WO2014063811A1 - Procédé pour faire fonctionner un moteur à combustion interne à deux temps, moteur à combustion interne à deux temps à balayage longitudinal ainsi que moteur à combustion interne à deux temps à balayage longitudinal chargé et récupérateur - Google Patents

Procédé pour faire fonctionner un moteur à combustion interne à deux temps, moteur à combustion interne à deux temps à balayage longitudinal ainsi que moteur à combustion interne à deux temps à balayage longitudinal chargé et récupérateur Download PDF

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Publication number
WO2014063811A1
WO2014063811A1 PCT/EP2013/003180 EP2013003180W WO2014063811A1 WO 2014063811 A1 WO2014063811 A1 WO 2014063811A1 EP 2013003180 W EP2013003180 W EP 2013003180W WO 2014063811 A1 WO2014063811 A1 WO 2014063811A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
recuperator
working chamber
tdc
internal combustion
Prior art date
Application number
PCT/EP2013/003180
Other languages
German (de)
English (en)
Inventor
Peter Kreuter
Original Assignee
Peter Kreuter
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Peter Kreuter filed Critical Peter Kreuter
Publication of WO2014063811A1 publication Critical patent/WO2014063811A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
    • F02B41/02—Engines with prolonged expansion
    • F02B41/04—Engines with prolonged expansion in main cylinders
    • 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
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • 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
    • F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
    • F02B25/02—Engines characterised by using fresh charge for scavenging cylinders using unidirectional scavenging
    • F02B25/04—Engines having ports both in cylinder head and in cylinder wall near bottom of piston stroke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/053—Component parts or details
    • F02G1/057—Regenerators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F02G5/02—Profiting from waste heat of exhaust gases
    • 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

Definitions

  • the invention relates to a method for operating a supercharged, longitudinally-flushed two-stroke internal combustion engine and a supercharged, longitudinally-flushed two-stroke internal combustion engine. which works by the method according to the invention.
  • the invention further relates to a recuperator for such an internal combustion engine.
  • Two-stroke internal combustion engines are gaining in importance against the background of the need to reduce fuel consumption. Characterized in that the rotational angle of the crankshaft of two-stroke engine between two power strokes is half the angle of rotation of a four-stroke internal combustion engine with the same number of cylinders have two-stroke internal combustion engines high potential for downsizing, for example by reducing the number of cylinders.
  • the invention has for its object to improve the efficiency of two-stroke internal combustion engines.
  • Claim 2 is directed to a two-stroke internal combustion engine, which operates according to the inventive method.
  • Claim 5 is directed to a recuperator for use in an internal combustion engine according to the invention.
  • the invention which can be used for two-stroke internal combustion engines of different sizes and powers, self-igniting or spark-ignited, fueled with gasoline, diesel, fuel or gas, is explained below with reference to schematic drawings, for example and with further details.
  • FIG. 1 is a schematic view of parts of a piston / cylinder unit of a two-stroke internal combustion engine according to the invention
  • Fig. 2 is a perspective view of a recuperator
  • Figures 3 to 6 are side views of the piston / cylinder unit in different operating positions to explain the function of the internal combustion engine according to the invention.
  • a two-stroke internal combustion engine in the illustrated example a diesel internal combustion engine, has at least one cylinder 10 in which a piston 12 formed with a combustion bowl 11 is movable up and down in the axial direction of the cylinder.
  • the piston 12 is connected to a crankshaft not shown in FIG. 1 via a connecting rod 14.
  • the piston 12 is approximately in its lowest position, d. H. its bottom dead center (UT), in which it in the cylinder wall formed passages, such as inlet slots 16, releases, which connect an annular space 18 surrounding the cylinder 10 with a working chamber 20 in the interior of the cylinder 10.
  • the working chamber 20 is limited as shown in FIG. 1 down from the piston 12 and upwardly from a cylinder head 22.
  • at least one outlet opening is formed, which is closable with an outlet valve 24 and from which an outlet channel 26 leads to the outside.
  • a recess or pocket 30 is formed in the cylinder head 22, whose diameter is equal to the diameter of the working chamber 20 and which extends the working chamber 20 of FIG. 1 upwards.
  • the outlet opening which is closable with the outlet valve 24, is formed in the bottom wall 32 of the pocket 30 which closes the working chamber 20 upwards.
  • an annular groove is formed, via which the bottom wall 32 merges into a Ringansharm 36, the Working chamber 20 projects out.
  • a recuperator 40 is arranged, the outer diameter of which is equal to or at most slightly smaller than the inner diameter of the working chamber 20.
  • the recuperator 40 has a main body 42 of heat-resistant material, for example heat-resistant steel, with advantageously high thermal conductivity and high specific heat.
  • the main body 42 is formed by a disc having a circular outer contour, which is provided with throughflow openings 44, for example through holes, which pass axially through the main body 42.
  • the thickness of the main body 42 is about 5 mm and are the through holes 44 with a diameter of about 1 mm, for example, and an areal density of, for example, about 25 / cm 2 , the stated values being in no way restrictive.
  • the base body 42 In its middle region, the base body 42 has a collar 46, which encloses a central through-opening 48.
  • a shaft 50 is rigidly fixed, which is similar to a shaft of the exhaust valve 24 passed through the cylinder head 22 with sealing linearly movable. Similar to the way in which the outlet valve 24 can be actuated by means of an outlet cam 52 in a manner known per se, the recuperator 40 is linearly reciprocatable by means of a recuperator cam 54.
  • the dimensioning of the collar 46 is such that the collar 46 at least substantially fluid-tightly surrounds the annular shoulder 36 of the cylinder head 22 and can be moved into the annular groove 34.
  • the collar 46, the annular shoulder 36 and the annular groove 34 thus form sealing means which at least largely prevent fluid passage through the passage opening 48.
  • the annular space 18 is connected to an inlet channel 60, wherein for controlling the connection between the inlet channel 60 and the annular space 18, for example, an annular slide valve is provided, the annular slide is designated in Fig. 1 with 62.
  • the annular slide 62 is rotatable in the example shown by means of its own drive or by the crankshaft of the internal combustion engine, not shown, in the clockwise direction, so that an inlet opening 64 of the annular slide 62 with the annular space 18 in alignment or the connection between the inlet channel 60 and the annular space 18 can be arranged occlusive.
  • the function of a longitudinally purged two-stroke engine is known per se and will not be explained in detail here.
  • the compressed air is supplied to the inlet channel 60 via a compressor device, not shown, compressed air.
  • the compressor device may include, for example, an exhaust gas turbocharger and / or a loader driven by the crankshaft or its own drive.
  • FIG. 3 shows the piston 12 in its BDC, in which the piston 12 releases the inlet slots 16, so that fresh charge, for example compressed fresh air, flows into the working chamber 20 at the bottom.
  • the exhaust valve 24 is open at this time and the recuperator 40 is located a short distance from the exhaust valve 24 in its BDC, ie its lowermost position in which the collar 46 slightly overlaps the collar 36.
  • the inlet opening 64 of the annular slide 62 releases the connection from the inlet channel 60 to the annular space 18.
  • the compressed, flowing in through the inlet slots 16 into the working chamber 20 fresh charge displaces the burnt during the previous working or expansion stroke charge from the working chamber 20, the burned charge through the through holes 44 of the recuperator 40 therethrough and the open r exhaust valve 24 and into the outlet channel 26 flows.
  • the working chamber 20 is rinsed.
  • the hot burned charge can leave the working chamber 20 only through the recuperator 40, since the collar 46 overlaps the annular shoulder 36 and the outer contour of the recuperator 40 largely coincides with the outer circumference of the working chamber 20. On in this way, the burnt charge transfers thermal energy contained in it to the recuperator 40, which is heated up.
  • the recuperator 40 is moved with further rotation of the Rekuperatornockens 54 from its UT according to Figures 3 and 4 in its TDC, in which the recuperator 40 at least approximately in contact with the bottom wall 32 of the bag 30 and the closed Exhaust valve 24 is located .. In this case, the collar 46 dips into the annular groove 34. The part of the compressed fresh charge located between the recuperator 40 and the bottom wall 32 is forced through the recuperator 40 back into the remaining space of the working chamber 20 or into the combustion bowl 11 of the piston 12, wherein the fresh charge continues to receive thermal energy from the recuperator 40.
  • Injection nozzle 38 is injected into the combustion chamber trough 11, so that the combustion of the fresh charge begins and the piston 12 moves under work output from its TDC in the direction UT (Fig. 6).
  • the outlet valve 24 remains closed.
  • the recuperator 40 may initially remain in its TDC and then moves out of the pocket 30 into its BDC before the piston 12 reaches its BDC.
  • the exhaust valve 24 is opened.
  • the rotary valve moves to a position in which it releases the connection to the annular space 18, so that the positions of FIG. 3 are reached again and the cycle starts again.
  • the stroke of the recuperator 40 is small compared to that of the piston 12 and is for example 20%, advantageously 15%, more preferably only 10% of the piston stroke.
  • the exhaust valve 24 is only relatively short open during the phase during which the piston 12 releases the inlet slots 16.
  • the opening of the exhaust valve 24 already begin before the piston reaches the inlet slots and / or end after the piston has crossed the inlet slots on its way to the OT.
  • the recuperator 40 remains relatively long in its UT, i. H. spaced from the bottom wall 32 and abuts the bottom wall only in the phase in which the piston is in its TDC and moves out of the TDC.
  • the recuperator can be formed in different ways and, for example, provided with a plurality of passing through the cylinder head shafts 50. It is advantageous for the function of the recuperator that the burned charge leaving the working chamber 20 flows as completely as possible through the recuperator into the outlet of the internal combustion engine and effectively heats the recuperator, which has a sufficiently high heat energy storage capacity. Further, it is advantageous if the fresh charge in its compression flows through the recuperator first completely from the piston side to the side facing away from the piston and flows back before reaching the TDC of the piston from the side facing away from the piston side of the recuperator 40 to the side of the piston 12 back.
  • the heat-storing region of the recuperator and its flow through can be designed in many different ways.
  • a collar In the central region of the recuperator, through which the injection nozzle 38 protrudes, a collar does not necessarily have to be formed.
  • the recuperator can abut directly on the outer circumference of a correspondingly designed injection nozzle 38 and be movable along this outer circumference.
  • the formation of a pocket in the cylinder head, the annular groove, the annular shoulder or the collar is not mandatory.
  • the exhaust cam (s) 52 and the recuperator cam (s) 54 may be actuated by a common camshaft driven by the crankshaft. It is advantageous if the exhaust cam or the exhaust cam can be ordered in phase relative to the crankshaft.
  • the inlet controlling rotary valve 62 can also be driven from the crankshaft ago, wherein the phase control of the rotary valve 62 is variable relative to the crankshaft for power control.
  • the rotary valve can also be rotationally driven by its own drive, such as an electric motor.
  • the rotary valve may be replaced by other suitable valves.
  • the injection nozzle 38 is replaced by a spark plug.
  • an injection nozzle may additionally be present. With external mixture formation of the fresh air is already flow above the inlet slots 16 fuel added.
  • a compression-determining distance may remain in the TDC of the piston between the piston top and the bottom of the recuperator.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

L'invention concerne un procédé pour faire fonctionner un moteur à combustion interne à deux temps à balayage longitudinal, chargé, présentant au moins un piston (12) animé d'un mouvement de va-et-vient dans un cylindre (10) entre un point mort supérieur (OT) et un point mort inférieur (UT) comprenant les étapes suivantes : alimentation de charge fraîche dans une zone inférieure d'une chambre de travail (20) du cylindre (10) pendant que le piston (12) se trouve dans sa position UT, évacuation de la charge brûlée de la zone supérieure de la chambre de travail (20), compression de la charge fraîche par le mouvement du piston (12) de la position UT vers la position OT, inflammation de la charge fraîche comprimée lorsque le piston (12) se trouve dans sa position OT et combustion de la charge fraîche au moins pendant le début du mouvement du piston de sa position OT vers sa position UT. Selon l'invention, un récupérateur (40) disposé dans la chambre de travail entre le piston et une tête de cylindre (22) est déplacé de manière telle que la charge brûlée, avant d'être poussée hors de la chambre de travail (20), s'écoule au travers du récupérateur (40) éloigné de la tête de cylindre (22), puis au moins une partie de la charge fraîche s'écoule au travers du récupérateur (40) pendant le mouvement du piston (12) hors d'une position UT puis, avant que le piston (12) n'atteigne sa position OT, s'écoule à nouveau au travers du récupérateur (40) à partir de côté opposé au piston (12) vers le côté face au piston en approchant le récupérateur (40) de la tête de cylindre (12).
PCT/EP2013/003180 2012-10-24 2013-10-22 Procédé pour faire fonctionner un moteur à combustion interne à deux temps, moteur à combustion interne à deux temps à balayage longitudinal ainsi que moteur à combustion interne à deux temps à balayage longitudinal chargé et récupérateur WO2014063811A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012020893.6 2012-10-24
DE102012020893.6A DE102012020893B4 (de) 2012-10-24 2012-10-24 Verfahren zum Betreiben einer aufgeladenen, längsgespülten Zweitaktbrennkraftmaschine sowie aufgeladene, längsgespülte Zweitaktbrennkraftmaschine und Rekuperator

Publications (1)

Publication Number Publication Date
WO2014063811A1 true WO2014063811A1 (fr) 2014-05-01

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PCT/EP2013/003180 WO2014063811A1 (fr) 2012-10-24 2013-10-22 Procédé pour faire fonctionner un moteur à combustion interne à deux temps, moteur à combustion interne à deux temps à balayage longitudinal ainsi que moteur à combustion interne à deux temps à balayage longitudinal chargé et récupérateur

Country Status (2)

Country Link
DE (1) DE102012020893B4 (fr)
WO (1) WO2014063811A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020245854A1 (fr) * 2019-06-04 2020-12-10 Fioretti Salvatore Unité de service à "piston asservi" synchrone à deux temps avec anneau flottant pour moteurs endothermiques
CZ308792B6 (cs) * 2020-04-01 2021-05-19 Marek Ing. Žák Dvoudobý spalovací motor

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4280468A (en) * 1980-02-11 1981-07-28 Millman Mitchell W Regenerative reciprocating open cycle internal combustion engine
US4790284A (en) * 1985-10-02 1988-12-13 Regenic Corporation Regenerative internal combustion engine
US4928658A (en) * 1985-10-02 1990-05-29 Ferrenberg Allan J Regenerative internal combustion engine
WO1995033133A1 (fr) * 1994-05-27 1995-12-07 Caterpillar Inc. Amelioration de la course de chauffe d'un moteur a recuperateur

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT410699B (de) * 1997-08-25 2003-06-25 Bernhard Dipl Ing Feistritzer Arbeitsverfahren einer brennkraftmaschine und brennkraftmaschine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4280468A (en) * 1980-02-11 1981-07-28 Millman Mitchell W Regenerative reciprocating open cycle internal combustion engine
US4790284A (en) * 1985-10-02 1988-12-13 Regenic Corporation Regenerative internal combustion engine
US4928658A (en) * 1985-10-02 1990-05-29 Ferrenberg Allan J Regenerative internal combustion engine
WO1995033133A1 (fr) * 1994-05-27 1995-12-07 Caterpillar Inc. Amelioration de la course de chauffe d'un moteur a recuperateur

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020245854A1 (fr) * 2019-06-04 2020-12-10 Fioretti Salvatore Unité de service à "piston asservi" synchrone à deux temps avec anneau flottant pour moteurs endothermiques
CZ308792B6 (cs) * 2020-04-01 2021-05-19 Marek Ing. Žák Dvoudobý spalovací motor

Also Published As

Publication number Publication date
DE102012020893B4 (de) 2018-07-12
DE102012020893A1 (de) 2014-04-24

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