US3738332A - Compression-ignition engine - Google Patents

Compression-ignition engine Download PDF

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Publication number
US3738332A
US3738332A US00132381A US3738332DA US3738332A US 3738332 A US3738332 A US 3738332A US 00132381 A US00132381 A US 00132381A US 3738332D A US3738332D A US 3738332DA US 3738332 A US3738332 A US 3738332A
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US
United States
Prior art keywords
protrusion
piston
transfer passageway
expressed
engine
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Expired - Lifetime
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US00132381A
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English (en)
Inventor
C Stephant
J Ghersi
P Eyzat
A Ecomard
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INS FRANCAIS DU PETROLE DES CO
INS FRANCAIS DU PETROLE DES CORBURANTS ET LUBRIFIANTS FR
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INS FRANCAIS DU PETROLE DES CO
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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
    • F02B19/00—Engines characterised by precombustion chambers
    • F02B19/02—Engines characterised by precombustion chambers the chamber being periodically isolated from its cylinder
    • F02B19/04—Engines characterised by precombustion chambers the chamber being periodically isolated from its cylinder the isolation being effected by a protuberance on piston or cylinder head
    • 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
    • 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

  • ABSTRACT Compression ignition engine comprising a prechamber g" Appllcatlon Priority Data communicating with the cylinder through a transfer Apr. 15,1970 France 7013719 passageway whose smallest diameter is 0.6 D, D
  • One of the suggested solutions consists in performing the complete combustion in a chamber separate from the cylinder and of transferring to the latter, under a substantially constant pressure, the gases issued from the separate combustion chamber.
  • an engine according to this invention can be operated so as to provide the same mean effective pressure (M.E.P.) close to 16 atmospheres, as a direct injection engine of conventional type, i.e., with the same cylinder bore diameter, to produce the same power as said engine, with a maximum pressure in the combustion chamber of only about 100 atmospheres instead of about atmospheres in the conventional engine, which considerably reduces the stresses to which are subjected the walls of the combustion chamber and therefore makes possible a lightening of the engine construction and a cost reduction.
  • M.E.P. mean effective pressure
  • a compression-ignition engine having at least one cylinder, the bottom of which includes a prechamber in communication with the cylinder through a transfer passageway, the piston of the engine being provided with a protrusion adapted to penetrate the transfer passageway towards the end of the compression stroke, a fuel injector opening into the prechamber and directing the fuel jet towards the passageway, and wherein the combination of the following elements provides for a combustion at substantially constant pressure in the cylinder:
  • the transfer passageway opens into the prechamber through an opening whose smallest diameter, expressed in millimeters, is at most equal to 0.6 D D being the diameter expressed in millimeters, of the cylinder bore,
  • the height of the protrusion is so determined that, during the downward stroke of the piston, the flow section left free for the flow of gases, between the protrusion and the lower edge of the transfer passageway becomes equal to the minimum section with which the transfer passageway opens into the precombustion chamber, when the crankshaft has rotated from the piston top dead center position through an angle expressed in degrees of crankshaft rotation corresponding to between one half the duration of injection at full load and the whole of said duration.
  • FIG. 1 is a partial cross-section of the upper part of an engine cylinder according to the invention
  • FIG. 2 is an enlarged partial view of the engine of FIG. 1, showing the construction parameters involved,
  • FIGS. 2A, 2B and 2C are enlarged partial views similar to FIG. 2 and showing the positioning of the piston protrusion at various stages of engine operation
  • FIG. 3 shows, by way of comparison, three curves representing the progress of the combustion respectively in a direct injection conventional engine, in an engine according to this invention and in an ideal engine wherein the combustion would be performed at constant pressure.
  • reference 1 indicates a cylinder of an engine, 2 a cylinder head, 3 and 4 respectively the inlet valve for the air used as combustion-sustaining agent and the exhaust valve.
  • a prechamber 5 communicating with the cylinder through a transfer passageway 6 leaving free for the gases a passage whose section is defined by the bore section of an insert member 6a.
  • Piston 7 is provided at its upper part with a protrusion adapted to penetrate the transfer passageway towards the end of the compression stroke.
  • the protrusion 8 has a substantially cylindrical shape but it would not be out of the scope of the invention to give to this protrusion a slightly frusto-conical shape widening out downwardly or upwardly, provided that the set of above-mentioned conditions which constitute the invention features i.e., the conditions relating to the transfer passageway, to the annular clearance between the same and the protrusion and the height of the latter, be fulfilled.
  • a fuel injector 9 opens into prechamber 5 and injects the fuel in the direction of the transfer passage way, as diagrammatically shown in FIG. 1.
  • FIG. 2 there have been shown all the parameters involved in the construction of an engine according to this invention.
  • the smallest diameter of the opening of the transfer passageway 6 into the prechamber 5 is at most equal to 0.6 D D being the diameter of the cylinder bore expressed in millimeters.
  • the smallest diameter of the transfer passageway hereabove referred to is the minimum diameter d of the passageway, the latter having also an enlarged section 6b at its opening into the prechamber.
  • the annular clearance between the protrusion 8 and the wall of passageway 6, when the piston is at the top dead center position has a valuej at most equal to 0.05 D" D being still the cylinder bore diameter expressed in millimeters.
  • the height of the protrusion is so determined that, when the piston moves apart from the top dead center position, the passage section left free for the gases between said protrusion and the wall of the transfer passageway becomes equal to the minimum opening section s (FIG. 1) of the transfer passageway into the precombustion chamber, when the crankshaft has rotated from the piston top dead center position through an angle expressed in degrees of crankshaft rotation corresponding to between one half the duration of injection at full load and the whole of said duration.
  • the minimum opening section of said passageway is indicated by reference s on FIG. 1. It is the minimum inlet section for the gases into said prechamber, and not the section of the enlarged portion 6b of the passageway 6.
  • FIGS. 2A to 2C illustrate three positions of the protrusion 8 as it moves downwardly out of the passageway.
  • the passage offered to the gases dashed arrows
  • the passage offered to the gases does not become equal to the minimum section s of the transfer passageway until after the boss 8 has moved to a position spaced further below this lower edge such as shown in FIG. 2C.
  • Condition c discussed above corresponds to the control of the injection duration such that the boss 8 is in the position shown in FIG. 2C when the crankshaft has rotated from the piston top dead center position through an angle corresponding to between one half the duration of injection at full load and the whole of said duration.
  • the present invention is related to engines having conventional injection timing with start of injection preceding top dead center position by a generally similar crankshaft angle for both small and full load operation with end of injection for full load following the top dead center position by a greater amount for full load than for partial load.
  • injection at small load from approximately 10 preceding the top dead center position to approximately 10 following the top dead center position and injection at full load extending to approximately 20 following the top dead center position could be utilized with the present invention.
  • conventional ignition initiation shortly prior to the top dead center position such as 2 to 3 prior to the top dead center position could be utilized.
  • the abscissae are the piston displacements from the top dead center position, expressed in degrees of crankshaft rotation and the ordinates are the percents of burned fuel during the progress of the combustion.
  • the curves 10, 11 and 12 respectively relate to three different types of engines.
  • the first type of engine to which corresponds the curve 10, is a direct injection engine of conventional type wherein the maximum pressure in the combustion chamber is 140 atmospheres, the mean effective pressure being 16 atmospheres.
  • the curve 1] relates to an ideal engine wherein the combustion would progress at constant pressure.
  • Curve 12 relates to an engine according to the invention, running with the same mean effective pressure of 16 atmospheres as the conventional engine corresponding to curve 10, said engine having the same cylinder bore and consequently the same power output as the conventional engine, but running with a maximum pressure in the combustion chamber which is not higher than atmospheres.
  • This engine when running with a maximum pressure of atmospheres can produce a mean effective pressure of 26 atmospheres resulting at equal cylinder bore in a power increase of about 60 percent with respect to a conventional engine running at a maximal pressure of I40 atmospheres in the combustion chamber.
  • the engine according to the invention further exhibits the very considerable advantage of discharging to the atmosphere exhaust gases containing only a reduced proportion of polluting substances.
  • the engine according. to the invention was a supercharged Diesel engine having six cylinders with a cylinder bore diameter of 185 mm and a nominal power of 900 HP at a running speed of 1,500 rpm.
  • the measurements carried out at the testing bench on engines running at full charge relate to the fumes and nitrogen oxides contents of the exhaust gases.
  • Exhaust Fumes A determined volume of exhaust gases from each engine is taken and passed through a filter of determined surface and porosity. The soots contained in the exhaust gases thus darken the filter surface which is compared by any known means to a conventional standard darkness scale called Bacharach scale.
  • direct injection engines nitrogen oxides content of 1,400 ppm (parts per million of parts) engine according to the invention: nitrogen oxides content of 700 ppm.
  • a compression-ignition engine having at least one cylinder, the bottom of which cylinder is provided with a prechamber communicating with the cylinder through a transfer passageway, a piston provided with a protrusion adapted to penetrate said transfer passageway towards the end of the compression stroke, and a fuel injector opening into said prechamber for injecting fuel in the direction of the transfer passageway, wherein the combustion proceeds at substantially constant pressure as a result of the combined use of the following characteristic features:
  • the transfer passageway opens into the prechamber through an opening whose smallest diameter expressed in millimeters is at most equal to 0.6 D, D being the diameter, expressed in millimeters, of the cylinder bore, and
  • the height of the protrusion is so determined that, during the downward stroke of the piston, the flow section left free for the flow of gases between the protrusion and the lower edge of the transfer, passageway becomes equal to the minimum section with which the transfer passageway opens into the precombustion chamber, when the crankshaft has rotated from the piston top dead center position through an angle expressed in degrees of crankshaft rotation corresponding to between one half the duration of injection at full load and the whole of said duration.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
  • Fuel-Injection Apparatus (AREA)
US00132381A 1970-04-15 1971-04-08 Compression-ignition engine Expired - Lifetime US3738332A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR7013719A FR2086996A5 (fr) 1970-04-15 1970-04-15

Publications (1)

Publication Number Publication Date
US3738332A true US3738332A (en) 1973-06-12

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Application Number Title Priority Date Filing Date
US00132381A Expired - Lifetime US3738332A (en) 1970-04-15 1971-04-08 Compression-ignition engine

Country Status (12)

Country Link
US (1) US3738332A (fr)
JP (1) JPS5429642B1 (fr)
BE (1) BE765120A (fr)
CA (1) CA948512A (fr)
CH (1) CH530553A (fr)
DK (1) DK131206B (fr)
ES (1) ES199321Y (fr)
FR (1) FR2086996A5 (fr)
GB (1) GB1298645A (fr)
NL (1) NL172582C (fr)
SE (1) SE356791B (fr)
SU (1) SU489355A3 (fr)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4487167A (en) * 1982-01-22 1984-12-11 Williams Robert H Oscillating piston diesel engine
US4682572A (en) * 1984-09-12 1987-07-28 Samuel Hepko High efficiency performance kinetic occlude system with rotary valve
US6098588A (en) * 1997-02-27 2000-08-08 Motorenfabrik Hatz Gmbh & Co. Kg Injection device and combustion process for an internal combustion engine
US6161516A (en) * 1996-11-07 2000-12-19 Rigazzi; Pier Andrea Process for the formation of a fuel mixture and for its ignition in a pre-chamber that is open toward the cylinders
US6499459B1 (en) * 2000-09-09 2002-12-31 Ford Global Technologies, Inc. Method and apparatus for creating homogeneous charge compression ignition
US20120048235A1 (en) * 2010-08-26 2012-03-01 Eitan Leaschauer Leaschauer Engine
US20140182558A1 (en) * 2010-08-26 2014-07-03 Eitan Leaschauer Leaschauer Engine
US9567895B2 (en) * 2010-08-26 2017-02-14 Eitan Leaschauer Leaschauer engine
US10125666B2 (en) 2016-01-14 2018-11-13 Nautilus Engineering, Llc Systems and methods of compression ignition engines
WO2019081956A1 (fr) 2017-10-28 2019-05-02 Ganz Engine Ltd Agencement structural d'un moteur à allumage par compression avec chambre de précombustion à géométrie variable pour modérer le volume d'émissions dangereuses
US10927750B2 (en) 2016-01-14 2021-02-23 Nautilus Engineering, Llc Systems and methods of compression ignition engines

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2519075A1 (fr) * 1981-12-24 1983-07-01 Gonchar Boris Perfectionnement aux moteurs a combustion interne a chambre de precombustion

Citations (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1263986A (en) * 1913-03-21 1918-04-23 Baltimore Oil Engine Company Internal-combustion engine and process of mixing fuel and air and producing combustion.
US1354786A (en) * 1918-11-21 1920-10-05 Tartrais Eugene Henri Two-stroke explosion-engine fed with liquid fuel
US1419702A (en) * 1921-07-14 1922-06-13 Tartrais Eugene Henri Combustion chamber for internal-combustion engines
US1524894A (en) * 1921-10-13 1925-02-03 Thomson Kenneth John Internal-combustion engine
US1687526A (en) * 1925-01-21 1928-10-16 Tartrais Eugene Henri Cylinder head for internal-combustion engines
US1691173A (en) * 1925-03-26 1928-11-13 Aage E Winckler Combustion chamber for internal-combustion engines
US1691302A (en) * 1923-02-21 1928-11-13 Adolphe C Peterson Fuel-injection engine
US1696799A (en) * 1926-04-12 1928-12-25 Held Georges Internal-combustion engine of the two-stroke type
US1772742A (en) * 1925-12-24 1930-08-12 Charles G Barrett Internal-combustion engine
US1838495A (en) * 1929-10-23 1931-12-29 Paul A O'neill Internal combustion engine
US1867683A (en) * 1923-10-22 1932-07-19 Sperry Dev Co Combustion engine
US1942127A (en) * 1931-02-05 1934-01-02 Russell Frederick Clifton Internal combustion engine
US1977752A (en) * 1931-10-01 1934-10-23 Baj Alessandro Internal combustion engine
US2012086A (en) * 1931-09-03 1935-08-20 Eclipse Aviat Corp Internal combustion engine
US2026321A (en) * 1933-06-10 1935-12-31 Thomas E Quick Internal combustion engine
US2442082A (en) * 1944-04-13 1948-05-25 Louis O French Internal-combustion engine
US3386422A (en) * 1965-11-23 1968-06-04 Inst Francais Du Petrole Compression-ignition engine
US3543735A (en) * 1968-06-24 1970-12-01 Mcculloch Corp Combustion system for internal combustion engine

Patent Citations (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1263986A (en) * 1913-03-21 1918-04-23 Baltimore Oil Engine Company Internal-combustion engine and process of mixing fuel and air and producing combustion.
US1354786A (en) * 1918-11-21 1920-10-05 Tartrais Eugene Henri Two-stroke explosion-engine fed with liquid fuel
US1419702A (en) * 1921-07-14 1922-06-13 Tartrais Eugene Henri Combustion chamber for internal-combustion engines
US1524894A (en) * 1921-10-13 1925-02-03 Thomson Kenneth John Internal-combustion engine
US1691302A (en) * 1923-02-21 1928-11-13 Adolphe C Peterson Fuel-injection engine
US1867683A (en) * 1923-10-22 1932-07-19 Sperry Dev Co Combustion engine
US1687526A (en) * 1925-01-21 1928-10-16 Tartrais Eugene Henri Cylinder head for internal-combustion engines
US1691173A (en) * 1925-03-26 1928-11-13 Aage E Winckler Combustion chamber for internal-combustion engines
US1772742A (en) * 1925-12-24 1930-08-12 Charles G Barrett Internal-combustion engine
US1696799A (en) * 1926-04-12 1928-12-25 Held Georges Internal-combustion engine of the two-stroke type
US1838495A (en) * 1929-10-23 1931-12-29 Paul A O'neill Internal combustion engine
US1942127A (en) * 1931-02-05 1934-01-02 Russell Frederick Clifton Internal combustion engine
US2012086A (en) * 1931-09-03 1935-08-20 Eclipse Aviat Corp Internal combustion engine
US1977752A (en) * 1931-10-01 1934-10-23 Baj Alessandro Internal combustion engine
US2026321A (en) * 1933-06-10 1935-12-31 Thomas E Quick Internal combustion engine
US2442082A (en) * 1944-04-13 1948-05-25 Louis O French Internal-combustion engine
US3386422A (en) * 1965-11-23 1968-06-04 Inst Francais Du Petrole Compression-ignition engine
US3543735A (en) * 1968-06-24 1970-12-01 Mcculloch Corp Combustion system for internal combustion engine

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4487167A (en) * 1982-01-22 1984-12-11 Williams Robert H Oscillating piston diesel engine
US4682572A (en) * 1984-09-12 1987-07-28 Samuel Hepko High efficiency performance kinetic occlude system with rotary valve
US6161516A (en) * 1996-11-07 2000-12-19 Rigazzi; Pier Andrea Process for the formation of a fuel mixture and for its ignition in a pre-chamber that is open toward the cylinders
US6098588A (en) * 1997-02-27 2000-08-08 Motorenfabrik Hatz Gmbh & Co. Kg Injection device and combustion process for an internal combustion engine
US6499459B1 (en) * 2000-09-09 2002-12-31 Ford Global Technologies, Inc. Method and apparatus for creating homogeneous charge compression ignition
US20140182558A1 (en) * 2010-08-26 2014-07-03 Eitan Leaschauer Leaschauer Engine
US20120048235A1 (en) * 2010-08-26 2012-03-01 Eitan Leaschauer Leaschauer Engine
US9371770B2 (en) * 2010-08-26 2016-06-21 Eitan Leaschauer Leaschauer engine
US9567895B2 (en) * 2010-08-26 2017-02-14 Eitan Leaschauer Leaschauer engine
US10125666B2 (en) 2016-01-14 2018-11-13 Nautilus Engineering, Llc Systems and methods of compression ignition engines
US10669926B2 (en) 2016-01-14 2020-06-02 Nautilus Engineering, Llc Systems and methods of compression ignition engines
US10927750B2 (en) 2016-01-14 2021-02-23 Nautilus Engineering, Llc Systems and methods of compression ignition engines
US11608773B2 (en) 2016-01-14 2023-03-21 Nautilus Engineering, Llc Systems and methods of compression ignition engines
WO2019081956A1 (fr) 2017-10-28 2019-05-02 Ganz Engine Ltd Agencement structural d'un moteur à allumage par compression avec chambre de précombustion à géométrie variable pour modérer le volume d'émissions dangereuses

Also Published As

Publication number Publication date
NL7105011A (fr) 1971-10-19
DK131206B (da) 1975-06-09
JPS5429642B1 (fr) 1979-09-25
ES199321Y (es) 1975-11-16
GB1298645A (en) 1972-12-06
ES199321U (es) 1975-07-16
DE2118359A1 (de) 1971-10-28
FR2086996A5 (fr) 1971-12-31
SE356791B (fr) 1973-06-04
SU489355A3 (ru) 1975-10-25
CH530553A (fr) 1972-11-15
CA948512A (en) 1974-06-04
NL172582C (nl) 1983-09-16
BE765120A (fr) 1971-10-01
DK131206C (fr) 1975-11-10
NL172582B (nl) 1983-04-18

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