US3809039A - Stratified charge spark ignition internal combustion engine with exhaust recycle - Google Patents

Stratified charge spark ignition internal combustion engine with exhaust recycle Download PDF

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Publication number
US3809039A
US3809039A US00291612A US29161272A US3809039A US 3809039 A US3809039 A US 3809039A US 00291612 A US00291612 A US 00291612A US 29161272 A US29161272 A US 29161272A US 3809039 A US3809039 A US 3809039A
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Prior art keywords
fuel
air mixture
engine
percent
mixture
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Expired - Lifetime
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US00291612A
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English (en)
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H Alquist
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Phillips Petroleum Co
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Phillips Petroleum Co
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Priority to US00291612A priority Critical patent/US3809039A/en
Priority to CA172,062A priority patent/CA976820A/en
Priority to JP6768773A priority patent/JPS5345856B2/ja
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Publication of US3809039A publication Critical patent/US3809039A/en
Anticipated expiration legal-status Critical
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D21/00—Controlling engines characterised by their being supplied with non-airborne oxygen or other non-fuel gas
    • F02D21/06—Controlling engines characterised by their being supplied with non-airborne oxygen or other non-fuel gas peculiar to engines having other non-fuel gas added to combustion air
    • F02D21/08—Controlling engines characterised by their being supplied with non-airborne oxygen or other non-fuel gas peculiar to engines having other non-fuel gas added to combustion air the other gas being the exhaust gas of engine
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S123/00—Internal-combustion engines
    • Y10S123/04—Stratification

Definitions

  • ABSTRACT A spark ignition system and a method for operating same by passing a first fuel-air mixture into a precombustion chamber of the engine and a second leaner fuel-air mixture into a primary combustion chamber, igniting the first mixture'for igniting the second mixture, and controllably mixing about 5 to about 20 percent of the exhaust gas resulting from the combustion of the fuel mixtures with the second fuel-air mixture during operation of the engine at greater than about 75 percent maximum power output with the amount of exhaust gas being mixed with the second fuel-air mixture varying directly with the power output of the engine.
  • This invention therefore resides in a spark ignition system and a method of operating same by passing a first fuel-air mixture into a precombustion chamber of the engine and a second leaner fuel-air mixture into a primary combusiton chamber, igniting the first mixture for igniting the second mixture, and controllably mixing about to about 20 percent of the exhaust gas resulting from the combustion of the fuel mixtures with the second fuel-air mixture during operation of the engine at greater than about 75 percent maximum power output with the amount of exhaust gas being mixed with the second fuel-air mixture varying directly with the power output of the engine.
  • FIG. 1 shows the apparatus of this invention
  • FIG. 2 shows the combustion chambers
  • FIG. 2a shows element 6 in more detail
  • FIGS. 3-8 show data of tests performed on the engine.
  • a spark ignition engine 2 has a primary combustion zone 4 and a precombustion zone 6 that are in fluid communication one with the other.
  • a primary combustion zone 4 and a precombustion zone 6 that are in fluid communication one with the other.
  • the primary and precombustion zones in the singular. It should be understood, however, that the engine can have a plurality of primary combustion zones, preferably with each primary zone having a precombustion zone with the associated elements as set forth with reference to the singular zones.
  • Each of the combustion zones 4, 6 has a separate carburetor 8, connected in fluid communication therewith which in turn is connected to an air supply, afuel supply, and a throttle for controllably discharging fuelair mixtures from the carburetors 8, 10 into their respective combustion zones 4, 6.
  • the carburetor 8 of the primary combustion zone or chamber 4 is constructed to receive and mix fuel and air therein and discharge a fuel-air mixture into the primary combustion zone 4 that is a relatively lean fuel-air mixture, being less than about an 80 percent stoichiometric fuel.
  • the carburetor 10 of the precombustion zone or chamber 6 is constructed to receive and mix fuel and air therein and discharge a fuel-air mixture into the pre-' combustion chamber 4 that is a richer mixture relative to the other fuel mixture, preferably a fuel-air mixture in the range of about a 500 to about a 1,000 percent stoichiometric fuel.
  • a spark ignition system is associated with the precombustion chamber 6 for igniting the fuelair mixture therein, which in turn ignites the fuel-air mixture in the primary combustion zone 4 for operating the engine 2.
  • An exhaust conduit 14 (FIG. 1) is connected to the exhaust outlet of the primary combustion chamber 4 for directing the exhaust gas resulting from combustion of the first and second fuel-air mixtures from the engine 2.
  • An exhaust gas recirculating conduit 16 is connected in fluid communication with the primary combustion zone 4 and the exhaust conduit 14.
  • a measuring means for example a pressure controller 18, is associated with the engine 2 for measuring a variable representative of the power output of the engine 2 and delivering a signal representative thereof.
  • the measuring means can measure the intake manifold pressure of the primary combustion zone 4 as shown in FIG. 1.
  • a control means such as a control valve 20 for example, is positioned in the exhaust gas recirculating conduit l6 and is connected to the measuring means 18 for receiving a signal therefrom and opening and closing the valve in response to said signal.
  • the valve 20 is constructed to be in the closed position in response to a signal representative of the output of the engine being less than about percent maximum power output of the engine.
  • the valve 20 is open and controllably positioned in response to a signal from the measuring means representative of the output of the engine 2 being greater than about 75 percent maximum power output with the opening of said valve 20 varying directly with the power output of the engine 2 and passing exhaust gas in the range of about 5 to about 20 percent of the total exhaust gas passing through conduit 14.
  • FIGS. 3-8 show the results of tests on an engine of this invention.
  • Shape cylindrical Orifice: one-eighth in. square edge Volume: 0.83 cu. in.
  • Intake valve location rear of chamber Spark gap location: rear of chamber Length/Diameter: 3.80
  • the precombustion chamber was operated with a supply of fuel-air mixture such that 88 percent of the precombustion chamber volume was filled with mixmm at the beginning of the compression stroke. Fuel was present in the mixture supplied the precombustion chamber in an amount 5 times that required for a stoichiometric mixture, i.e., 500 percent stoichiometric fuel.
  • the engine used was a CFR, single cylinder unit similar in basic configuration to the standard knock-test engine except for two additional combustion chamber access holes.
  • a sketch of the arrangement of the precombustion chamber and the main CFR engine combustion chamber is shown in FIG. 2.
  • the fuel was a conventional premium grade gasoline having a research octane number of 99 and containing 2.5 ml TEL per gallon.
  • FIG. 3 presents peak dP/dT values on an arbitrary, but linear, scale as functions of stoichiometry. Results of the conventional engine, the precombustion chambered engine, and the precombustion chambered engine with 8 percent EGR are included. Objectionable combustion noise did not occur below a value of 6 on the scale in FIG. 3.
  • FIG. 4 presents exhaust NO, concentrations (as NO) plotted against the percentage stoichiometric fuel. At all stoichiometries richer than 70 percent stoichiometric fuel, 8 percent EGR reduced NO; emission. At stoichiometrics leaner than 70 percent, the presence of recirculated exhaust gas appeared to increase NO,,. Although the reasons for this increase are unknown, it is unimportant since NO; values with the prechambered engine were quite low at the stoichiometries where the increase occurred. Hence, there would be no incentive for EGR application in this stoichiometry range. Eight Percent EGR reduced N from the precombustion. chambered engine about 54 percent at 90 percent stoichiometric fuel at constant power.
  • FIG. 5 shows that 8 percent EGR in the precombustion chambered engine produced a 4 to 7 percent loss of power at constant throttle.
  • the prechambered engine without EGR resulted in a 5 to 9 percent decrease in power as compared to the conventional engine.
  • the total power decrease attributed to the simultaneous application of the precombustion chambered combustion process and the 8 percent EGR' was about 12 percent. Although not desirable, this power loss is certainly acceptable.
  • FIG. 6 shows that 8 percent EGR had only a mirror effect on exhaust hydrocarbon concentrations. From I00 percent to 70 percent stoichiometric fuel, which is the range where EGR is applied to the precombustion chambered engine, 8 percent EGR increased hydrocarbon emissions no more than 14 percent and as little as 6 percent.
  • FIG. 7 shows that the influence of 8 percent EGR on the carbon monoxide emissions from a precombustion chambered engine is negligible.
  • FIG. 8 compares the effectiveness of about the same amount of exhaust gas recirculation (EGR) on NO formation from a conventional engine and a prechambered engine.
  • EGR exhaust gas recirculation
  • FIG. 8 shows that applying EGR to the prechambered engine has about the same benefit on NO (at a given stoichiometric mixture) as the application of EGR to the conventional engine.
  • the application of EGR enrichens the lean misfire limit from about 74 percent stoichiometric fuel to about 89 percent stoichiometric fuel (see FIG. 8) which limits the usefulness of EGR.
  • the application of EGR has no deleterious effect on lean misfire limit.
  • EGR has the other important benefit of substantially reducing excessive rates of pressure rise (leading -to noise) of the prechambered engine.
  • This invention therefore provides a spark ignition engine which will operate with low pollution emissions while maintaining high power output and efficiency.
  • a spark ignition system having a primary combustion zone, mixing means for controllably mixing a primary fuel-air mixture, and means for passing said primary fuel-air mixture into the primary combustion zone, the improvement comprising:
  • a precombustion chamber being in fluid communication with the primary combustion zone
  • mixing means for controllably mixing another fuel-air mixture being a richer fuel mixture relative to said primary fuel-air mixture
  • exhaust means for directing the combustion gas resulting from combustion ofthe fuel-air mixture from the engine
  • measuring means for measuring a variable representative of the power output of the engine and delivering a signal in response thereto;
  • control means for passing about 5 to about 20 percent of the exhaust gas resulting from the combustion of the first and second fuel-air mixtures into the primary combustion chamber during operation of the engine at greater than about 75 percent maximum power output of the engine, said control means comprising a control valve positioned in the conduit and connected to the measuring means, said valve being in a closed position in response to a signal from the measuring means representative of the output of the engine being less than about 75 percent maximum power output and said valve being controllably opened in response to a signal from the measuring means representative of the output of the engine being greater than about 75 percent maximum power output with the opening of said valve varying directly with the power output 5 of the engine.
  • variable measured by the measuring means is the manifold pressure of the primary combustion zone.

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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)
  • Exhaust-Gas Circulating Devices (AREA)
US00291612A 1972-09-25 1972-09-25 Stratified charge spark ignition internal combustion engine with exhaust recycle Expired - Lifetime US3809039A (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US00291612A US3809039A (en) 1972-09-25 1972-09-25 Stratified charge spark ignition internal combustion engine with exhaust recycle
CA172,062A CA976820A (en) 1972-09-25 1973-05-23 Internal combustion engine with exhaust gas recirculation
JP6768773A JPS5345856B2 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html) 1972-09-25 1973-06-15

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US00291612A US3809039A (en) 1972-09-25 1972-09-25 Stratified charge spark ignition internal combustion engine with exhaust recycle

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JP (1) JPS5345856B2 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
CA (1) CA976820A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3890945A (en) * 1973-03-19 1975-06-24 Toyota Motor Co Ltd Exhaust gas cleaning system for internal combustion engines
US3908618A (en) * 1973-02-26 1975-09-30 Nissan Motor Torch-ignition reciprocating-piston type internal combustion engine
US3941105A (en) * 1973-11-08 1976-03-02 Honda Giken Kogyo Kabushiki Kaisha Exhaust gas recirculation for three-valve engine
US4020808A (en) * 1973-02-23 1977-05-03 Honda Giken Kogyo Kabushiki Kaisha Exhaust gas recirculation for emissions control
US4024708A (en) * 1974-12-04 1977-05-24 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Multi cylinder internal combustion engine
US4031867A (en) * 1974-12-28 1977-06-28 Fuji Jukogyo Kabushiki Kaisha Internal combustion engine combustion process
US4041916A (en) * 1975-04-15 1977-08-16 Nissan Motor Company, Limited Internal combustion engine and method of operating same
US4051824A (en) * 1974-11-30 1977-10-04 Fuji Jukogyo Kabushiki Kaisha Internal combustion engine for motor vehicles
US4074661A (en) * 1975-02-14 1978-02-21 Nippon Soken, Inc. Fuel reforming system for an internal combustion engine
US4074664A (en) * 1976-02-12 1978-02-21 Astron Innovations, Inc. Fuel control system for internal combustion engines
US4096832A (en) * 1976-08-26 1978-06-27 Casull Don C Ignition apparatus and method for an internal combustion engine
US4146005A (en) * 1976-08-18 1979-03-27 Phillips Petroleum Company Method of operating a spark ignition engine
US4231339A (en) * 1978-06-16 1980-11-04 Yamaha Hatsukoko Kabushiki Kaisha Control device for exhaust gas recycled internal combustion engine
US4271810A (en) * 1980-01-11 1981-06-09 General Motors Corporation Divided chamber engine with prechamber exhaust recirculation
US4574754A (en) * 1982-08-16 1986-03-11 Rhoades Jr Warren A Stratified charge combustion system and method for gaseous fuel internal combustion engines
US20140109866A1 (en) * 2012-10-24 2014-04-24 Ge Jenbacher Gmbh & Co Og Internal combustion engine
WO2020076221A1 (en) * 2018-10-11 2020-04-16 Scania Cv Ab A pre-chamber arrangement for a gas engine and a gas engine

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5890456U (ja) * 1981-12-07 1983-06-18 第一精工株式会社 カウンタ−の固定構造

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2421406A (en) * 1944-08-19 1947-06-03 Carter Carburetor Corp Fuel conditioning device
CA549164A (en) * 1957-11-26 August Pablo Two-cycle internal combustion engines
US3066662A (en) * 1960-08-26 1962-12-04 Walker Mfg Co Ignition device for internal combustion engines
US3479997A (en) * 1968-05-13 1969-11-25 Continental Motors Corp Inlet valve for internal combustion engine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA549164A (en) * 1957-11-26 August Pablo Two-cycle internal combustion engines
US2421406A (en) * 1944-08-19 1947-06-03 Carter Carburetor Corp Fuel conditioning device
US3066662A (en) * 1960-08-26 1962-12-04 Walker Mfg Co Ignition device for internal combustion engines
US3479997A (en) * 1968-05-13 1969-11-25 Continental Motors Corp Inlet valve for internal combustion engine

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4020808A (en) * 1973-02-23 1977-05-03 Honda Giken Kogyo Kabushiki Kaisha Exhaust gas recirculation for emissions control
US3908618A (en) * 1973-02-26 1975-09-30 Nissan Motor Torch-ignition reciprocating-piston type internal combustion engine
US3890945A (en) * 1973-03-19 1975-06-24 Toyota Motor Co Ltd Exhaust gas cleaning system for internal combustion engines
US3941105A (en) * 1973-11-08 1976-03-02 Honda Giken Kogyo Kabushiki Kaisha Exhaust gas recirculation for three-valve engine
US4051824A (en) * 1974-11-30 1977-10-04 Fuji Jukogyo Kabushiki Kaisha Internal combustion engine for motor vehicles
US4024708A (en) * 1974-12-04 1977-05-24 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Multi cylinder internal combustion engine
US4031867A (en) * 1974-12-28 1977-06-28 Fuji Jukogyo Kabushiki Kaisha Internal combustion engine combustion process
US4074661A (en) * 1975-02-14 1978-02-21 Nippon Soken, Inc. Fuel reforming system for an internal combustion engine
US4041916A (en) * 1975-04-15 1977-08-16 Nissan Motor Company, Limited Internal combustion engine and method of operating same
US4074664A (en) * 1976-02-12 1978-02-21 Astron Innovations, Inc. Fuel control system for internal combustion engines
US4146005A (en) * 1976-08-18 1979-03-27 Phillips Petroleum Company Method of operating a spark ignition engine
US4096832A (en) * 1976-08-26 1978-06-27 Casull Don C Ignition apparatus and method for an internal combustion engine
US4231339A (en) * 1978-06-16 1980-11-04 Yamaha Hatsukoko Kabushiki Kaisha Control device for exhaust gas recycled internal combustion engine
US4271810A (en) * 1980-01-11 1981-06-09 General Motors Corporation Divided chamber engine with prechamber exhaust recirculation
US4574754A (en) * 1982-08-16 1986-03-11 Rhoades Jr Warren A Stratified charge combustion system and method for gaseous fuel internal combustion engines
US20140109866A1 (en) * 2012-10-24 2014-04-24 Ge Jenbacher Gmbh & Co Og Internal combustion engine
CN103821637A (zh) * 2012-10-24 2014-05-28 Ge延巴赫两合无限公司 内燃机
US9644571B2 (en) * 2012-10-24 2017-05-09 Ge Jenbacher Gmbh & Co Og Internal combustion engine
WO2020076221A1 (en) * 2018-10-11 2020-04-16 Scania Cv Ab A pre-chamber arrangement for a gas engine and a gas engine
CN112789398A (zh) * 2018-10-11 2021-05-11 斯堪尼亚商用车有限公司 用于燃气发动机的预燃室布置和燃气发动机
SE543937C2 (en) * 2018-10-11 2021-09-28 Scania Cv Ab A pre-chamber arrangement and a gas engine for increased combustion efficiency
US11578683B2 (en) 2018-10-11 2023-02-14 Scania Cv Ab Pre-chamber arrangement for a gas engine and a gas engine

Also Published As

Publication number Publication date
CA976820A (en) 1975-10-28
JPS4970028A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html) 1974-07-06
JPS5345856B2 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html) 1978-12-09

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