DE3832134A1 - Utilisation of energy from the cylinder head walls of axial flow rotary engines with partially shut-off fuel feed - Google Patents

Utilisation of energy from the cylinder head walls of axial flow rotary engines with partially shut-off fuel feed

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Publication number
DE3832134A1
DE3832134A1 DE19883832134 DE3832134A DE3832134A1 DE 3832134 A1 DE3832134 A1 DE 3832134A1 DE 19883832134 DE19883832134 DE 19883832134 DE 3832134 A DE3832134 A DE 3832134A DE 3832134 A1 DE3832134 A1 DE 3832134A1
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Germany
Prior art keywords
cylinder
cylinders
stroke
energy
cylinder head
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Granted
Application number
DE19883832134
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German (de)
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DE3832134C2 (en
Inventor
Des Erfinders Auf Nennung Verzicht
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kuehner Hubert Dipl-Ing (fh) 7993 Kressbronn De
Original Assignee
Kuehner Hubert Dipl-Ing (fh) 7993 Kressbronn De
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Priority claimed from DE19883808506 external-priority patent/DE3808506A1/en
Application filed by Kuehner Hubert Dipl-Ing (fh) 7993 Kressbronn De filed Critical Kuehner Hubert Dipl-Ing (fh) 7993 Kressbronn De
Priority to DE19883832134 priority Critical patent/DE3832134C2/en
Publication of DE3832134A1 publication Critical patent/DE3832134A1/en
Application granted granted Critical
Publication of DE3832134C2 publication Critical patent/DE3832134C2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/06—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft the piston motion being transmitted by curved surfaces
    • 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
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
    • F02B2053/005—Wankel engines
    • 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
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

In order to achieve economical operation, the cylinder housing (11) moves in the direction of the arrow (8) beneath the static cylinder head cover (1) as represented in the development of the cylinder pitch circle according to Fig. 2. In the process, the pistons (7) carried in the cylinders (6) are guided by means of rollers (9) on a fixed lifting curve (10) with precisely two sinusoidal periods so that for one revolution of the cylinder housing (11) they perform a full working cycle of four strokes. In each working cycle, each cylinder (6) always moves over the same stroke zone of the cylinder cover (1). A characteristic temperature curve (a) according to Fig. 1 can therefore be assigned to the said stroke zones with the inlet port (2), the injection valve (3), the spark plug (4) and the exhaust port (5). The said temperature curve (a) has its highest values over the expansion stroke. If, between the working cylinders (6), the fuel feed in one or more cylinders (6) is then interrupted, their air which has only been compressed can absorb heat from the hot cylinder cover side in the expansion stroke and transmit this as additional pressure energy to the pistons (7). In the process the temperature curve assumed is approximately that of (b). <IMAGE>

Description

Die Erfindung betrifft die gesteuerte Unterbrechung der Kraftstoffzufuhr in einzelnen Zylindern von Achsial-Kreiskolbenmotoren mit Kraftstoffeinspritzung.The invention relates to controlled interruption the fuel supply in individual cylinders from Axial rotary piston engines with fuel injection.

Brennkraftmaschinen in Fahrzeugen mit hohem Leistungs­ angebot brauchen in vielen Verkehrssituationen nur einen Teil dieser Leistung, weshalb versucht wird im Teillastbetrieb oder bei Schiebebetrieb den Kraftstoffverbrauch zu reduzieren.Internal combustion engines in vehicles with high performance offer in many traffic situations only part of this achievement, which is why it is tried in partial load operation or in push mode Reduce fuel consumption.

Es ist bekannt, daß es bei Hubkolbenmotoren mit Kraftstoffeinspritzung die Möglichkeit gibt für alle oder einzelne Zylinder die Kraftstoffzufuhr zu unterbrechen, um so einen Teillast- oder Sparbetrieb zu erreichen.It is known that with reciprocating engines Fuel injection gives everyone the opportunity or individual cylinders to the fuel supply interrupt so as to operate at partial load or economy to reach.

Da Hubkolbenmotoren feste unveränderte Brennraumwände haben, kühlen sie bei Unterbrechung der Kraftstoff­ zufuhr durch den wiederholten Durchsatz kalter Frischluft und damit unterbrochener Verbrennung schnell stark aus.Reciprocating engines have fixed, unchanged combustion chamber walls they cool when the fuel is interrupted Feed through the repeated throughput cold Fresh air and thus interrupted combustion quickly out strong.

Es entstehen zu den immer vorhandenen Kompressions­ und Reibungsverlusten auch noch beträchtliche thermische Verluste.It results in the compression that is always present and friction losses also considerable thermal losses.

Der Erfindung liegt die Aufgabe zugrunde, die thermischen Verluste bei Achsial-Kreiskolbenmotoren nicht nur zu vermeiden, sondern aus den abgeschalteten Zylindern noch zusätzlich thermische Energie zu gewinnen. The invention is based, which thermal losses in axial rotary piston engines not only to avoid, but from the switched off Additional thermal energy to cylinders win.  

Die Aufgabe wird erfindungsgemäß dadurch gelöst, daß im Spar- oder Schubbetrieb bei 4-Takt-Achsial- Kreiskolbenmotoren mit sinusförmigem Hubverlauf (10) und ruhendem oder auch drehbar gelagertem Zylinder­ gehäuse (11) die Kraftstoffzufuhr für einen oder mehrere Zylinder (6) abgeschaltet wird, wobei die abgeschalteten Zylinder (6) möglichst zwischen noch arbeitenden Zylindern (6) liegen sollen, um dadurch von der im Expansionstakt gemeinsam benutzten heißen Zylinderdeckelzone Wärmeenergie in den Expan­ sionstakt der abgeschalteten Zylinder (6) zu übernehmen.The object is achieved in that the fuel supply for one or more cylinders ( 6 ) is switched off in economy or overrun mode with 4-stroke axial rotary piston engines with sinusoidal stroke ( 10 ) and stationary or rotatably mounted cylinder housing ( 11 ) , The switched-off cylinders ( 6 ) should lie between cylinders ( 6 ) that are still working, in order to thereby take over heat energy from the hot cylinder cover zone used jointly in the expansion cycle into the expansion cycle of the switched-off cylinders ( 6 ).

Die mit der Erfindung erzielten Vorteile bestehen darin, daß wenn Achsial-Kreiskolbenmotoren durch abwechselndes Abschalten einzelner Zylinder (6) im Sparbetrieb gefahren werden, diese abgeschalteten Zylinder (6) nicht nur Reibungs- und Leckgasverluste aufweisen, sondern die Aufnahme von Wärmeenergie aus der heißen Zylinderdeckelzone während des Expansions­ taktes diese Verluste überwiegen und so eine positive Energiebilanz bei den abgeschalteten Zylindern (6) erreicht wird.The advantages achieved by the invention are that when axial rotary piston motors are operated in economy mode by alternately switching off individual cylinders ( 6 ), these switched off cylinders ( 6 ) not only have friction and leakage gas losses, but also the absorption of thermal energy from the hot cylinder cover zone during the expansion cycle these losses predominate and a positive energy balance is achieved with the cylinders ( 6 ) switched off.

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt.An embodiment of the invention is in the Drawing shown.

Fig. 1 zeigt den typischen, qualitativen Temperatur­ verlauf an der Oberfläche des Zylinder­ deckels (1). Fig. 1 shows the typical, qualitative temperature profile on the surface of the cylinder cover ( 1 ).

Fig. 2 zeigt eine Zylinder-Teilkreis-Abwicklung mit einem ganzen Viertakt-Arbeitsspiel. Fig. 2 shows a cylinder pitch circle processing with a whole four-stroke cycle.

Im Unterschied zu herkömmlichen Hubkolbenmotoren haben Achsial-Kreiskolbenmotoren die Zylinderdeckel­ seite (1) nicht einem Zylinder (6) fest zugeordnet, sondern die Zylinder (6) bewegen sich relativ zum Zylinderdeckel (1). Sind die Zylinder (6) ruhend, so dreht sich der Zylinderdeckel (1) mit der Motorwelle und der Hubkurve (10). Kreisen dagegen die Zylinder (6), wie in Fig. 2 in Pfeilrichtung (8) dargestellt, während nun die Hubkurve (10) und der Zylinderdeckel (1) ruhend sind, so haben in beiden Fällen alle Kolben (7) zur Zylinderdeckelseite (1) hin keine feste Arbeitsraumwand mehr, wie bei den herkömmlichen Hubkolbenmotoren, sondern alle mit ihren Rollen (9) auf der Hubkurve (10) in sinusförmigem Hubverlauf geführten Kolben (7) in ihren Zylindern (6) benutzen nun für jeden Takt immer dieselbe Zylinderdeckelzone. Das heißt, jeder Zylinder (6) benutzt bei einem Umlauf für ein ganzes Arbeitsspiel immer beim Ansaugen denselben Einlaßkanal (2), dasselbe Einspritzventil (3), dieselbe Verdichtungszone mit derselben Zündkerze (4), die gleiche Expansionszone und schließlich zum Ausschieben denselben Auslaßkanal (5) wie alle anderen Kolben (7). Es stellt sich also an der Zylinderdeckelseite (1) nicht eine mittlere Temperatur zwischen einmal kalter Ansaugluft und dann wieder heißem Expansionsgas ein, sondern jede Zylinderdeckelzone hat ihren eigenen typischen Temperaturbereich.In contrast to conventional reciprocating piston engines, axial rotary piston engines do not permanently assign the cylinder cover side ( 1 ) to a cylinder ( 6 ), but the cylinders ( 6 ) move relative to the cylinder cover ( 1 ). If the cylinders ( 6 ) are stationary, the cylinder cover ( 1 ) rotates with the motor shaft and the lifting curve ( 10 ). If, on the other hand, the cylinders ( 6 ) circle as shown in Fig. 2 in the direction of the arrow ( 8 ) while the stroke curve ( 10 ) and the cylinder cover ( 1 ) are at rest, in both cases all pistons ( 7 ) have to the cylinder cover side ( 1 ) no longer a fixed working space wall, as with the conventional reciprocating piston engines, but instead all the pistons ( 7 ) in their cylinders ( 6 ) guided with their rollers ( 9 ) on the stroke curve ( 10 ) in a sinusoidal stroke now use the same cylinder cover zone for each cycle. This means that each cylinder ( 6 ) uses the same inlet channel ( 2 ), the same injection valve ( 3 ), the same compression zone with the same spark plug ( 4 ), the same expansion zone and finally the same outlet channel for pushing out for an entire work cycle. 5 ) like all other pistons ( 7 ). The cylinder cover side ( 1 ) therefore does not have an average temperature between cold intake air and then hot expansion gas, but each cylinder cover zone has its own typical temperature range.

Würde nun die Kraftstoffzufuhr am Einspritzventil (3) für alle Zylinder (6) unterbrochen (Schiebebetrieb), so ergäbe dies etwa den in Fig. 1 gestrichelt dargestellten Temperaturverlauf (b) mit einer Symmetrielinie in OT. Das heißt, alle Kolben (7) verdichten etwa mit demselben Polytropenexponenten mit dem sie dann auch wieder expandieren und es ergäbe sich kein thermischer Energiegewinn. Erhalten dagegen alle Zylinder (6) über das Einspritzventil (3) eine Kraftstoffzufuhr, so ergeben sich im Expansions- undIf the fuel supply at the injection valve ( 3 ) were now interrupted for all cylinders ( 6 ) (push operation), this would result in the temperature curve (b) shown in dashed lines in FIG. 1 with a symmetry line in TDC. This means that all pistons ( 7 ) compress with approximately the same polytropic exponent with which they then expand again and there would be no thermal energy gain. If, on the other hand, all cylinders ( 6 ) receive a fuel supply via the injection valve ( 3 ), the result is expansion and

Ausschiebe-Takt sehr heiße Zonen auf der Zylinderdeckelseite (1), etwa mit dem Temperaturverlauf nach Fig. 1 Kurve (a). Wenn nun aber nur bei einzelnen Zylindern (6), möglichst gleichmäßig verteilt und abwechselnd, die Kraftstoff­ zufuhr am Einspritzventil (3) unterbrochen wird, dann verdichten zwar alle Zylinder (6) noch mit demselben Temperaturverlauf, im Expansionstakt dagegen bekommen die abgeschalteten Zylinder (6) einen thermischen Energiebetrag von der heißen Expansionszone, welchen ihre zuvor vorbei gekommenen, mit Kraftstoffzufuhr arbeitenden Zylinder (6) dort abgegeben haben. Je nachdem wieviel Zylinder (6) abgeschaltet sind und wieviele noch Kraftstoffzufuhr bekommen, stellt sich ein näher bei Kurve (a) oder näher bei Kurve (b) liegender Temperaturverlauf ein.Exhaust cycle very hot zones on the cylinder cover side ( 1 ), approximately with the temperature profile according to Fig. 1 curve ( a ). If, however, the fuel supply to the injection valve ( 3 ) is interrupted only with individual cylinders ( 6 ), as evenly as possible and alternately, then all cylinders ( 6 ) still compress with the same temperature profile, while the deactivated cylinders ( 6 ) a thermal amount of energy from the hot expansion zone, which her previously passed, working with fuel supply cylinders ( 6 ) gave off there. Depending on how many cylinders ( 6 ) are switched off and how many are still being supplied with fuel, a temperature curve closer to curve ( a ) or closer to curve ( b ) is obtained.

Claims (1)

Energienutzung aus den Zylinderkopfwänden von Achsial- Kreiskolbenmotoren bei teilweise abgeschalteter Kraftstoffzufuhr, dadurch gekennzeichnet, daß im Spar- oder Schubbetrieb bei 4-Takt-Achsial- Kolbenmotoren mit sinusförmigem Hubverlauf (10) und ruhendem oder auch drehbar gelagertem Zylindergehäuse (11) die Kraftstoffzufuhr für einen oder mehrere Zylinder (6) an dem Einspritzventil (3) abgeschaltet wird, wobei die abgeschalteten Zylinder (6) möglichst zwischen noch arbeitenden Zylindern (6) liegen sollen, um dadurch über die im Expansionstakt gemeinsam benutzte Zylinderdeckel­ fläche (1) Wärmeenergie in den Expansionstakt der abgeschalteten Zylinder (6) zu übernehmen.Use of energy from the cylinder head walls of axial rotary piston engines with partially switched off fuel supply, characterized in that the fuel supply for one is in economy or overrun mode with 4-stroke axial piston engines with a sinusoidal stroke ( 10 ) and stationary or rotatably mounted cylinder housing ( 11 ) or more cylinders (6) is switched off to the injection valve (3), wherein the disabled cylinders (6) should be between more operating cylinders (6) as possible, thereby over the shared in the expansion stroke cylinder cover surface (1) heat energy in the expansion stroke the deactivated cylinder ( 6 ).
DE19883832134 1988-03-15 1988-09-22 Axial piston internal combustion engine Expired - Fee Related DE3832134C2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE19883832134 DE3832134C2 (en) 1988-03-15 1988-09-22 Axial piston internal combustion engine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19883808506 DE3808506A1 (en) 1987-03-28 1988-03-15 Axial-rotary piston engine with sinusoidal stroke path
DE19883832134 DE3832134C2 (en) 1988-03-15 1988-09-22 Axial piston internal combustion engine

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DE3832134A1 true DE3832134A1 (en) 1990-04-05
DE3832134C2 DE3832134C2 (en) 1998-08-27

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009024505B4 (en) * 2009-06-08 2013-07-25 Erwin Becker Reciprocating engine and method for operating a reciprocating engine
RU2506438C2 (en) * 2012-02-09 2014-02-10 Анатолий Андреевич Гах Crank-free variable-power rotary piston ice
DE102015001985A1 (en) 2015-02-14 2016-08-18 Benjamin-Elias Probst Double chamber five-stroke engine Sutur X

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE6806197U (en) * 1968-11-09 1970-08-13 Rudolf Maxein K G Maschb HYDRAULIC MOTOR.
EP0079750A1 (en) * 1981-11-12 1983-05-25 WALLER, Francis E. Parallel cylinder internal combustion engine
DE3408447A1 (en) * 1984-03-08 1985-09-12 Reinhold Dipl.-Hdl. 7590 Achern Starck Drive-shaft-controlled engine with sinusoidal power transmission surfaces
DE3711205A1 (en) * 1987-04-02 1988-10-20 Motos Motor Technik Gmbh Axial opposed piston type internal combustion engine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE6806197U (en) * 1968-11-09 1970-08-13 Rudolf Maxein K G Maschb HYDRAULIC MOTOR.
EP0079750A1 (en) * 1981-11-12 1983-05-25 WALLER, Francis E. Parallel cylinder internal combustion engine
DE3408447A1 (en) * 1984-03-08 1985-09-12 Reinhold Dipl.-Hdl. 7590 Achern Starck Drive-shaft-controlled engine with sinusoidal power transmission surfaces
DE3711205A1 (en) * 1987-04-02 1988-10-20 Motos Motor Technik Gmbh Axial opposed piston type internal combustion engine

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
MTZ 51 (1990) 2, 82-87 *
MTZ 54 (1993) 5, 240-246 *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009024505B4 (en) * 2009-06-08 2013-07-25 Erwin Becker Reciprocating engine and method for operating a reciprocating engine
RU2506438C2 (en) * 2012-02-09 2014-02-10 Анатолий Андреевич Гах Crank-free variable-power rotary piston ice
DE102015001985A1 (en) 2015-02-14 2016-08-18 Benjamin-Elias Probst Double chamber five-stroke engine Sutur X

Also Published As

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