EP0603961B1 - Kolbenbrennkraftmaschine mit beweglichem Zylinderkopf - Google Patents

Kolbenbrennkraftmaschine mit beweglichem Zylinderkopf Download PDF

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Publication number
EP0603961B1
EP0603961B1 EP93203576A EP93203576A EP0603961B1 EP 0603961 B1 EP0603961 B1 EP 0603961B1 EP 93203576 A EP93203576 A EP 93203576A EP 93203576 A EP93203576 A EP 93203576A EP 0603961 B1 EP0603961 B1 EP 0603961B1
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EP
European Patent Office
Prior art keywords
piston
cylinder
stroke
induction
elastic means
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP93203576A
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English (en)
French (fr)
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EP0603961A1 (de
Inventor
Ivo Demi
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.)
Malanima Giovanni
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Malanima Giovanni
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Publication date
Application filed by Malanima Giovanni filed Critical Malanima Giovanni
Publication of EP0603961A1 publication Critical patent/EP0603961A1/de
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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
    • F02B75/00—Other engines
    • F02B75/36—Engines with parts of combustion- or working-chamber walls resiliently yielding under pressure
    • F02B75/38—Reciprocating - piston 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
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • F02B75/041—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of cylinder or cylinderhead positioning
    • F02B75/042—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of cylinder or cylinderhead positioning the cylinderhead comprising a counter-piston
    • 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
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/14—Direct injection into combustion chamber
    • 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
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the present invention relates to a reciprocating internal combustion engine with a head structured so as to exploit to best advantage the energy produced by the combustion of an air and fuel mixture.
  • reciprocating internal combustion engines comprise essentially a cylinder block provided with one or more cylinders, a head fastened to the cylinder block, one or more pistons, each sealingly sliding in a corresponding cylinder to execute a given two- or four-stroke working cycle, Otto or Diesel; each piston, together with the head, defines a combustion chamber and is operatively connected to a crank-shaft through a kinematic mechanism with a connecting rod and a crank.
  • the head is fastened to the cylinder block by means of bolts, with the interposition of sealing gaskets.
  • Reciprocating engines have also been developed without a fixed head, wherein two opposed cylinders are sliding in opposite directions in just one cylinder to execute a given working cycle; the two pistons define a combustion chamber between them and are operatively connected to a common crank-shaft by means of respective kinematic mechanisms.
  • DE-C-259168 discloses an i.c. engine with a partially movable head formed by a specially designed piston, which provides an original timing system for opening and closing induction and exhaust ports.
  • DE-A-3130767 discloses an i.c. engine with a movable head which permits to change the compression ratio and to smooth the pressure peaks of the cycle.
  • EP-A-0488431 discloses an i.c. engine with a head formed by a mobile supplementary piston with the function of varying the volume of the combustion chamber to control the compression and ignition pressure. Said mobile supplementary piston is kept against a fixed stop of a cylinder by the action of a spring. During the engine working cycle, strong impacts of the supplementary piston against said fixed stop of the cylinder occur and cause high noise and breaking of the parts coming into contact.
  • the object of the present invention is a reciprocating internal combustion engine that allows to match the following targets:
  • a pressure peak occurs in the combustion chamber that is in part absorbed by the elastic means in engagement with the elastically yielding head; in this way, the accumulated energy can be returned during the subsequent expansion stage and can possibly be used to accomplish a better exhaust of burnt gases produced by the combustion.
  • the energy absorbed by the elastic means during the combustion stage allows a decrease in the value of the maximum pressure in the combustion chamber, with a consequent reduction of stresses on the elements of the engine.
  • the subsequent recovery, during the expansion stage and the additional downward stroke, of the energy accumulated by the elastic means allows the power delivered by the engine to remain at a substantially unchanged level and a better evacuation of the exhaust gases from the cylinder to be accomplished, in favour of a better filling of the same cylinder in the subsequent induction stage and of a more complete combustion, with the consequent reduction of polluting agents in the engine's exhaust gases.
  • the slight depression caused in the combustion chamber by an additional upward return stroke of the further piston after the additional downward stroke allows the fuel mixture to fill the combustion chamber without being discharged through an exhaust duct, thereby reducing or annulling the fuel losses usually involved with the discharge of the exhaust gas.
  • the engine according to the invention allows the following advantageous results:
  • FIG. 1 an air-cooled, Otto cycle, single-cylinder reciprocating internal combustion engine; the engine is provided with a cylinder block, indicated as a whole with 1, provided with cooling fins 2. There is indicated with 3 a liner forming a cylinder 4 and there is indicated with 5 a main piston provided with gas rings 48, sealingly sliding in the cylinder 4.
  • an elastically yielding head formed by a further piston 8, provided with gas rings 40, that slides sealingly in the same cylinder 4 of the liner 3.
  • the piston 8 is opposed to the piston 5 and in the position corresponding to its lower end of stroke, shown in Fig. 1, it defines with the piston 5 a combustion chamber indicated with 9.
  • the piston 8, also visible in Fig. 3, is provided with a shoulder 10 and with a threaded pin 11 to which a flange 13 is fastened by means of nuts 12.
  • the flange 13 is provided with holes 14 in which there are inserted guide rods 15, that have heads 16 fastened to the base 1 by means of bolts 17.
  • the pre-loads of the springs 18 and 25 are selected so that they balance one another, keeping flange 13 and piston 8 in the selected position of lower end of stroke, as shown in Fig. 1, until the pressure in the combustion chamber 9 does not overcome the pre-load of the springs 25.
  • an ignition spark plug screwed into a threaded hole 33 of the further piston 8 and connected, by means of a conductor 34 and a sliding contact 35, to a known ignition current generator, not shown.
  • Conductor 34 and contact 35 are supported by a cap 36, fastened to the plate 30.
  • FIG. 1 There are not shown in Fig. 1 usual induction and exhaust ports, operated by the piston 5, by means of which a mixture of air and fuel is fed to the cylinder 4 and the burnt gases generated by the combustion of the mixture in the chamber 9 are discharged. These ports are shown in Fig. 4, where they are indicated with 37 and 38, respectively.
  • FIG. 7 The operation of the engine shown in Figs. 1-3 shall now be illustrated with reference to Fig. 4, through five diagrammmatic representations marked A, B, C, D, E, wherein there are shown the positions assumed by the different elements in the successive stages of a working cycle, that, as previously said, is a two-stroke Otto cycle, represented in Fig. 7.
  • A the engine during the mixture compression stage, with the piston 5 moving upward toward T.D.C. (top dead center) and the piston 8 in the position of lower end of stroke (step 1-2 of Fig. 7).
  • B the engine after ignition, during the mixture's combustion stage, with the piston 5 at the T.D.C. and the piston 8 having moved to the position of upper end of stroke, compressing the springs 25 (step 2-3 of Fig. 7 and dashed-and-dotted line 70, that shows the change in volume due to the displacement of the piston 8).
  • combustion can be represented by a succession of infinitesimal steps at constant volume, at progressively increasing levels, interspaced by a lot of infinitesimal steps at constant temperature, at progressively increasing levels, as shown in Fig. 8, wherein the dashed lines 71 represent the steps at constant volume (isochors) and the dashed lines 72 represent the steps at constant temperature (isotherms).
  • C the engine during the expansion stroke, with the piston 5 moving downward toward B.D.C. (bottom dead centre) and the piston 8 being urged by the springs 25 toward the position of lower end of stroke (steps 3-4 and 4-5 of Fig. 7).
  • step 3-4 of Fig. 7 the engine during the exhaust and scavenging stage (step 5-1 of Fig. 7), with the piston 5 at B.D.C., the induction port 37 and exhaust port 38 simultaneously open, and the piston 8 urged by the springs 25, due to the accumulated energy, to execute an additional downward stroke below the position of lower end of stroke, so as to contribute to the exhaust of burnt gases and to the scavenging of the cylinder 4 with fresh mixture.
  • E the engine during the mixture's induction and compression stroke, with the piston 5 returning towards T.D.C.
  • the elastically yielding head 7 absorbs energy during the combustion stage, with the advantage of lowering the value of the maximum pressure in the combustion chamber 9 and of reducing the stresses to which the engine's elements are subjected.
  • the energy accumulated by the head 7 is recovered in the subsequent expansion stroke, allowing the energy delivered by the engine to remain substantially unchanged.
  • the head 7 exerts a thrust action on the burnt gases and encourages their evacuation from the cylinder 4, while, during the execution of the additional return stroke, it generates a depression in the cylinder that causes a larger quantity of mixture to flow into it; as a consequence, there are both a better filling and a more complete combustion, together with a reduction of polluting elements in the engine's exhaust gases.
  • Fig. 5 an Otto cycle, four-stroke single-cylinder reciprocating internal combustion engine; the engine is provided with a cylinder block, of the type cooled with water, indicated as a whole with 50, provided with chambers 51 containing the cooling water; there is indicated with 52 a cylinder, obtained directly in the block 50, in which there sealingly slides a main piston 53, represented in the position corresponding to its T.D.C., operatively connected to a crank-shaft 6, as shown diagrammatically in Fig. 6.
  • a return-action spring connected to the piston 55 and to a plate 59 provided with a threaded stem 60, by means of which it is screwed onto a cover 61, fastened to the base 50.
  • a spring placed between the piston 55 and the plate 59. The lower end-of-stroke position of the piston 55 is adjusted with the threaded stem 60.
  • Fig. 6 The operation of the engine of Fig. 5 is illustrated in Fig. 6, through six diagrammatic representations, marked F, G, H, I, L, M, wherein there are illustrated the stages of a working cycle, that, as has been said, is a four-stroke Otto cycle.
  • F the engine during the mixture induction stroke, with the port 62 open, the piston 53 moving downwards toward B.D.C., and the piston 55 in the position of lower end of stroke.
  • G an engine at the end of the compression stroke, at the moment of ignition and when the mixture starts to burn.
  • H the engine during the mixture combustion stage, with the piston 53 at T.D.C. and the piston 55 that has moved to the position of upper end of stroke, compressing the spring 58.
  • I the engine during the expansion stroke, with the piston 53 that moves downwards toward B.D.C. and the piston 55 that is urged by the spring 58 to the position of lower end of stroke.
  • L the engine at the end of the expansion stroke, with the piston 53 near B.D.C. and the piston 55 urged by the spring 58, due to the accumulated energy, to execute an additional downward stroke below the position of lower end of stroke, so as to return part of the elastic energy.
  • M the engine during the exhaust stroke, with the exhaust port 63 open, the piston 53 that is moving upward again toward T.D.C. and the piston 55 that, under the action of the spring 57, is returned to the position of lower end of stroke, executing an additional return stroke.
  • the engines described can be fed with usual systems, by means of carburettors, indirect injection systems (with a fuel injector located in an air-intake duct), direct injection systems (with a fuel injector located in the combustion chamber), may be of the induction or supercharged type and may operate on Otto or Diesel cycle.
  • the engines according to the invention are capable of absorbing part of the energy generated during combustion, and are thus also suitable for utilizing "energetic" fuels, that involve faster and more intense combustions than those with traditional petrol and fuel-oil; for example Diesel-cycle engines with elastically yielding heads can be fed with mixtures of fuel-oil and petrol.

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  • 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)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Valve Device For Special Equipments (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Stored Programmes (AREA)

Claims (5)

  1. Hubkolben-Verbrennungsmaschine, die
    einen Zylinderblock (1; 50), der mindestens einen Zylinder (4; 52), der mit einem Einlaßkanal (37; 62) und einem Auslaßkanal (68; 63) vorgesehen ist, aufweist,
    mindestens einen Arbeitskolben (5; 53), der betreibbar mit einer Kurbelwelle (6) verbunden ist und dichtend in dem Zylinder (4; 52) gleitet, um einen gegebenen Arbeitszyklus auszuführen, der eine Abfolge von Einlaß-, Verdichtungs- und Verbrennungsstufen gefolgt durch eine Expansionsstufe, die einen Expansionstakt des Arbeitskolbens (5; 53) beinhaltet, aufweist, und
    einen Kopf (7; 54), der mit dem Zylinder (4; 52) zum Definieren einer Verbrennungskammer (9, 56) verbunden ist, aufweist, wobei der Kopf (7; 54) an dem Zylinderblock (1; 50) in einer elastisch nachgebenden Weise befestigt ist und durch mindestens einen weiteren Kolben (8; 55) gebildet wird, der in dem zylinder (4; 52) dichtend gleitet, dem Arbeitskolben (5; 53) gegenüber liegt und der Wirkung eines ersten elastischen Mittels (25; 58), das den weiteren Kolben (8; 55) in einer Ruheposition während der Verdichtungsstufe hält, unterworfen ist, wobei ein zweites elastisches Mittel (18; 57) vorgesehen ist, um einen zusätzlichen Abwärtshub des weiteren Kolbens (8; 55) unter die Ruheposition an dem Ende des Expansionstaktes des Arbeitskolbens (5; 53) zu ermöglichen und zu begrenzen, wobei das zweite elastische Mittel (18; 57) eine elastische Kraft aufweist, die die elastischen Kraft des ersten elastischen Mittels (25; 58) ausgleicht, um den weiteren Kolben (8; 53) im wesentlichen in die Ruheposition an dem Ende des Expansionstaktes des Arbeitskolbens (5; 53) zurückzubringen und zu halten, dadurch gekennzeichnet,
    daß das erste (25; 58) und das zweite (18; 57) elastische Mittel vorgespannte Federn mit gegenseitig entgegengesetzten, ausgleichenden Vorspannwerten sind und daß der Einlaßkanal (37; 52) und der Auslaßkanal (38; 63) unterhalb des weiteren Kolbens (8; 55) in der Ruheposition derart angeordnet sind, daß sie Öffnungs- und Schließzeiten, die die direkt durch den Arbeitskolben (5; 53) gesteuert werden, während der Einlaß-, Verdichtungs-, Verbrennungs- und Expansionsstufen aufweisen.
  2. Maschine nach Anspruch 1, dadurch gekennzeichnet, daß der weitere Kolben (8) mit einem Flansch (13) vorgesehen ist, der gleitend in Eingriff mit einem Führungsmittel (15, 19, 21), das an dem Zylinderblock (1) befestigt ist, ist und Abstützungen für das erste und das zweite elastische Mittel (25, 18) bildet.
  3. Maschine nach Anspruch 1, dadurch gekennzeichnet, daß das erste und das zweite elastische Mittel (57, 58) zwischen dem weiteren Kolben (55) und einer Platte (59), die mit einem Gewindestiel (60), der an eine Abdeckung (61), die an dem Block (50) befestigt ist, geschraubt ist, vorgesehen ist, angeordnet sind.
  4. Maschine nach Anspruch 1, dadurch gekennzeichnet, daß der Zylinderblock (1) mit Einlaßkanälen (37) und Auslaßkanälen (38) für einen Zweitakt-Arbeitszyklus vorgesehen ist.
  5. Maschine nach Anspruch 1, dadurch gekennzeichnet, daß der Block (52) mit Einlaßkanälen (62) und Auslaßkanälen (63) für einen Viertakt-Arbeitszyklus vorgesehen ist.
EP93203576A 1992-12-23 1993-12-17 Kolbenbrennkraftmaschine mit beweglichem Zylinderkopf Expired - Lifetime EP0603961B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITMI922935A IT1256224B (it) 1992-12-23 1992-12-23 Motore a combustione interna alternativo a testata mobile
ITMI922935 1992-12-23

Publications (2)

Publication Number Publication Date
EP0603961A1 EP0603961A1 (de) 1994-06-29
EP0603961B1 true EP0603961B1 (de) 1997-03-19

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Application Number Title Priority Date Filing Date
EP93203576A Expired - Lifetime EP0603961B1 (de) 1992-12-23 1993-12-17 Kolbenbrennkraftmaschine mit beweglichem Zylinderkopf

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EP (1) EP0603961B1 (de)
AT (1) ATE150523T1 (de)
DE (1) DE69309020D1 (de)
IT (1) IT1256224B (de)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29613109U1 (de) * 1996-07-18 1997-11-13 Pollerhoff, Holger, 45279 Essen Kolben mit Eigenoszillation für Verbrennungskraftmaschinen
US6622667B1 (en) * 2000-07-25 2003-09-23 Deltahawk, Inc. Internal combustion engine
JP5677858B2 (ja) 2008-02-28 2015-02-25 ダグラス ケイ ファー 高効率内爆エンジン

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE342230A (de) *
DE3130767A1 (de) * 1981-02-19 1983-04-28 Ulrich 2000 Norderstedt Becker Zweitakt-brennkraftmaschine mit veraenderlichem verdichtungsraum und veraenderlichem hubraum
IT1243259B (it) * 1990-11-08 1994-05-26 Giuseppe Mignone Motore endotermico a pressione di compressione costante a tutti i regimi di giri, a pressione di scoppio controllata a tutti i regimi di giri, a camera di scoppio variabile

Also Published As

Publication number Publication date
EP0603961A1 (de) 1994-06-29
ATE150523T1 (de) 1997-04-15
DE69309020D1 (de) 1997-04-24
ITMI922935A0 (it) 1992-12-23
IT1256224B (it) 1995-11-29
ITMI922935A1 (it) 1994-06-23

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