
DE19837978B4 (en) * | 1998-04-16 | 2006-05-18 | Borgwarner Turbo Systems Gmbh | Air-flow controller in twin stage turbocharged internal combustion engine |
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 |
-
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 (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2496165A1 (en) * | 1980-12-12 | 1982-06-18 | Mtu Friedrichshafen Gmbh | INTERNAL COMBUSTION ENGINE SUPERCHARGED BY EXHAUST GAS TURBOCHARGERS |
FR2496164A1 (en) * | 1980-12-12 | 1982-06-18 | Mtu Friedrichshafen Gmbh | INTERNAL COMBUSTION ENGINE SUPERCHARGED BY EXHAUST GAS TURBOCHARGERS |
US5069194A (en) * | 1988-07-19 | 1991-12-03 | Mtu Motoren-Und Turbine-Union | Control of a charged, piston internal combustion engine having a plurality of exhaust gas turbochargers |
DE19514572A1 (en) * | 1995-04-20 | 1996-10-24 | Man Nutzfahrzeuge Ag | Charged combustion engine with high pressure stage |
EP0864737A1 (en) | 1997-03-11 | 1998-09-16 | Man Nutzfahrzeuge Ag | Control device for a pressure-charged internal combustion engine |
EP2166211A1 (en) * | 2008-09-19 | 2010-03-24 | MAN Nutzfahrzeuge Aktiengesellschaft | 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 |
EP2971637A4 (en) * | 2013-03-15 | 2016-10-26 | Cummins Inc | Intercooling and aftercooling multi-stage turbocharger system |
WO2016139009A1 (en) * | 2015-03-02 | 2016-09-09 | Bayerische Motoren Werke Aktiengesellschaft | Two-stage exhaust-gas turbocharging device for an internal combustion engine |
CN107002551A (en) * | 2015-03-02 | 2017-08-01 | 宝马股份公司 | Two-stage exhaust gas turbocharge device for internal combustion engine |
Also Published As
Publication number | Publication date |
---|---|
FR2326581A1 (en) | 1977-04-29 |
GB1551833A (en) | 1979-09-05 |
FR2326581B1 (en) | 1978-11-03 |
DE2544471C3 (en) | 1979-03-22 |
DE2544471B2 (en) | 1978-07-06 |
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C3 | Grant after two publication steps (3rd publication) | ||
8339 | Ceased/non-payment of the annual fee |