US20010003280A1 - Fuel injection - Google Patents
Fuel injection Download PDFInfo
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- US20010003280A1 US20010003280A1 US09/262,921 US26292199A US2001003280A1 US 20010003280 A1 US20010003280 A1 US 20010003280A1 US 26292199 A US26292199 A US 26292199A US 2001003280 A1 US2001003280 A1 US 2001003280A1
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- Prior art keywords
- fuel
- engine
- combustion chamber
- cloud
- injector
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Classifications
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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
- F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
- F02M69/04—Injectors peculiar thereto
- F02M69/042—Positioning of injectors with respect to engine, e.g. in the air intake conduit
- F02M69/044—Positioning of injectors with respect to engine, e.g. in the air intake conduit for injecting into the intake conduit downstream of an air throttle valve
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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
- F02B17/00—Engines characterised by means for effecting stratification of charge in cylinders
- F02B17/005—Engines characterised by means for effecting stratification of charge in cylinders having direct injection in the combustion chamber
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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
- F02M51/00—Fuel-injection apparatus characterised by being operated electrically
- F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
- F02M51/08—Injectors peculiar thereto with means directly operating the valve needle specially for low-pressure fuel-injection
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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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
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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
- F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
- F02M69/04—Injectors peculiar thereto
- F02M69/042—Positioning of injectors with respect to engine, e.g. in the air intake conduit
- F02M69/045—Positioning of injectors with respect to engine, e.g. in the air intake conduit for injecting into the combustion chamber
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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
- F02B75/00—Other engines
- F02B75/12—Other methods of operation
- F02B2075/125—Direct injection in the combustion chamber for spark ignition engines, i.e. not in pre-combustion chamber
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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
- F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
- F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
- F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
- F02B23/101—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder the injector being placed on or close to the cylinder centre axis, e.g. with mixture formation using spray guided concepts
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- 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 present invention relates to fuel injection in an internal combustion engine and more particularly to forming a cloud of fuel in such engines.
- Direct injection engines are aimed at improving fuel economy at low engine loads by providing a stratified charge in the combustion chamber.
- a stratified charge engine is one in which the combustion chamber contains stratified layers of different air/fuel mixtures. The strata closest to the spark plug contains a mixture slightly rich of stoichiometry, and subsequent strata contain progressively leaner mixtures. The overall air/fuel mixture within the combustion chamber is lean of stoichiometry, thereby improving overall fuel economy at low loads.
- high engine loads typically greater than 50% of full engine load, a homogeneous air-fuel mixture is provided in the combustion chamber.
- Conventional direct injection engines typically include a piston having a depression in the top face thereof (typically referred to as a bowl) and a swirl or tumble control valve located in the intake port to produce a swirl or tumble of the air entering the combustion chamber.
- a piston having a depression in the top face thereof (typically referred to as a bowl) and a swirl or tumble control valve located in the intake port to produce a swirl or tumble of the air entering the combustion chamber.
- the fuel impinges against the bottom of the bowl and cooperates with the motion of the air in the chamber to produce the stratified charge, with the richest portion of the charge moving toward the ignition source.
- the inventors of the present invention have recognized certain disadvantages with these prior art engines. For example, because the fuel sprayed from the fuel injector is directed toward the piston bowl, it is likely that a portion of the fuel will stick to the piston surface causing an undesirable wall-wetting condition. As the remainder of the fuel is burned, the flame propagating toward the piston surface is unable to completely burn the liquid fuel film on the piston surface. This results in undesirable soot formation during combustion.
- the inventors of the present invention have found that with bowl-in-piston engines, switching between a stratified charge and a homogeneous charge occurs at part loads ranging between 30% to 40% of full engine load. As the engine load increases, more fuel is required. However, because of the physical limitations of the bowl (i.e. the size of the bowl relative to the size of the combustion chamber), the amount of fuel that can be placed in the bowl and still attain a stratified charge is limited. Otherwise, the potential for wall wetting and subsequent soot formation may increase. As a result, above about 40% of full engine load, fuel economy is compromised.
- valve and intake port the fuel impinges on the valve and intake port.
- the valve and port may be cool and the fuel will not vaporize as desired, causing high HC emissions and soot.
- valve and port wetting by the fuel results in a longer response tome from the change of fuel injection pulse width to the change in fuel that enters the cylinder. This increases the difficulty in fuel metering control, fuel consumption, and HC/CO emissions.
- An object of the present invention is to provide a direct injection spark ignition engine which overcomes the disadvantages of prior technology. This object is achieved, and disadvantages of prior art approaches overcome, by providing a method of forming a fuel cloud in the combustion chamber using an impingement target immediately adjacent the fuel outlet of the fuel injector. The fuel strikes the target at a high velocity and forms a cloud of fuel thereabout. The fuel then remains suspended in the combustion chamber creating a relatively rich strata near the spark plug.
- An advantage of the present invention is that wall-wetting on the piston surface is reduced.
- Another, more specific, advantage of the present invention is that a near complete combustion occurs with little or no soot formation with low HC and NO x formation.
- Yet another advantage of the present invention is that a less complex engine is provided in that no bowl is required for the piston.
- Still another advantage of the present invention is that regulated emissions may be reduced.
- Another advantage of the present invention is that the engine load range in which a stratified charge may be produced is extended.
- FIGS. 1 and 2 are a diagrammatic cross-sectional representations of a direct injection engine according to the present invention.
- FIG. 3 is a diagrammatic cross-sectional representations of a port injection engine according to the present invention.
- FIGS. 4 - 5 are diagrammatic cross-sectional representations of a fuel injector according to the present invention.
- FIG. 6 is a diagrammatic representations of alternative fuel injector mounting according to the present invention.
- An internal combustion engine 10 includes a cylinder block 12 , having a cylinder bore 14 formed therein and a piston 16 reciprocally housed within the bore 14 .
- the piston 16 has a substantially flat top 18 , i.e. without a substantial piston bowl formed therein.
- a cylinder head 20 is attached to the block 12 and encloses a top end 22 of the bore 14 to form a combustion chamber 24 .
- the engine 10 is preferably a multi-valve engine having, for example, two intake ports and two exhaust ports. For the sake of clarity, only one intake port 26 is shown and is formed within the cylinder head 20 and communicates with the combustion chamber 24 through an intake valve 28 .
- An intake port 26 provides intake air within the combustion chamber 24 .
- the intake port 26 comprises a conventional intake port providing little or no swirl or tumble, although deactivation of one of the intake valves may produce some swirl motion.
- the intake port may be modified in a known manner to provide tumble and/or swirl motion as desired to promote flame propagation and combustion.
- a particular combustion chamber may work better with tumble and/or swirl motion to properly locate the cloud 80 —near the spark plug 30 for ignition.
- the engine 10 includes a spark plug 30 communicating with the combustion chamber 24 for igniting an air/fuel mixture within combustion chamber 24 .
- the engine 10 further includes a fuel injector 32 defining an axis 34 for injecting fuel directly into the combustion chamber 24 in FIGS. 1 - 2 and into the intake port in FIG. 3.
- the injector 32 is generally located along axis 36 of the cylinder 14 .
- the injector 32 need not be coincident with the axis 36 .
- the injector 32 may be mounted on the side of cylinder bore 14 , typically referred to as a side mounted injector, as shown in the example illustrated in FIG. 2.
- an injector 32 may be provided in an intake port as illustrated in FIG. 3 for a port fuel injected engine.
- the injector 32 includes tip 36 having an orifice 38 for injecting fuel from a fuel system (not shown) to the combustion chamber 24 .
- the injector 32 further includes an impingement surface 70 provided adjacent the orifice 38 .
- the impingement surface comprises a convex surface as illustrated in FIG. 4.
- the convex impingement surface 70 ′ has a recess 72 formed thereunder, forming a “mushroom-shaped” impingement surface 70 ′.
- FIGS. 4 and 5 illustrate the impingement surface provided on the injector 32 itself.
- impingement surface 70 may be formed in the engine itself, such as on the head (not shown), or provided in an insert 74 mounted to the engine, and preferably threadably engaged thereto.
- the injector 32 ′ is engaged with the insert 74 , preferably through a second threaded attachment.
- the engine 10 further includes a controller 40 (see FIG. 1) having a memory storage device 42 .
- a plurality of sensors 44 sense numerous engine operating parameters such as engine speed, engine load, spark timing, EGR rate, fuel delivery rate, engine air charge temperature, engine coolant temperature, intake manifold absolute pressure, the operating position of the throttle, vehicle gear selection, vehicle speed, intake manifold air mass flow rate, accelerator position, and other parameters known to those skilled in the art and suggested by this disclosure.
- the impingement surface 70 is preferably convex in cross section and preferably has a substantially spherical shape.
- shape of the impingement surface may be altered to include substantially flat or concave or conical, etc. surfaces and yet achieve some of the beneficial effects described herein, but the inventor has found the spherical shape, especially using the recess 74 , provides the most beneficial operation by minimizing wetting and maximizing fuel droplet dispersion and achieve the desired fuel penetration.
- the principle under which my invention works is as follows.
- the fuel is injected from the injector tip 36 at high speed.
- the impingement surface 70 is provided as close to the orifice 38 as possible to maximize the velocity at which the fuel strikes the surface 70 .
- the fuel slows prior to striking the surface 70 due to the air resistance met within the combustion chamber 24 and more fuel may be inclined to wet the surface 70 at lower reflex velocities.
- the inventor has found empirically that a commercially available fuel injector 32 having a 45 degree coangle injecting fuel at approximately 70 bar will properly strike a surface 70 positioned approximately 1.5 mm from the orifice 38 . At this distance, the fuel cone angle is such that almost all of the fuel stream strikes the surface 70 and is deflected thereby. Furthermore, the surface 70 is close to the injector, so the velocity of the stream is not significantly reduced before striking the surface 70 . Preferably the fuel leaves the injector 32 at approximately 60-100 m/s. Upon deflection, the fuel breaks into small droplets, promoting fast vaporization. The velocity of the deflected droplets is decreased from the injected velocity.
- the fuel is deflected into a cloud 80 , and the velocity of the fuel is reduced. This promotes a cloud 80 of small fuel droplets and vapor. If the surface 70 is positioned too close to the orifice 38 , the fuel will be deflected back toward the injector. If positioned too far from the orifice 38 , the fuel stream will not all strike the surface 70 as described above and a desired cloud 80 will not be formed, plus the velocity of the stream will be reduced prior to impacting the surface 70 and not deflect as desired.
- a Port Fuel Injection (PFI) application may use a similar system, preferably including an injector having a smaller injector coangle than a DI application, and therefore the cone angle may be significantly smaller than the 45 degrees described in the example above, perhaps as small as 10 or 15 degrees, and, depending on the distance the impingement surface is placed from the injector, the injector coangle may be as wide as 40 degrees or more.
- the velocity of the fuel from the injector in a PFI application is likely to be lower than the DI velocity, dependent again upon many factors. Initial tests show that a PFI injector may operate with a velocity range as low as about 20-40 m/s, and depending upon other factors as described above, this range may be expanded.
- An advantage of the present invention is that the fuel cloud 80 does not substantially strike the piston surface 18 , if at all.
- air is entrapped between the piston 16 and the cloud 80 , thereby forming a lean mixture above the piston.
- This enables lower hydrocarbon (HC) and soot production from the combustion process.
- the cloud 80 is pushed upwardly by the piston 16 during the compression stroke, and therefore a rich mixture is formed near the spark plug 30 , thereby enabling proper ignition and combustion. And this stratified operation enables lean operation in some instances.
- the injection may occur later in the cycle because the lower penetration will enable proper fuel mixture at the spark plug 30 . This also promotes lower levels of NO x production.
- the present invention when used in a DI application, does not require the fuel to be directed toward the spark plug 30 with the piston surface 18 , and therefore the location of the piston relative to the plug 30 is not critical to position fuel near the plug 30 .
- This is contrary to the applications where the fuel is injected onto the top of the piston and reflected by the shape of a bowl formed in the piston, as utilized for example in U.S. Pat. No. 5,553,588.
- the present invention therefore enables one to inject fuel later in the compression stroke, as it is not necessary to position the piston in the proper position to reflect the fuel, and the present invention may still also may eliminate piston wetting at such late injection.
- a direct injection engine is preferably run at approximately homogeneous charge.
- PFI Port Fuel Injection system
- fuel injector 32 injects fuel into the combustion chamber 24 at a predetermined velocity along axis 34 of injector 32 and at a predetermined initial cone angle.
- fuel is injected during the compression stroke at about 60° before top dead center.
- the fuel strikes the impingement surface 70 and forms a cloud 80 . Consequently, the injected fuel shallowly penetrates into combustion chamber 24 so as to float therein to reduce wall-wetting.
- piston 16 progressively compresses the air within combustion chamber 24 during the compression stroke, the cloud is urged toward the top 22 of the combustion chamber by the action of the substantially flat top piston 16 .
- the fuel thereby remains substantially unmixed with air inducted through intake port 26 , thereby producing the stratified charge in combustion chamber 24 .
- the piston motion causes the cloud 80 to engulf the spark plug 30 so that the fuel may be ignited.
- the droplet size for an undeflected fuel stream is between about 15 ⁇ m and about 25 ⁇ m approximately 45 mm away from the tip of the injector 32 with the surface 70 removed.
- the injection velocity of the fuel entering into the combustion chamber is between about 60 m/s and about 100 m/s, as measured along axis 34 of injector 32 .
- the initial cone angle ⁇ of fuel cone is between about 30° and about 60°, and preferably 45°. After deflection, the fuel droplet size is between approximately about 6 ⁇ m and about 12 ⁇ m.
- controller 40 controls a switch point for switching between a stratified charge produced in combustion chamber 24 , as described above, and a homogeneous charge.
- a switch point for switching between a stratified charge produced in combustion chamber 24 , as described above, and a homogeneous charge.
- changing between a stratified charge and a homogeneous charge may be accomplished by changing injection timing from the compression stroke to the intake stroke, for example.
- the switch point occurs at a point greater than about 50% of full engine load, and, more desirably, at a point between about 60% and about 70% of full engine load.
Abstract
A stratified charge is formed in an engine by injecting fuel at an impingement surface adjacent an outlet of the injector. The injected fuel thereby forms a cloud shallowly penetrating the combustion chamber so as to float therein to reduce wall-wetting and subsequent soot formation. A substantially flat top piston urges the cloud upwardly during a compression stroke of the engine. The cloud remains substantially unmixed with the inducted air, thereby producing the stratified charge. The continued motion of the piston causes the cloud to move toward the spark plug for ignition.
Description
- The present invention relates to fuel injection in an internal combustion engine and more particularly to forming a cloud of fuel in such engines.
- Direct injection engines are aimed at improving fuel economy at low engine loads by providing a stratified charge in the combustion chamber. A stratified charge engine is one in which the combustion chamber contains stratified layers of different air/fuel mixtures. The strata closest to the spark plug contains a mixture slightly rich of stoichiometry, and subsequent strata contain progressively leaner mixtures. The overall air/fuel mixture within the combustion chamber is lean of stoichiometry, thereby improving overall fuel economy at low loads. At high engine loads, typically greater than 50% of full engine load, a homogeneous air-fuel mixture is provided in the combustion chamber.
- Conventional direct injection engines typically include a piston having a depression in the top face thereof (typically referred to as a bowl) and a swirl or tumble control valve located in the intake port to produce a swirl or tumble of the air entering the combustion chamber. As fuel is injected into the combustion chamber, the fuel impinges against the bottom of the bowl and cooperates with the motion of the air in the chamber to produce the stratified charge, with the richest portion of the charge moving toward the ignition source.
- The inventors of the present invention have recognized certain disadvantages with these prior art engines. For example, because the fuel sprayed from the fuel injector is directed toward the piston bowl, it is likely that a portion of the fuel will stick to the piston surface causing an undesirable wall-wetting condition. As the remainder of the fuel is burned, the flame propagating toward the piston surface is unable to completely burn the liquid fuel film on the piston surface. This results in undesirable soot formation during combustion.
- In addition, because the design of these engines relies on the fuel impinging against the bowl and subsequently directed toward the spark plug, fuel injection timing is of a major concern. In direct injection engines, fuel injection is a function of time whereas the motion of the piston is a function of crank angle. In port injected engines, fuel entering the chamber is a function of crank angle because the opening of the intake valve is a function of crank angle. As a result, it is imperative to control the timing of fuel injection in a direct injection engine so that the injected fuel may impinge on the bowl at the proper time and the fuel cloud may move toward the spark plug. In other words, if the fuel is injected too early, the spray may miss the bowl entirely, thereby not deflecting toward the spark plug. If the fuel is injected too late, then excess wall-wetting may occur.
- Further, the inventors of the present invention have found that with bowl-in-piston engines, switching between a stratified charge and a homogeneous charge occurs at part loads ranging between 30% to 40% of full engine load. As the engine load increases, more fuel is required. However, because of the physical limitations of the bowl (i.e. the size of the bowl relative to the size of the combustion chamber), the amount of fuel that can be placed in the bowl and still attain a stratified charge is limited. Otherwise, the potential for wall wetting and subsequent soot formation may increase. As a result, above about 40% of full engine load, fuel economy is compromised.
- Other disadvantages with prior art engines results in a heavier piston, increased engine height to accommodate the larger piston, a larger combustion chamber surface to volume ratio, more heat loss, and increased charge heating during the intake and compression strokes, which increases the tendency for engine knocking.
- Furthermore, with port injection, the fuel impinges on the valve and intake port. At cold startup, the valve and port may be cool and the fuel will not vaporize as desired, causing high HC emissions and soot. During transient conditions, valve and port wetting by the fuel results in a longer response tome from the change of fuel injection pulse width to the change in fuel that enters the cylinder. This increases the difficulty in fuel metering control, fuel consumption, and HC/CO emissions.
- In copending application, Ser. No. 08/925,131, ('131 application) assigned to the assignee of the present invention, and which is incorporated herein by reference in its entirety, a fuel cloud is directly injected into a combustion chamber. The present invention is directed, in part, at improving the formation of a cloud of fuel in the combustion chamber.
- An object of the present invention is to provide a direct injection spark ignition engine which overcomes the disadvantages of prior technology. This object is achieved, and disadvantages of prior art approaches overcome, by providing a method of forming a fuel cloud in the combustion chamber using an impingement target immediately adjacent the fuel outlet of the fuel injector. The fuel strikes the target at a high velocity and forms a cloud of fuel thereabout. The fuel then remains suspended in the combustion chamber creating a relatively rich strata near the spark plug.
- An advantage of the present invention is that wall-wetting on the piston surface is reduced.
- Another, more specific, advantage of the present invention is that a near complete combustion occurs with little or no soot formation with low HC and NOx formation.
- Yet another advantage of the present invention is that a less complex engine is provided in that no bowl is required for the piston.
- Still another advantage of the present invention is that regulated emissions may be reduced.
- Another advantage of the present invention is that the engine load range in which a stratified charge may be produced is extended.
- Other objects, features and advantages of the present invention will be readily appreciated by the reader of this specification.
- The invention will now be described, by way of example, with reference to the accompanying drawings, in which:
- FIGS. 1 and 2 are a diagrammatic cross-sectional representations of a direct injection engine according to the present invention;
- FIG. 3 is a diagrammatic cross-sectional representations of a port injection engine according to the present invention;
- FIGS.4-5 are diagrammatic cross-sectional representations of a fuel injector according to the present invention; and,
- FIG. 6 is a diagrammatic representations of alternative fuel injector mounting according to the present invention.
- An
internal combustion engine 10 according to the present invention, as shown in FIGS. 1-3, includes acylinder block 12, having acylinder bore 14 formed therein and apiston 16 reciprocally housed within thebore 14. Thepiston 16 has a substantiallyflat top 18, i.e. without a substantial piston bowl formed therein. Acylinder head 20 is attached to theblock 12 and encloses atop end 22 of thebore 14 to form acombustion chamber 24. Theengine 10 is preferably a multi-valve engine having, for example, two intake ports and two exhaust ports. For the sake of clarity, only oneintake port 26 is shown and is formed within thecylinder head 20 and communicates with thecombustion chamber 24 through anintake valve 28. - An
intake port 26 provides intake air within thecombustion chamber 24. In a preferred embodiment, theintake port 26 comprises a conventional intake port providing little or no swirl or tumble, although deactivation of one of the intake valves may produce some swirl motion. One skilled in the art appreciates that the intake port may be modified in a known manner to provide tumble and/or swirl motion as desired to promote flame propagation and combustion. Furthermore, a particular combustion chamber may work better with tumble and/or swirl motion to properly locate thecloud 80—near thespark plug 30 for ignition. - The
engine 10 includes aspark plug 30 communicating with thecombustion chamber 24 for igniting an air/fuel mixture withincombustion chamber 24. Theengine 10 further includes afuel injector 32 defining anaxis 34 for injecting fuel directly into thecombustion chamber 24 in FIGS. 1-2 and into the intake port in FIG. 3. In the example of FIG. 1, theinjector 32 is generally located alongaxis 36 of thecylinder 14. However, theinjector 32 need not be coincident with theaxis 36. In fact, theinjector 32 may be mounted on the side ofcylinder bore 14, typically referred to as a side mounted injector, as shown in the example illustrated in FIG. 2. Likewise, aninjector 32 may be provided in an intake port as illustrated in FIG. 3 for a port fuel injected engine. - As shown in FIG. 4, the
injector 32 includestip 36 having anorifice 38 for injecting fuel from a fuel system (not shown) to thecombustion chamber 24. Theinjector 32 further includes animpingement surface 70 provided adjacent theorifice 38. Preferably the impingement surface comprises a convex surface as illustrated in FIG. 4. In a further embodiment illustrated in FIG. 5, theconvex impingement surface 70′ has arecess 72 formed thereunder, forming a “mushroom-shaped”impingement surface 70′. The embodiments of FIGS. 4 and 5 illustrate the impingement surface provided on theinjector 32 itself. One skilled in the art appreciates theimpingement surface 70 may be formed in the engine itself, such as on the head (not shown), or provided in aninsert 74 mounted to the engine, and preferably threadably engaged thereto. Theinjector 32′ is engaged with theinsert 74, preferably through a second threaded attachment. - The
engine 10 further includes a controller 40 (see FIG. 1) having amemory storage device 42. A plurality ofsensors 44 sense numerous engine operating parameters such as engine speed, engine load, spark timing, EGR rate, fuel delivery rate, engine air charge temperature, engine coolant temperature, intake manifold absolute pressure, the operating position of the throttle, vehicle gear selection, vehicle speed, intake manifold air mass flow rate, accelerator position, and other parameters known to those skilled in the art and suggested by this disclosure. - As described above, the
impingement surface 70 is preferably convex in cross section and preferably has a substantially spherical shape. One skilled in the art appreciates that the shape of the impingement surface may be altered to include substantially flat or concave or conical, etc. surfaces and yet achieve some of the beneficial effects described herein, but the inventor has found the spherical shape, especially using therecess 74, provides the most beneficial operation by minimizing wetting and maximizing fuel droplet dispersion and achieve the desired fuel penetration. - The principle under which my invention works is as follows. The fuel is injected from the
injector tip 36 at high speed. Theimpingement surface 70 is provided as close to theorifice 38 as possible to maximize the velocity at which the fuel strikes thesurface 70. As one positions the surface further from theorifice 38, the fuel slows prior to striking thesurface 70 due to the air resistance met within thecombustion chamber 24 and more fuel may be inclined to wet thesurface 70 at lower reflex velocities. - The inventor has found empirically that a commercially
available fuel injector 32 having a 45 degree coangle injecting fuel at approximately 70 bar will properly strike asurface 70 positioned approximately 1.5 mm from theorifice 38. At this distance, the fuel cone angle is such that almost all of the fuel stream strikes thesurface 70 and is deflected thereby. Furthermore, thesurface 70 is close to the injector, so the velocity of the stream is not significantly reduced before striking thesurface 70. Preferably the fuel leaves theinjector 32 at approximately 60-100 m/s. Upon deflection, the fuel breaks into small droplets, promoting fast vaporization. The velocity of the deflected droplets is decreased from the injected velocity. The fuel is deflected into acloud 80, and the velocity of the fuel is reduced. This promotes acloud 80 of small fuel droplets and vapor. If thesurface 70 is positioned too close to theorifice 38, the fuel will be deflected back toward the injector. If positioned too far from theorifice 38, the fuel stream will not all strike thesurface 70 as described above and a desiredcloud 80 will not be formed, plus the velocity of the stream will be reduced prior to impacting thesurface 70 and not deflect as desired. - One skilled in the art appreciates that a Port Fuel Injection (PFI) application may use a similar system, preferably including an injector having a smaller injector coangle than a DI application, and therefore the cone angle may be significantly smaller than the 45 degrees described in the example above, perhaps as small as 10 or 15 degrees, and, depending on the distance the impingement surface is placed from the injector, the injector coangle may be as wide as 40 degrees or more. Likewise, the velocity of the fuel from the injector in a PFI application is likely to be lower than the DI velocity, dependent again upon many factors. Initial tests show that a PFI injector may operate with a velocity range as low as about 20-40 m/s, and depending upon other factors as described above, this range may be expanded.
- One skilled in the art appreciates that a number of variable affect the stream coming from the injector and therefore the numbers described above are representative for a particular embodiment. For example, if the pressure in the combustion chamber is increased, the diameter of the stream may be reduced (this effect is less as one is closer to the injector). Likewise, all other things being equal, a lower injector angle will produce a narrower stream. In this case, one skilled in the art appreciates the
surface 70 may be smaller or further positioned from theorifice 38, depending on several variables, including those described above. - An advantage of the present invention is that the
fuel cloud 80 does not substantially strike thepiston surface 18, if at all. Thus, air is entrapped between thepiston 16 and thecloud 80, thereby forming a lean mixture above the piston. This enables lower hydrocarbon (HC) and soot production from the combustion process. Similarly, thecloud 80 is pushed upwardly by thepiston 16 during the compression stroke, and therefore a rich mixture is formed near thespark plug 30, thereby enabling proper ignition and combustion. And this stratified operation enables lean operation in some instances. Furthermore, the injection may occur later in the cycle because the lower penetration will enable proper fuel mixture at thespark plug 30. This also promotes lower levels of NOx production. - The present invention, when used in a DI application, does not require the fuel to be directed toward the
spark plug 30 with thepiston surface 18, and therefore the location of the piston relative to theplug 30 is not critical to position fuel near theplug 30. This is contrary to the applications where the fuel is injected onto the top of the piston and reflected by the shape of a bowl formed in the piston, as utilized for example in U.S. Pat. No. 5,553,588. The present invention therefore enables one to inject fuel later in the compression stroke, as it is not necessary to position the piston in the proper position to reflect the fuel, and the present invention may still also may eliminate piston wetting at such late injection. Furthermore, at high load, a direct injection engine is preferably run at approximately homogeneous charge. In such a case, fuel is injected after about 100 crank angle degrees after top dead center of the intake stroke. A nearly homogeneous charge may thereby be formed in the combustion chamber, but the cloud will result in a leaner mixture near the bottom of the combustion chamber. This reduces hydrocarbon loading at the piston/linear crevices and thereby improves emissions. - Similarly, in a Port Fuel Injection system (PFI), emissions are improved. In the PFI engine, the charge is substantially homogeneous under most operating conditions. The impingement improves the fuel penetration and valve wetting is reduced or eliminated. Therefore, the engine may employ open-valve injection to improve cold start and transient operation.
- According to the present invention,
fuel injector 32 injects fuel into thecombustion chamber 24 at a predetermined velocity alongaxis 34 ofinjector 32 and at a predetermined initial cone angle. In one embodiment, fuel is injected during the compression stroke at about 60° before top dead center. The fuel strikes theimpingement surface 70 and forms acloud 80. Consequently, the injected fuel shallowly penetrates intocombustion chamber 24 so as to float therein to reduce wall-wetting. Aspiston 16 progressively compresses the air withincombustion chamber 24 during the compression stroke, the cloud is urged toward the top 22 of the combustion chamber by the action of the substantially flattop piston 16. The fuel thereby remains substantially unmixed with air inducted throughintake port 26, thereby producing the stratified charge incombustion chamber 24. Further, the piston motion causes thecloud 80 to engulf thespark plug 30 so that the fuel may be ignited. - In a preferred embodiment, the droplet size for an undeflected fuel stream, as measured by the Sauter Mean Diameter method, is between about 15 μm and about 25 μm approximately 45 mm away from the tip of the
injector 32 with thesurface 70 removed. The injection velocity of the fuel entering into the combustion chamber is between about 60 m/s and about 100 m/s, as measured alongaxis 34 ofinjector 32. Also, the initial cone angle θ of fuel cone is between about 30° and about 60°, and preferably 45°. After deflection, the fuel droplet size is between approximately about 6 μm and about 12 μm. - The effects of having such a shallowly penetrating fuel injected from
fuel injector 34 is clearly shown in the graphs of FIGS. 3-5 of the '131 application. In the '131 application, the benefits of vaporization and formation of a stratified charge are discussed in detail and therefore not presented here. - According to the present invention,
controller 40 controls a switch point for switching between a stratified charge produced incombustion chamber 24, as described above, and a homogeneous charge. Those skilled in the art will recognize in view of this disclosure that changing between a stratified charge and a homogeneous charge may be accomplished by changing injection timing from the compression stroke to the intake stroke, for example. The switch point occurs at a point greater than about 50% of full engine load, and, more desirably, at a point between about 60% and about 70% of full engine load. This is due to the fact that a stratified charge may be produced incombustion chamber 24, as described above, with a relatively large amount of fuel being delivered therein without the potential for wall wetting and subsequent soot formation because the charge is not constrained by a bowl formed inpiston surface 18 of a limited volume, but rather is constrained by the entire volume ofcombustion chamber 24. - While the best mode for carrying out the invention has been described in detail, those skilled in the art to which this invention relates will recognize various alternative designs and embodiments, including those mentioned above, in practicing the invention that has been defined by the following claims.
Claims (30)
1. A method of forming a combustible fuel mixture for a spark ignition internal combustion engine, the engine having a cylinder block with a plurality of cylinder bores formed therein, the cylinder bore defining a longitudinal axis, a plurality of substantially flat top pistons each reciprocally housed within a cylinder bore, a cylinder head attached to the block and closing top ends of the bores to form a plurality of combustion chambers, an intake port formed in the cylinder head and communicating with the combustion chamber via an intake valve for introducing air into the combustion chamber, a fuel injector, defining an axis and communicating with the combustion chamber, for supplying fuel into the combustion chamber, and an ignition source communicating with the combustion chamber for igniting fuel within the combustion chamber, with said method comprising the steps of:
injecting fuel from the fuel injector having an outlet into the engine at a predetermined velocity and forming said injected fuel with spray jet having a predetermined initial cone angle, with said injected fuel impinging on a surface adjacent the outlet of said injector thereby forming a cloud shallowly penetrating the combustion chamber so as to float therein to reduce wall wetting;
urging said cloud upwardly in said combustion chamber with said substantially flat top piston during a compression stroke of the engine.
2. A method according to wherein said predetermined velocity is between about 60 m/s and about 100 m/s along the axis of the fuel injector.
claim 1
3. A method according to wherein said predetermined initial cone angle is between about 30° and about 60°.
claim 1
4. A method according to wherein an amount of fuel vaporized into said cloud relative to the amount of fuel injected is greater than about 95%.
claim 1
5. A method according to wherein said mixture comprises a stratified mixture and said cloud defines a relatively rich region and the remainder of the volume of the combustion chamber defines a lean region, with said fuel remaining substantially unmixed with said inducted air, thereby producing said stratified charge and said piston moves said cloud toward said ignition source.
claim 1
6. A method according to wherein said engine comprises a direct injection engine.
claim 5
7. A fuel injected, spark ignition internal combustion engine comprising:
a cylinder block;
a cylinder bore formed in said cylinder block, with said bore defining a longitudinal axis and having a top end;
a cylinder head attached to said block and closing said top end of said bore to form a combustion chamber;
an intake port formed in said cylinder head and communicating with said combustion chamber via an intake valve for inducting air into said combustion chamber;
a fuel injector, defining an axis, for injecting fuel into said combustion chamber, said injector having an outlet for injecting said fuel at a predetermined velocity and formed into a cone having a predetermined initial cone angle;
an impingement surface provided adjacent said outlet of said injector, with said injected fuel striking said impingement surface thereby forming a fuel cloud for shallowly penetrating into said combustion chamber so as to float therein to reduce wall wetting; and
a substantially flat top piston reciprocally housed within a said bore.
8. An engine according to wherein said fuel is formed into a droplet size is between about 6 μm and about 12 μm after striking said impingement surface.
claim 7
9. An engine according to wherein said predetermined initial cone angle is between about 30° and about 60°.
claim 8
10. An engine according to wherein said predetermined velocity is between about 60 m/s and about 100 m/s along said axis of said fuel injector.
claim 9
11. An engine according to wherein an amount of fuel vaporized into said cloud relative to the amount of fuel injected is greater than about 95%.
claim 7
12. An engine according to wherein said fuel remains substantially unmixed with said inducted air, thereby producing a stratified charge and wherein said cloud defines a relatively rich region and the remainder of the volume of the combustion chamber defines a lean region, with said substantially flat top piston urging said cloud upwardly during a compression stroke of the engine and an ignition source communicates with said combustion chamber, with said cloud engulfing said ignition source so that said fuel is ignitable by said ignition source.
claim 7
13. An engine according to further comprising an engine controller, with said engine controller being responsive to a plurality of engine operating parameters, with said controller causing a switch between a stratified charge and a homogeneous charge formed within the combustion chamber, with said switch occurring at an engine load of greater than about 50% of full engine load.
claim 12
14. An engine according to , wherein said impingement surface comprises a substantially spherical surface positioned adjacent the outlet of said injector so substantially all of said jet strikes said surface.
claim 7
15. An engine according to , wherein said impingement surface is positioned approximately 1.25 mm from said injector outlet.
claim 14
16. An engine according to , wherein said impingement surface has a spherical diameter of approximately 3 mm.
claim 15
17. An engine according to , wherein said impingement surface has a recess formed thereunder.
claim 16
18. An engine according to , wherein said engine comprises a direct injection engine.
claim 17
19. An engine according to , wherein said engine operates with a stratified charge.
claim 18
20. An engine according to , wherein said engine comprises a port injection engine.
claim 17
21. An engine according to , wherein said engine operates with a substantially homogeneous charge.
claim 20
22. A stratified charge, direct injection, spark ignition internal combustion engine comprising:
a cylinder block;
a cylinder bore formed in said cylinder block, with said bore defining a longitudinal axis and having a top end;
a cylinder head attached to said block and closing said top end of said bore to form a combustion chamber;
an intake port formed in said cylinder head and communicating with said combustion chamber via an intake valve for inducting air into said combustion chamber;
a fuel injector, defining an axis, for injecting fuel directly into said combustion chamber at a predetermined velocity and having a spray jet exiting an outlet of the injector;
an impingement surface positioned adjacent said outlet of said injector, said impingement surface having a size and positioned in close proximity to said outlet so substantially all of said jet strikes said surface, with said injected fuel thereby shallowly penetrating into said combustion chamber so as to form a cloud and float therein to reduce wall wetting;
a substantially flat top piston reciprocally housed within said bore, with said substantially flat top piston causing said injected fuel to move upwardly during a compression stroke of the engine, with said fuel remaining substantially unmixed with said inducted air, thereby producing said stratified charge; and,
an ignition source communicating with said combustion chamber, with said cloud engulfing said ignition source so that said fuel is ignitable by said ignition source.
23. An engine according to , wherein said impingement surface comprises a substantially spherical surface.
claim 22
24. An engine according to , wherein said impingement surface has a diameter of approximately 2.5 mm and is positioned approximately 1.25 mm from said outlet.
claim 23
25. An engine according to wherein said impingement surface is provided on said engine head.
claim 24
26. An engine according to wherein said impingement surface is provided on said injector.
claim 24
27. An engine according to , wherein said impingement surface has a recess formed thereunder.
claim 24
28. An engine according to wherein said fuel is injected at approximately 100 degrees after intake.
claim 24
29. An engine according to wherein an amount of fuel vaporized into said cloud relative to the amount of fuel injected is greater than about 95%.
claim 24
30. An engine according to further comprising an engine controller, with said engine controller being responsive to a plurality of engine operating parameters, with said controller causing a switch between a stratified charge and a homogeneous charge formed within said combustion chamber, with said switch occurring at an engine load between about 60% and about 70% of full engine load.
claim 24
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/262,921 US6386175B2 (en) | 1999-03-05 | 1999-03-05 | Fuel injection |
EP00301631A EP1035321B1 (en) | 1999-03-05 | 2000-02-29 | Fuel injection |
DE60025305T DE60025305D1 (en) | 1999-03-05 | 2000-02-29 | Fuel injection |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/262,921 US6386175B2 (en) | 1999-03-05 | 1999-03-05 | Fuel injection |
Publications (2)
Publication Number | Publication Date |
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US20010003280A1 true US20010003280A1 (en) | 2001-06-14 |
US6386175B2 US6386175B2 (en) | 2002-05-14 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/262,921 Expired - Lifetime US6386175B2 (en) | 1999-03-05 | 1999-03-05 | Fuel injection |
Country Status (3)
Country | Link |
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US (1) | US6386175B2 (en) |
EP (1) | EP1035321B1 (en) |
DE (1) | DE60025305D1 (en) |
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US10683816B2 (en) | 2012-12-07 | 2020-06-16 | Ethanol Boosting Systems, Llc | Port injection system for reduction of particulates from turbocharged direct injection gasoline engines |
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US11624328B2 (en) | 2012-12-07 | 2023-04-11 | Ethanol Boosting Systems, Inc. | Port injection system for reduction of particulates from turbocharged direct injection gasoline engines |
US11959428B2 (en) | 2012-12-07 | 2024-04-16 | Ethanol Boosting Systems, Llc | Port injection system for reduction of particulates from turbocharged direct injection gasoline engines |
US11015493B2 (en) * | 2014-02-14 | 2021-05-25 | Eaton Intelligent Power Limited | Rocker arm assembly for engine braking |
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Also Published As
Publication number | Publication date |
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DE60025305D1 (en) | 2006-03-30 |
EP1035321A3 (en) | 2001-05-30 |
EP1035321A2 (en) | 2000-09-13 |
US6386175B2 (en) | 2002-05-14 |
EP1035321B1 (en) | 2006-01-04 |
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