US3823702A - Internal combustion engine manifold and fluid flow configuration - Google Patents

Internal combustion engine manifold and fluid flow configuration Download PDF

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Publication number
US3823702A
US3823702A US00105474A US10547471A US3823702A US 3823702 A US3823702 A US 3823702A US 00105474 A US00105474 A US 00105474A US 10547471 A US10547471 A US 10547471A US 3823702 A US3823702 A US 3823702A
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Prior art keywords
manifold
port
cylinder head
intake
disposed
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US00105474A
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English (en)
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C Roberts
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Individual
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Priority to US00105474A priority Critical patent/US3823702A/en
Priority to FR7147211A priority patent/FR2119776A5/fr
Priority to DE19722200818 priority patent/DE2200818A1/de
Priority to IT47618/72A priority patent/IT948154B/it
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Publication of US3823702A publication Critical patent/US3823702A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M1/00—Carburettors with means for facilitating engine's starting or its idling below operational temperatures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2700/00—Supplying, feeding or preparing air, fuel, fuel air mixtures or auxiliary fluids for a combustion engine; Use of exhaust gas; Compressors for piston engines
    • F02M2700/43—Arrangements for supplying air, fuel or auxiliary fluids to a combustion space of mixture compressing engines working with liquid fuel
    • F02M2700/4302—Arrangements for supplying air, fuel or auxiliary fluids to a combustion space of mixture compressing engines working with liquid fuel whereby air and fuel are sucked into the mixture conduit
    • F02M2700/4392—Conduits, manifolds, as far as heating and cooling if not concerned; Arrangements for removing condensed fuel

Definitions

  • ABSTRACT The manifold and cylinder head structures of an internal combustion engine are provided with fluid flow passageways extending from the manifold plenum to the valve ports of the engine cylinders, with fluid vflow control members disposed in the passageways and defining peripheral restrictions therein.
  • the members are integrally formed in a gasket sandwiched between the manifold and the cylinder head and having openings registered with the passageways, which openings have a cross sectional area less than the passageway cross sectional areas.
  • the insert members are elongated and increase in cross sectional area from the upstream to the downstream ends.
  • each insert member has an integral flange at either end or intermediate the ends, the flange being retained between the manifold and the cylinder head.
  • a plurality of members are formed integrally in a single gasket element sandwiched between the manifold and the cylinder head.
  • the insert members are integral with the manifold or with the cylinder head port runners.
  • the intake passageway insert members are press fit or otherwise secured closely adjacent the intake ports.
  • the present invention constitutes an improvement over the inventions disclosed in my prior patents, the improvement constituting various configurations in which fluid flow members are provided in the passageways extending between the valve ports and the intake and exhaust manifolds, the members defining peripheral restrictions in the passageways such that, in the intake passageway any liquid fuel will be trapped and caused to fume over the edge of the member, avoiding the induction of unatomized fuel to the engine cylinders; and in the exhaust passageway, unburned hydrocarbons, which have a tendency to flow along the walls of the exhaust passage, will also be trapped in a high temperature area and burned prior to emission from the vehicle tail pipe, these factors resulting in a significant reduction in exhaust pollutants.
  • the restrictions are such as will tend to effect a greater uniformity of intake'fluid flow rates throughout the entire operating range of the engine, thereby effecting an adequate combustible charge delivery to all cylinders at all times; and in the exhaust passageways the restrictions provide for substantially equalized exhaust back pressure to all of the cylinders, thus providing for a more economical and efficient operation of the engine as a whole.
  • FIG. I is a diagrammatic cross-sectional view through an engine cylinder and the intake and exhaust port runners and manifolds embodying one preferred configuration of the present invention
  • FIG. 2 is a fragmentary cross-sectional view through a manifold and port runner embodying one preferred configuration of the invention
  • FIG. 2A is a perspective view of the insert member used in the embodiment of FIG. 2;
  • FIGS. 3 through 8 are fragmantary cross-sectional views through manifold and cylinder head configurations and the associated fluid flow control members, according to various other embodiments of the invention.
  • FIG. 9 is a perspective exploded view of an engine and manifold structure illustrating a gasket configuration embodying the present invention.
  • FIGS. 10 through 13 are fragmentary cross-sectional views through cylinder head intake port runner configurations and the associated fluid flow control members, according to further embodiments of the invention.
  • FIG. 1 illustrates an engine cylinder block 10 having a cylinder 12 in which reciprocates a conventional piston l4, and a cylinder head 16 having a combustion chamber 18 overlying the cylinder 12.
  • Intakeand exhaust ports 20 and 22 connect the combustion chamber 18 respectively with intake and exhaust port runners 24 and 26 in the cylinder head 16 and are opened and closed by intake and exhaust valves 28 and 30 in conventional fashion.
  • Intake and exhaust manifolds 32 and 34 respectively having passages 36 and 38 registering with the port runners 24 and 26 and communicating with intake and exhaust manifold plenums 40 and 42, are secured to the cylinder head by any means such as studs 44.
  • Intake and exhaust fluid flow control members 46 and 48 are disposed in the intake and exhaust passageways formed by the port runners and manifold passages, and may be formed .in various configurations as suggested by FIGS. 2 through 13 hereafter described.
  • a fluid flow control member 46a is illustrated as comprising preferably a stamped or otherwise suitably formed metal insert member having a frusto-conically equivalent shape in which the transverse cross-sectional area increases from the upstream end to the downstream end thereof.
  • the member 4611 has a peripheral flange 50 arranged to be sandwiched between a manifold mounting flange 52 and a manifold gasket 56.
  • the member 46a is disposed within the intake manifold passage 36 in a manner to form a peripheral space 60 which will act to trap any liquid fuel or water condensation entrained in the fuel-air mixture flowing toward the intake port runner passage 24.
  • This liquid will be subjected to fluid turbulence and cylinder head engine heat,'promoting atomization or vaporization of the liquid, and any liquid which may end to creep back across the outer surface of the member 46 to its upstream end, where it may flow over the edge of the member 46, will be atomized off the edge by the inducted fuel-air mixture flow before further entrainment in the mixture.
  • This configuration efiectively eliminates the introduction of unatomized or unvaporized fuel or other liquids into the combustion chamber, promoting more complete combustion of the mixture in the engine and avoiding rich mixtures which cause high pollutant emission.
  • the frusto-conicalequivalent shape of the member 46a achieves the fliud flow control results heretofore described in my US. Pat. Nos. 3,429,303 and 3,457,904 and need not be further described herein except to note that the included angle of conicity equivalence is preferably between and which has been found to be the range within which the fluid flow control is best achieved.
  • the member 46a further constitutes a restriction of a predetermined length within the fluid flow passageway. Similar members 46a are provided in all of the intake passageways, all having the same longitudinal dimensions and all having the same transverse crosssectional area at the upstream ends thereof, with the total of such cross-sectional areas being less than could accomodate the volume flow available from the intake manifold plenum 40. This construction has the result of equalizing the flow rates to the individual combustion chambers to provide uniform mixtures thereto which produces maximumefflciency in engine operation.
  • the same fluid flow control member 46a can be used as an insert in the exhaust port runner 26 as shown in FIG. 3.
  • the peripheral flange 50 of the member 46a is, similarly to the disclosure of FIG. 2, sandwiched between a flange 54 of the exhaust manifold 34 and an exhaust manifold gasket 58.
  • the member 46a thus provides a peripheral space 62. Since unburned hydrocarbons and other solids emitted from the combustion chamber on the exhaust stroke of the piston tend to flow along the walls of the exhaust passageway, this space 62 serves to trap them at a location close to the engine where they will be subjected to the turbulent hot exhaust gases as well as cylinder head engine heat and consumed prior to being entrained in the exhaust rather than discharged through the exhaust manifold 34 to the exhaust pipe (not shown). This contributes highly to the reduction in hydrocarbon and solid pollutant emissions from the engine.
  • FIG. 4 illustrates an insert member 46b which has a peripheral flange 64 integrally formed with the member 46b and extending from the midsection thereof between the upstream and downstream ends such that one end of the insert member 46b projects into the manifold passage 36 and the other end projects into the cylinder head port runner passage 24. Also, it will be seen that the flange 64 replaces the conventional gasket between the manifold 32 and cylinder head 16.
  • FIG. 5 illustrates the configuration of a fluid flow control member 46c in which a flange 66 is formed integrally with the smaller cross sectional end of the member 46c for clamping between the intake manifold flange 52 and cylinder head 16, and has a return bent portion 66a forming a peripheral space 68 for the entrapment of unvaporized or unatomized liquid fuel in the fuel-air mixture for the purposes heretofore described.
  • FIG. 6 illustrates arfluid flow control member 46d which is similar to the member 46a of FIG. 2 but has a flange 70 which serves as the gasket between the intake manifold flange 52 and the cylinder head 16.
  • FIG. 7 illustrates a structure in which a fluid flow control member 46e is integral withthe manifold 32 and is formed to provide a peripheral space 72 around the smaller upstream end of the member 46e for entrapment of liquid fuel as heretofore described.
  • FIG. 8 illustrates a simplified fluid flow control member 46f which in effect is simply the gasket sandwiched between the manifold 32 and the cylinder head 16 but having an opening 74 of a cross-sectional area smaller than the corss-sectional area of the fluid flow passageway and thereby providing a shoulder against which liquid fuel will be trapped and caused to flow inward toward the opening 74 where it will be atomized over the edge thereof.
  • the members 46f will all of the members 46f having the same thickness or constituting a single gasket with a plurality of openings 74, one for each cylinder, the axial length of the restricted openings 74 will all be the same, and this configuration will tend to even out the fuel-air charges inducted into the intake port runners 24.
  • the frusto-conical equivalent formation is not provided in this configuration.
  • FIG. 9 illustrates an engine 76 having the cylinder head 16 on which the intake manifold 32 is adapted to be secured by means of the studs 34.
  • fuel flow control members 46g are integrally formed with a manifold gasket 78 by stamping or any other means desired. The members 46g will thus be disposed within the passages of the manifold 32 substantially as in the configuration of FIG. 6.
  • FIGZ 11 illustrates a fluid flow control member 46i having its larger end formed to be press fit within the intake port runner 24 closely adjacent the intake valve port 20, thereby providing a peripheral space 82 for the previously described purposes.
  • FIG. 12 illustrates a fluid flow control member 64j which consists of a substantially straight cylindrical member having its downstream end press fit within the intake port runner 24 which is enlarged close to the intake port 20 to provide a peripheral space 84 for the same purposes heretofore described.
  • FIG. 13 illustrates a fliud flow control member 46k which has its larger cross-sectional end forged outwardly to engage in a peripheral groove 86 formed in the cylinder head 16 closely adjacent the intake valve port 20, thereby providing a peripheral space 88 for the above described purposes.
  • the spaces 80, 82, 84 and 88 of the embodiments of the invention shown in FIGS. l0l3 act to trap liquid fuel in an area of the cylinder head 16 which is close to the combustion chamber 18 and hence is subject to higher temperatures for vaporization.
  • a fluid flow control member formed of sheet material and disposed within at least one of said passageways, said member formed with an opening having at least in one transverse cross-section a cross-sectional area less than the smallest transverse cross-sectional area of said passageway and defining a peripheral restriction therein, and
  • an internal combustion engine cylinder head structure provided with a combustion chamber and an intake port runner terminating in an intake valve port opening to said combustion chamber
  • the improvement comprising a member associated with said port runner and forming a peripheral recess facing upstream of flow through said port runner and positioned to trap liquid entrained in gases flowing through said port runner to said intake valve port, and to retain said liquid until it vaporizes or creeps inward into the upstream end of said member, said upstream end having an edge effective to atomize said liquid by shearing action of gas flow into said member.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
US00105474A 1971-01-11 1971-01-11 Internal combustion engine manifold and fluid flow configuration Expired - Lifetime US3823702A (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US00105474A US3823702A (en) 1971-01-11 1971-01-11 Internal combustion engine manifold and fluid flow configuration
FR7147211A FR2119776A5 (fr) 1971-01-11 1971-12-29
DE19722200818 DE2200818A1 (de) 1971-01-11 1972-01-08 Einlass- und Auslassleitungen fuer einen Verbrennungsmotor sowie deren Stroemungskanaele
IT47618/72A IT948154B (it) 1971-01-11 1972-01-10 Strutture di collettore e di condotti di flusso per motori a combustione interna

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US00105474A US3823702A (en) 1971-01-11 1971-01-11 Internal combustion engine manifold and fluid flow configuration

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US (1) US3823702A (fr)
DE (1) DE2200818A1 (fr)
FR (1) FR2119776A5 (fr)
IT (1) IT948154B (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4180029A (en) * 1976-12-29 1979-12-25 Toyota Jidosha Kogyo Kabushiki Kaisha 2-Cycle engine of an active thermoatmosphere combustion
FR2472671A1 (fr) * 1979-10-23 1981-07-03 Dresser Investments Procede et dispositif pour effectuer des economies de consommation par modification de l'ecoulement
US4756045A (en) * 1986-06-02 1988-07-12 Action Technology Vacuum cleaner hose having alternating height corrugations
DE4111772A1 (de) * 1991-04-11 1992-10-15 Kloeckner Humboldt Deutz Ag Ansaugsystem fuer eine selbstzuendende brennkraftmaschine
EP1540166A1 (fr) * 2002-07-18 2005-06-15 Kohler Co. Composant pour gerer le flux aerien dans un orifice de culasse et autour de celle-ci
US20060037577A1 (en) * 2004-08-17 2006-02-23 Dave Procknow Air flow arrangement for a reduced-emission single cylinder engine
US20100065004A1 (en) * 2008-09-12 2010-03-18 Gm Global Technology Operations, Inc. Mixture Motion Enhancing Intake Manifold Gasket
CN101131127B (zh) * 2006-08-24 2010-07-21 通用汽车环球科技运作公司 进气歧管调谐阀模糊逻辑诊断
US8973905B2 (en) 2012-09-27 2015-03-10 Kohler Co. Venturi insert for a carburetor, and carburetor, system and apparatus incorporating the same

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2536792B1 (fr) * 1982-11-29 1987-03-20 Peugeot Circuit d'admission pour moteur a combustion interne equipe d'un dispositif d'attenuation du bruit d'admission
WO2013093541A1 (fr) * 2011-12-22 2013-06-27 Renault Trucks Culasse pour moteur

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1512952A (en) * 1919-06-30 1924-10-28 Advance Rumely Co Reatomizer
US1526963A (en) * 1922-04-17 1925-02-17 Aquila D Chandler Revaporizer
US1530157A (en) * 1921-10-17 1925-03-17 Charles W Gillett Reatomizer
US1632196A (en) * 1920-09-07 1927-06-14 Willys Overland Co Intake nozzle
US2073179A (en) * 1933-08-24 1937-03-09 Virgil H Kirkham Internal combustion engine
US2822253A (en) * 1955-05-16 1958-02-04 Richard E Caddock Liquid fuel collector and distributor ring for carburetors
US3457904A (en) * 1968-08-05 1969-07-29 Charles G Roberts Internal combustion engine with improved intake and exhaust

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1512952A (en) * 1919-06-30 1924-10-28 Advance Rumely Co Reatomizer
US1632196A (en) * 1920-09-07 1927-06-14 Willys Overland Co Intake nozzle
US1530157A (en) * 1921-10-17 1925-03-17 Charles W Gillett Reatomizer
US1526963A (en) * 1922-04-17 1925-02-17 Aquila D Chandler Revaporizer
US2073179A (en) * 1933-08-24 1937-03-09 Virgil H Kirkham Internal combustion engine
US2822253A (en) * 1955-05-16 1958-02-04 Richard E Caddock Liquid fuel collector and distributor ring for carburetors
US3457904A (en) * 1968-08-05 1969-07-29 Charles G Roberts Internal combustion engine with improved intake and exhaust

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4180029A (en) * 1976-12-29 1979-12-25 Toyota Jidosha Kogyo Kabushiki Kaisha 2-Cycle engine of an active thermoatmosphere combustion
FR2472671A1 (fr) * 1979-10-23 1981-07-03 Dresser Investments Procede et dispositif pour effectuer des economies de consommation par modification de l'ecoulement
US4756045A (en) * 1986-06-02 1988-07-12 Action Technology Vacuum cleaner hose having alternating height corrugations
DE4111772A1 (de) * 1991-04-11 1992-10-15 Kloeckner Humboldt Deutz Ag Ansaugsystem fuer eine selbstzuendende brennkraftmaschine
EP1540166A1 (fr) * 2002-07-18 2005-06-15 Kohler Co. Composant pour gerer le flux aerien dans un orifice de culasse et autour de celle-ci
EP1540166A4 (fr) * 2002-07-18 2008-06-18 Kohler Co Composant pour gerer le flux aerien dans un orifice de culasse et autour de celle-ci
US20060037577A1 (en) * 2004-08-17 2006-02-23 Dave Procknow Air flow arrangement for a reduced-emission single cylinder engine
US7086367B2 (en) * 2004-08-17 2006-08-08 Briggs & Stratton Corporation Air flow arrangement for a reduced-emission single cylinder engine
CN101131127B (zh) * 2006-08-24 2010-07-21 通用汽车环球科技运作公司 进气歧管调谐阀模糊逻辑诊断
US20100065004A1 (en) * 2008-09-12 2010-03-18 Gm Global Technology Operations, Inc. Mixture Motion Enhancing Intake Manifold Gasket
US8973905B2 (en) 2012-09-27 2015-03-10 Kohler Co. Venturi insert for a carburetor, and carburetor, system and apparatus incorporating the same

Also Published As

Publication number Publication date
FR2119776A5 (fr) 1972-08-04
DE2200818A1 (de) 1972-07-20
IT948154B (it) 1973-05-30

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