FUEL MIXTURE SYSTEM AND ASSEMBLY

Abstract

A system and attendant structural assembly operative to establish a coordinated mixture of gaseous and distillate fuels for an engine including an electronic control unit (ECU) operative to monitor predetermined engine data determinative of engine fuel requirements and structured to regulate ratios of the gaseous and distillate fuel of an operative fuel mixture for the engine. The system and assembly includes at least one mixing assembly comprising an integrated throttle body and air gas mixer directly connected to one another, wherein the throttle body is disposed in fluid communication with a pressurized gaseous fuel supply and the air gas mixer is disposed in fluid communication with a flow of intake air to a combustion section of the engine. In use, the throttle body is structured to direct a variable gaseous fuel flow directly to the air gas mixer for dispensing into the intake air flow to the combustion section.

Description

CLAIM OF PRIORITY

The present application is a continuation-in-part application of previously filed, now pending application having Ser. No. 13/947,410, filed on Jul. 22, 2013.

BACKGROUND OF THE INVENTION

1. Field of the Invention

This invention is directed to a system and attendant apparatus operative to establish a variable operative fuel mixture for powering a stationary engine or generator, as well as a vehicle engine. The operative fuel mixture may comprise a varying ratio of both a gaseous fuel, such as natural gas, and a distillate fuel, such as diesel. The ratio of gaseous and distillate fuel is dependent, at least in part, on a plurality of operating characteristics of the engine, which are monitored by an electronic control unit (ECU). The system is adaptable for determining an efficient and effective operative fuel mixture due at least partially to the inclusion of one or more mixing assemblies each comprising and integrated throttle body and air-gas mixer.

2. Description of the Related Art

Typically large, stationary engines as well as mobile engines used to power heavy duty industrial vehicles are powered by either direct drive diesel or diesel electric power trains frequently including a multiple horse power turbo charged operation.

Accordingly, it is well recognized that distillate fuels, specifically diesel, are used as the primary fuel source for such engines. Attempts to maximize the operational efficiency, while maintaining reasonable safety standards, have previously involved modified throttle control facilities. These attempts serve to diminish adverse effects of control mechanisms which may be potentially harmful to the engine operation and may also be at least generally uneconomical. Typical adverse effects include increased fuel consumption and wear on operative components. Therefore, many diesel engines are expected to accommodate various types of high capacity loads and provide maximum power for relatively significant periods of operation. As a result, many diesel engines are commonly operated at maximum or near maximum capacity resulting in an attempted maximum power delivery from the engine and consequent high rates of diesel consumption. It is generally recognized that the provision of a substantially rich fuel mixture in the cylinders of a diesel engine is necessary for providing maximum power when required. Such continued high capacity operation of the engine results not only in wear on the engine components, but also in high fuel consumption rates, lower operating efficiencies, more frequent oil changes and higher costs of operation.

Accordingly, there is a long recognized need for a fuel control system specifically intended for use with high capacity, variable or constant speed compression ignition engines that would allow the use of more efficient fueling methods using other commonly available fuel sources. Therefore, an improved fuel control system is proposed which is determinative of an effective and efficient operative fuel mixture comprised of a combination of gaseous and distillate fuels. More specifically, gaseous fuels can comprise a natural gas or other appropriate gaseous type fuels, wherein distillate fuel would typically include, but not be limited to diesel fuel.

Such a preferred and proposed fuel control system should be capable of regulating the composition of the operative fuel mixture on which the engine operates to include 100% distillate fuel, when the operating mode(s) thereof clearly indicate that the combination of gaseous and distillate fuels is not advantageous. Further, such a proposed fuel control system could have an included secondary function to act as a general safety system serving to monitor critical engine operating parameters. As a result, control facilities associated with such a preferred fuel control system should allow for discrete, user defined control and safety set points for various engine and/or fuel system parameters.

In order to enhance efficient operation of an engine it is known to use a mass air flow sensor to determine the mass flow rate of air entering an internal combustion engine. It is known that air changes its density as it expands and contracts with temperature and pressure. As a result, it has been found that the determination of mass air flow is more appropriate than volumetric flow sensors for accurately determining the quantity of intake air delivered to the combustion section of the engine.

In the proper operation of CI engines, other factors to be considered include, but are not limited to, the occurrence of engine knocking. Knocking is a common occurrence in diesel engines where fuel is injected into highly compressed air at the end of the compression stroke. There is a short lag between the fuel being injected and combustion starting. Typically there is a quantity of fuel in the combustion chamber which will be ignited first in areas of greater oxygen density prior to the combustion of the complete fuel charge. A sudden increase in pressure and temperature may cause what has been recognized as a distinctive diesel “knock” or “clatter”.

Yet another factor to be considered in the effective and efficient performance of CI engines is “flammability limits”. Flammability limits refer to the fact that mixtures of gaseous fuel and air will only burn if the fuel concentration lies within well defined limits. The terms “flammability limits” and “explosive limits” are used interchangeably and recognized flammability limits are typically determined experimentally. Maintaining a preferred combination of fuel and air in an explosive mixture is important in internal combustion engines specifically including, but not limited to, CI engines or diesel engines. In addition, it is important to maintain the air fuel mixture below “lower flammability limits” prior to the delivery of the air fuel mixture into the combustion chambers in order to avoid or restrict pre-ignition and resultant damage to the engine.

SUMMARY OF THE INVENTION

This invention is directed to a system and included apparatus, comprising technology that allows for the safe and efficient use of a gaseous fuel such as, but not limited to, natural gas, in combination with a predetermined quantity of conventional distillate fuel, such as diesel fuel. As a result, the composition of an “operative fuel mixture” used to power an associated engine will, dependent on the operating modes and/or operating characteristics thereof, be either a combined mixture of gaseous fuel and distillate fuel or substantially entirely distillate fuel, absent any contribution of gaseous fuel.

Moreover, the fuel control system of the present invention incorporates “real time” measurement capabilities specifically, but not exclusively, of each of the gaseous fuel and distillate fuel and the operative fuel mixture. More specifically, metering technology appropriate to each of the gaseous and distillate fuels will be used to establish the percentage of gaseous fuel and diesel fuel contained in the composition of the operative fuel mixture. Such appropriate metering will also facilitate the tracking of the overall gaseous fuel and diesel fuel consumption.

Accordingly, the system of at least one preferred embodiment of the present invention includes both controlling and safety features, specifically adaptable for use with compression ignition engines (CI), of the type more fully described herein. It is to be noted that the term “operative fuel mixture” may, as set forth above, include a composition composed of both gaseous fuel and distillate fuel present in varying ratios. However, for purposes of clarity, the term “operative fuel mixture” may also specifically refer to a composition comprised substantially entirely of the distillate fuel. Therefore, and as set forth in greater detail hereinafter, the composition of the operative fuel mixture may best comprise both gaseous fuel and distillate fuel in predetermined quantities, wherein the ratio of the gaseous and distillate fuels may vary. It is again emphasized, that the term “gaseous fuel” is meant to include natural gas or other gaseous type fuels appropriate for engine operation. Similarly, the term “distillate fuel” refers primarily, but not exclusively, to a diesel fuel.

The system and assembly of the present invention allows operators of stationary engines, including electric power generators and/or vehicle mounted engines, to substantially reduce costs, extend run time and improve sustainability by substituting natural gas or other gaseous fuel for a portion of the distillate fuel, such as diesel fuel in predetermined ratios. As a result, safe use of a natural gas and other gaseous fuel is used in place of distillate fuel with the combined ratios of an “operative gas mixture” in the range of 50% to 70% of the engines total fuel requirement. Importantly, generators or other stationary engines converted with the system and assembly of the present invention exhibit diesel like performance in such critical areas as load acceptance, power output, stability and efficiency.

Additional advantages of the system and assembly of the present invention allow for the onsite conversion of stationary or mobile engines to natural gas and/or diesel fuel operation. The installation and/or conversion process utilizes components that are installed externally of the engine/generator in a manner which does not require any changes or modifications to the combustion section thereof. As such, OEM combustion section components including cylinders, pistons, fuel injectors and/or cylinder heads remain the same. By retaining the OEM diesel or distillate fuel system in its entirety, the operative and structural features of the present invention maintains the engines capability to operate solely on diesel fuel when such is needed based on the operational modes or operating characteristics of the engine.

Moreover, the present invention utilizes “pipe-line supplied gaseous fuel” at a positive pressure, generally in the range of 3 psi to 7 psi. Accordingly, gaseous fuel is added to the intake air of the combustion section of the engine, at a positive pressure, utilizing one or more unique mixing assemblies. In more specific terms, each of the one or more mixing assemblies includes an electronically controlled throttle body integrated with a fixed geometry, low restriction air gas mixture. In terms of the integrated features of the throttle body and corresponding air gas mixer, the air gas mixer comprises a housing wherein the throttle body is fixedly mounted on or connected directly to the housing of the corresponding air gas mixer, such as on the exterior thereof. In addition, at least a portion of the housing of the air gas mixer is disposed in and thereby may at least partially define a path of travel or flow line of intake air to the combustion section of the engine. Moreover, a dispensing nozzle is disposed within the interior of the housing in direct communication and/or aligned relation within the flow path of the intake air. Further, a delivery conduit is disposed on the interior of the housing of the air gas mixer in interconnecting, gaseous fuel delivering relation between the throttle body and the dispensing nozzle.

As indicated, the supply of gaseous fuel is maintained at a positive pressure and delivered from the fuel supply to the throttle body and eventually from the throttle body to the corresponding, integrated air gas mixer at such positive pressure. Therefore, the gaseous fuel supply, throttle body and integrated air gas mixer are cooperatively structured and collectively operative to deliver gaseous fuel in appropriate, variable quantities and under a positive pressure to the intake air of the combustion section of the engine. This may differ from conventional fuel systems, wherein fuel is not maintained under a positive pressure or “pushed” from a fuel delivery assembly into the flow path of intake air. Moreover, one advantageous feature of the positive pressure delivery of the gaseous fuel of the present invention comprises the ability to “predict” and/or more precisely control the quantity of gaseous fuel being delivered to the flow of intake air and to the combustion section of the engine. As a result the maximum amount of gaseous fuel, within predetermined limits or parameters, may be added to the gaseous and distillate fuel mixture of the operative fuel composition and thereby assure efficient operation of the engine without consuming an excessive amount of distillate fuel. Factors which may limit the delivery of the maximum quantity of gaseous fuel, as set forth above may include, but are not limited to, the occurrence of “knocking” in the engine, maintaining appropriate lower flammability limits, etc.

Further direct mounting or connection of the throttle body to the integrated air gas mixer provides an additional safety feature. More specifically, due to such an integrated structure, there will not be a collection of gaseous fuel in a connecting conduit or line, between throttle body and air gas mixer and/or intake air, which may exist in conventional fuel systems. Therefore, unlike conventional fuel delivery connections, the gaseous fuel of the present invention may be “pushed” under the aforementioned positive pressure from the throttle body directly into the air gas mixer.

Dependent on the structural and operative features of the engine and/or generator with which the system and included structure is utilized, a turbo charger may be disposed within one or more intake air flow paths to the combustion chamber. When one or more turbochargers are so utilized and installed, the integrated throttle body and air gas mixer are disposed in fluid communication with the corresponding flow path upstream of the turbocharger. In yet another preferred embodiment of the system and assembly of the present invention a plurality of mixing assemblies are utilized, wherein each mixing assembly comprises an integrated throttle body and air gas mixer. As set forth above, the structural integration of each of the throttle body and corresponding air gas mixer comprises the air gas mixer including a housing disposed at least partially within and thereby at least partially defining the intake air flow path to the combustion section of the engine. Further, each throttle body will be fixedly mounted on or directly connected to the corresponding, integrated air gas mixer, such as on the housing thereof, to at least partially define the integrated structure thereof. The result of this integrated structure will be the advantages and enhanced operative features, as set forth above.

As also indicated, each of the throttle bodies are independently operable based on monitored data determined by the ECU. As a result, each of a plurality of integrated throttle bodies/air gas mixers may provide a different and variable gaseous fuel flow to a different intake air flow path and corresponding combustion cylinder of the combustion section of the engine. Therefore, each combustion cylinder associated with the engine/generator with which the system of the present invention is utilized, may receive a gaseous fuel and distillate fuel mixture which differs from one or more of the other cylinders, depending upon the operating characteristics of the engine. This allows for even greater efficiency in regulating output of the engine based on operating characteristics of the engine, as detected by the monitoring capabilities of the ECU. Such engine operating characteristics include, but are not limited to, fuel rates, exhaust gas temperatures, vibrations levels, manifold air temperatures, mass air flow, gas pressures, engine coolant temperature, engine RPM, compressor inlet pressures and/or manifold air pressures. Operational enhancement and versatility of the ECU is structured to sample each data input up to 50 times per second thereby insuring rapid detection and collection of anomalies.

Yet another preferred embodiment of the present invention is directed to a fuel control system operative to establish gaseous fuel input for a compression ignition (CI) or diesel engine which is powered by a variable mixture of gaseous and distillate fuels dependent, at least in part, on the operating characteristics or parameters of the CI engine. Moreover, this additional preferred embodiment includes an electronic control module (ECU), of the type generally described above and in greater detail herein. As such, the ECU is operative to determine and/or regulate a concentration of gaseous fuel added into the intake air which is then directed to the combustion section of the CI engine. In order to facilitate proper and more efficient operation of the CI engine, a mass air flow measuring assembly comprising at least one mass air flow (MAF) sensor. The at least one MAF sensor is disposed in monitoring relation to the flow of intake air and along the flow path thereof upstream of a throttle assembly, also to be described in greater detail herein after.

The at least one MAF sensor is operatively connected to the ECU and cooperatively structured therewith to transfer appropriate, predetermined data and/or data signals thereto. The data delivered from the MAF sensor to the ECU is indicative of mass flow rate of the intake air passing along the path of intake air flow to the combustion section of the engine. The at least one MAF sensor is preferred over other known or conventional volumetric flow sensors for determining the quantity of intake air due to its greater accuracy and/or dependency in certain applications and at least partially dependent on the use of the engine with which the one MAF sensor is combined. As will also be described in greater detail, this additional preferred embodiment defines the mass air flow measuring assembly as including the one MAF sensor comprising a “hot wire” MAF sensor. As utilized and applied, the hot-wire mass air flow sensor functions by heating a wire, which is suspended in the engines intake air, with an electric current. The wire's electrical resistance increases when the wire temperature increases. This in turn limits the electrical current flowing through the circuit. When intake air flows past the wire, the wire cools thereby decreasing its resistance, which in turn allows more current to flow through the circuit. The current flow through the circuit increases the wire's temperature until the resistance reaches equilibrium.

Accordingly, it may be determined that the operative current required to maintain the wires temperature is proportional to the “mass air flow” over the heated wire. Moreover, the integrated electronic circuit associated with the hot-wire MAF sensor converts the measurement of current to a voltage signal which is then sent to the ECU. The voltage signal or data signal, as used herein, is thereby indicative of the mass air flow rate of the intake air which in turn will be determinative, within certain operational parameters of the engine, of the amount of gaseous fuel which is added to the intake air flow directed to the combustion section of the CI engine. Further with regard to these structural and operative features of the hot-wire MAF sensor, if air density increases due to pressure increase or temperature increase or temperature drop while the air volume remains constant, the denser air will remove more heat from the heated wire indicating a higher mass air flow. Therefore, unlike other related sensors the hot-wire MAF sensor responds directly to air density. As a result, the hot-wire sensor represents a distinctive and more efficient operative component of this preferred embodiment of the fuel control system as it is better suited to support the combustion process of a CI engine which operates on a variable mixture of gaseous and distillate fuels.

Further, it is to be noted that the aforementioned predetermined operating parameters of this preferred embodiment include, but are not limited to, a maximum gaseous fuel input into the intake air flow of 4.5% by volume of the quantity of intake air based on the determination of by the mass flow rate of the intake air. Moreover, the 4.5% of gaseous fuel relative to intake air is also sufficient to maintain lower flammability limits of the air mass and gaseous fuel mixture prior to entering into the combustion chambers of the CI engine.

Additional predetermined operating parameters also include the restriction, reduction or prevention of engine knocking. More specifically, this preferred embodiment of the fuel control system of the present invention includes an engine knock sensor operatively connected to the ECU. Accordingly, when engine knocking is detected the predetermined operating parameters dictate that the input of gaseous fuel into the intake air flow is reduced to an amount which serves to eliminate or at a minimum significantly restrict the occurrence of engine knocking so as to prevent damage to the engine.

As also explained in greater detail, the “throttle assembly” used in the structure and operation of this embodiment of the fuel control system preferably comprises the “throttle body” associated with the aforementioned mixing assembly. Accordingly, the throttle assembly comprises and/or is at least partially defined by the structurally integrated throttle body and air gas mixer. Moreover, the integrated throttle body and air gas mixer is disposed and structured to dispose the throttle body in fluid communication with a positively pressured gaseous fuel supply. As a result, gaseous fuel is “pushed” under a positive pressure, to the integrated throttle body and air gas mixer and there through to the intake air flow, being directed to the combustion section of the CI engine.

Due to the fact that the gaseous fuel is delivered under a positive pressure from the gaseous fuel supply it can be more efficiently regulated by effectively “pushing” the gaseous fuel through the throttle body into the air gas mixer and therefrom directly into the intake air flow in specified quantities and/or volumes to accommodate delivery of gaseous fuel in the amounts no greater than the 4.5% by volume of intake air and/or controlled, lesser amounts to restrict engine knocking and other unwanted operating features associated with the CI engine.

These and other objects, features and advantages of the present invention will become clearer when the drawings as well as the detailed description are taken into consideration.

BRIEF DESCRIPTION OF THE DRAWINGS

For a fuller understanding of the nature of the present invention, reference should be had to the following detailed description taken in connection with the accompanying drawings in which:

FIG. 1 is a perspective view of one preferred embodiment of the system and assembly of the present invention wherein a mixing assembly comprising an integrated throttle body and air gas mixer are connected to an intake air flow path being delivered to a combustion section of an engine/generator with which the mixing assembly is utilized.

FIG. 2 is a schematic representation of the embodiment of FIG. 1.

FIG. 3 is a schematic representation of yet another preferred embodiment of the system of the present invention comprising a plurality of mixing assemblies of the type represented in FIGS. 1, 4 and 5.

FIG. 4 is a perspective detailed view of an integrated throttle body and air gas mixer defining one of a possible plurality of mixing assemblies of the type represented in FIG. 1.

FIG. 5 is a rear perspective detailed view of the embodiment of FIG. 4.

FIG. 6 is a schematic representation of yet another preferred embodiment of the fuel control system of the present invention.

Like reference numerals refer to like parts throughout the several views of the drawings.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

As schematically represented in the accompanying Figures, the present invention is directed to a control system and included structure operative to establish a coordinated operative fuel mixture of combined gaseous fuel and distillate fuel. The ratio of gaseous fuel to distillate fuel will vary dependent on the operating characteristics of an engine which incorporates the structural and operative features of the system of the present invention. In particular, the control system of the present invention is specifically, but not exclusively, adaptable for use with stationary compression ignition (CI) engines or generators, which may or may not include turbo-charging capabilities.

With primary references to FIGS. 1-3, the system of the present invention comprises an electronic control unit 12 operative to monitor at least predetermined engine data associated with and indicative of the operating characteristics of the engine with which the system is utilized. It is emphasized that FIGS. 2 and 3 are schematic representations intended to provide a detailed description of the structural and operative characteristics of the system of the present invention. As such, the electronic control unit (ECU) 12 includes a plurality of data channels 14 for the monitoring of intended, predetermined or critical parameters such as, but not necessarily limited to fuel rates, exhaust gas temperatures, operation levels, manifold air temperatures, mass air flow, gas pressure, engine coolant, engine RPM, compressor inlet pressures and manifold air pressures, etc.

In addition, one feature of the system of the present invention is the incorporation of at least one mixing assembly generally indicated as 16. As also schematically represented in FIG. 3, yet another preferred embodiment of the system of the present invention incorporates the use of a plurality of such mixing assemblies 16 as will be described in greater detail hereinafter. Accordingly, each mixing assembly 16 comprises an integrated throttle body 18 and air gas mixer 20. Each of the one or more throttle bodies 18 is connected in fluid communication with a gaseous fuel supply 22. Moreover, each of the air gas mixers 20, being structurally integrated with a corresponding one of throttle bodies 18, is disposed in direct fluid communication with a flow path 22 of intake air 22′, wherein the flow path or flow line 22 may be an OEM portion of the engine, as represented in FIG. 1, so as to deliver intake air 22′ to a combustion section 24 of the engine.

With primary reference to FIGS. 1, 4 and 5 each of the one or more mixing assemblies 16 is defined by the structurally integrated throttle body 18 and air gas mixer 20. As such, the air gas mixer 20 includes a housing 26 having an interior 28 which at least partially defines a corresponding one of the flow paths 22 of the inlet air 22′ being delivered to the combustion section 24. As clearly represented in FIG. 1, the housing 26 of the air gas mixer 20 may be installed directly in-line with the corresponding OEM air intake flow path 22, by any appropriate fluid seal connectors, as at 25, Such installation thereby facilitates the interior 28 of the housing 26 defining at least a portion of the flow path 22 of the intake air 22′.

Additional structural features of the air mixer 20 include a dispensing nozzle 30 represented in FIGS. 3 and 4. The dispensing nozzle 30 includes an aerodynamically shaped head 31 formed on one end of the nozzle 30. A plurality of dispensing nozzle ports 32, represented in FIG. 4, are disposed downstream of the head 31 and are structured to deliver or dispense the gaseous fuel, received from the corresponding, integrated air mixer 20, directly into the intake air 22′ travelling along the intake air flow path 22 as set forth above. At least one, but preferably a plurality of interconnecting segments or vanes 34, are disposed and structured to facilitate the substantially aligned, supported disposition of the dispensing nozzles 30 into the flow path 22 of intake air 22′. Further, each of the connecting vanes 38 may be configured and dimensioned to not adversely disrupt air flow 22′ and further facilitate proper mixing of the gaseous fuel into the flow of intake air 22′. A delivery conduit 40 is also disposed on the interior of the housing 26 and serves to provide a direct fluid flow connection of gaseous fuel from the throttle housing 18 into the delivery nozzle 30 of the corresponding, integrated air gas mixer 20.

In at least one preferred embodiment, the structural integration of the throttle body 18 and air gas mixer 20 comprises the mounting and/or direct fixed connection of the throttle body 18 on the exterior of the housing 26. Therefore, the delivery conduit 40 is in direct fluid communication between the nozzle 30 and the outlet fuel outlet (not shown) from the throttle body 18. Due to such an integrated structure, there will not be a collection of gaseous fuel in a connecting conduit or line, between throttle body and air gas mixer and/or intake air, which may exist in conventional fuel systems. Therefore, unlike conventional fuel delivery connections, the gaseous fuel of the present invention may be “pushed” under positive pressure from the throttle body 18 directly into the air gas mixer 20.

More specifically, and as indicated herein, the gaseous fuel supply 21 stores, maintains and dispenses the gaseous fuel under a positive pressure to the throttle body 18. As a result, there will be a positive pressure flow of gaseous fuel, through the delivery conduit 40, into the dispensing nozzle 30. Due to this positively pressurized fuel delivery, there will be no collection of gaseous fuel between the throttle body 18 and the dispensing nozzle 30 of the air gas mixer 20 as may be known in conventional fuel systems as at least generally set forth above. Therefore, the supply of gaseous fuel is maintained at a positive pressure and delivered from the fuel supply 21 to the throttle body 18 and eventually from the throttle body 18 to the corresponding, integrated air gas mixer 20 at such positive pressure. Accordingly, the gaseous fuel supply 21, throttle body 18 and integrated air gas mixer 20 are cooperatively structured and collectively operative to deliver gaseous fuel in appropriate, variable quantities and under a positive pressure to the intake air 22′ of the combustion section 24 of the engine.

In the embodiments of FIGS. 1, 4 and 5, the throttle body 18 is electrically powered and as such includes an electrical socket or other appropriate connection 44. Further, the delivery of gaseous fuel from the fuel supply 21, under pressure, to the throttle body 18 is accomplished by interconnection of an appropriate conduit or line to a throttle body inlet 46.

With primary reference to FIG. 3 in combination with the structural details represented in FIGS. 1, 4 and 5, an additional preferred embodiment of the system comprises the electronic control unit structured to monitor predetermined engine data by virtue of at least one but more practically a plurality of data input and input channels 14. As indicated, the monitored engine data is determinative of engine fuel requirements and will ultimately determine the appropriate and/or most efficient ratio between the distillate fuel and gaseous fuel defining the aforementioned operative fuel mixture being delivered to the combustion section 24 and/or the individual combustion cylinders 24′ defining the combustion section 24. As with the embodiment of FIG. 2, additional preferred embodiment includes a pressurized gaseous fuel supply 21 structured to retain and dispense the gaseous fuel under a positive pressure preferably, but not necessarily, of generally about 3 psi to 7 psi. As also emphasized above, each of the one or more mixing assemblies 16 are structured to independently establish a predetermined coordinated mixture and/or ratio of gaseous and distillate fuels, which in turn define the operative fuel mixture for each combustion section 24 and more specifically for each of the combustion chambers 24′. As indicated, the supply of gaseous fuel is maintained at a positive pressure and delivered from the fuel supply 21 to the throttle body 18 and eventually from the throttle body 18 to the corresponding, integrated air gas mixer 20 at such positive pressure. Therefore, the gaseous fuel supply, throttle body 18 and integrated air gas mixer 20 are cooperatively structured and collectively operative to deliver gaseous fuel in appropriate, variable quantities and under a positive pressure to the intake air of the combustion section 24 of the engine.

Therefore, in the additional preferred embodiment of FIG. 3, a plurality of mixing assemblies 16 each include an integrated throttle body 18 and air gas mixer 20. As a result, each of the various cylinders 24′ of the combustion section 24 may have a different, variable ratio of gaseous and distillate fuels delivered thereto. Accordingly, an effectively different operative fuel mixture may be consumed in the different combustion chambers 24′. It is also emphasized that the ECU 12 and the one or more input data channels 14 are structured to continuously and repetitively monitor the predetermined engine data which in turn is determinative of the specific and/or range or ratios of distillate and gaseous fuels present in the mixture of the operative fuel mixture being delivered to each of the chambers 24′.

Accordingly, each of the plurality of mixing assemblies 16 comprises the integrated throttle body and air gas mixer 18 and 20 respectively. Further, each of the throttle bodies 18 is independently connected in gaseous fuel receiving relation to a common and/or separate fuel supply 21. As also represented, each of the air gas mixers 20 is disposed in fluid communication with a different flow path 22 and the intake air 22′ associated therewith. Further, the integrated structure of each of the mixing assemblies 16 include a throttle body 18 fixedly mounted on and/or connected to an exterior of a corresponding housing 26 of the associated, integrated air gas mixer 20. Similarly, each of the air gas mixers 20 includes a delivery nozzle 30 receiving gaseous fuel from a corresponding, integrated throttle body 18 through a delivery conduit 40. As such, each of the delivery conduits 40 is disposed within the interior 28 the housing 26 of corresponding ones of the air gas mixers 20.

With further regard to both FIGS. 2 and 3, dependent on the intended operation and structure of the engine with which the system of the present invention is utilized, a turbocharger 50 may be disposed within or along the flow path 22 of intake air 22′ so as to further process the intake air 22′ prior to being delivered to the combustion section 24 and/or individual cylinders 24′. In the embodiment of FIG. 2, a single turbocharger 50 is located between the mixing assembly 16 and the combustion section 24, such that the mixing assembly 16, including the integrated throttle body 18 and air gas mixer 20 is upstream along the flow path 22 of intake air 22′ being delivered to the combustion section 24.

Yet another preferred embodiment of the fuel control system of the present invention is schematically represented in FIG. 6. Many of the structural and operative features of the embodiment of FIG. 6 are substantially equivalent to the embodiments of FIGS. 1 through 5. Accordingly the additional preferred embodiment, as represented in FIG. 6 comprises the ECU 12 operative to monitor at least predetermined engine data associated with and indicative of the operating characteristics of the IC engine. The ECU comprises a plurality of data channels 14 for the monitoring of intended, predetermined operating parameters of the engine, which may be critical to the safety and/or appropriate fuel mixture. Such predetermined operating parameters include, but are not necessarily limited to, fuel rates, exhaust gas temperatures, operation levels, manifold air temperature, mass air flow, gas pressure, engine coolant, engine RPM, compressor inlet pressures and manifold air pressures, etc.

Further, the preferred embodiment of FIG. 6 also includes a throttle assembly which is embodied in the aforementioned and described mixing assembly, which is generally represented in FIG. 6, as 116. As such, the mixing assembly 116 comprises a structurally integrated throttle body 18 and an air gas mixer 20 connected in fluid communication with a gaseous fuel supply 21 maintained under a positive pressure. Therefore, gaseous fuel delivered from the fuel supply 21 is effectively “pushed” under the aforementioned positive pressure to the throttle body 18. The positive delivery of the gaseous fuel to the throttle body 18 and there from to the air gas mixer 20 thereby allows a “predictive” amount of gaseous fuel being delivered to the intake air 22′.

In more specific terms and again with primary referenced to FIG. 6, the ECU 12 is operative to determine and/or regulate the concentration of gaseous fuel within the intake air flow 22, 22′ being delivered to a combustion section 24 of the CI engine. In order to affect a more precise quantity of gaseous fuel utilized to power the combustion section 24, a mass air flow measuring assembly 60 is inserted in fluid communication with the path of inlet air flow 22 and in direct fluid communication with the intake air 22′. Moreover, the mass air flow measuring assembly 60 preferably includes at least one mass air flow sensor 62 operatively connected to the ECU 12 so as to provide signals determination of the mass air flow rate of the intake air 22′ passing along the intake flow path 22. In turn the ECU 12 is operatively connected to the mixing assembly 116 including throttle assembly including the integrated throttle body and the air gas mixer 18 and 20 respectively. As a result, gaseous fuel delivered under pressure from the fuel supply 21, will be effectively “pushed” in adequate quantities to sufficiently and safely power the combustion section 24. In addition, the throttle body 18 is cooperatively structured with the ECU 12 and operative therewith to establish a sufficient concentration and/or quantity of gaseous fuel being delivered to the intake air 22′ to comply with proper operation of the CI engine in accord with predetermined operating parameters of the CI engine. As also indicated the condition of state of the predetermined operating parameters are determined by the ECU 12 over data channels 14.

Accordingly, in this preferred embodiment of the present invention, the aforementioned operating parameters specifically include, but are not limited to, a maximum gaseous fuel input into the intake air of 4.5% by volume of the quantity of intake air and/or mass flow rate thereof. Moreover, the operating parameters can also be at least partially defined by a control of the quantity of gaseous fuel into the intake air 22′ which is sufficiently less to eliminate or restrict the occurrence of engine knocking. Therefore, the additional preferred embodiment of FIG. 6 may also include an engine knocking sensor 64 disposed and structured to facilitate the detection of engine knocking. Further the engine knocking sensor 64 is connected and/or operatively structured with the ECU 12 to facilitate the determination by the ECU 12 that engine knocking is or has occurred. In turn the ECU 12 is operatively connected to the throttle assembly or throttle body 18 so as to regulate and more specifically diminish the quantity of gaseous fuel being delivered into the intake air 22′ through the aforementioned integrated gas mixer 20. As such, the lesser quantity of gaseous fuel, below the maximum of 4.5% by volume of intake air is sufficiently reduced to restrict the engine knocking.

Since many modifications, variations and changes in detail can be made to the described preferred embodiment of the invention, it is intended that all matters in the foregoing description and shown in the accompanying drawings be interpreted as illustrative and not in a limiting sense. Thus, the scope of the invention should be determined by the appended claims and their legal equivalents.

Now that the invention has been described,

Claims

1. A control system for establishing gaseous fuel input for a compression ignition engine operative on a variable mixture of gaseous and distillate fuels, said control system comprising:

an electronic control module (ECU) operative to regulate a concentration of gaseous fuel within an intake air flow to a combustion section of the CI engine,

a mass air flow measuring assembly comprising at least one mass air flow (MAF) sensor disposed in monitoring relation to the intake air flow,

said one MAF sensor operatively connected to said ECU and structured to transfer data signals to said ECU indicative of a mass flow rate of the intake air flow,

a throttle assembly structured to deliver variable quantities of gaseous fuel to the intake air flow dependent at least on the mass flow rate of intake air, and

said throttle assembly cooperatively structured with said ECU and operative therewith to establish a sufficient concentration of gaseous fuel delivered to the intake air flow to comply with predetermined operating parameters of the CI engine.

2. A control system as recited in claim 1 wherein said predetermined operating parameters comprise a maximum gaseous fuel input of 4.5% by volume of the mass flow rate of intake air.

3. A control system as recited in claim 2 wherein said predetermined operating parameters further comprise a sufficient input of gaseous fuel to restrict the occurrence of engine knocking.

4. A control system as recited in claim 1 wherein said predetermined operating parameters comprise an input of a sufficiently reduced quantity of gaseous fuel to restrict the occurrence of engine knocking.

5. A control system as recited in claim 4 further comprising a knock sensor assembly operatively disposed relative to the combustion section and structured to determine an occurrence of engine knock therein.

6. A control system as recited in claim 5 wherein said knock sensor assembly is operatively connected to said ECU and structured to signal said ECU of an occurrence of engine knock in the combustion section.

7. A control system as recited in claim 6 wherein said ECU is cooperatively structured with said throttle assembly to regulate delivery of gaseous fuel to the intake air based on the determination of engine knock by said knock sensor assembly.

8. A control system as recited in claim 6 wherein said ECU is cooperatively structured with said throttle assembly to deliver a diminished quantity of gaseous fuel to the intake air flow upon a determination of engine knock by said knock sensor assembly.

9. A control system as recited in claim 8 wherein said diminished quantity of gaseous fuel comprises an amount sufficiently less than 4.5% by volume of the mass flow rate of intake air to restrict engine knock in the combustion section.

10. A control system as recited in claim 9 wherein said predetermined operating parameters comprise a maximum gaseous fuel input of 4.5% by volume of the mass flow rate of intake air.

11. A control system as recited in claim 1 wherein said one MAF sensor comprises a hot-wire MAF sensor.

12. A control system as recited in claim 1 further comprising a gaseous fuel supply structured to retain and deliver the gaseous fuel under a positive pressure; said throttle assembly and said gaseous fuel supply being cooperatively structured to direct the variable gaseous fuel flow from the throttle assembly to the intake air at a positive pressure.

13. A control system as recited in claim 12 wherein said predetermined operating parameters comprise a maximum gaseous fuel input of 4.5% by volume of the mass flow rate of intake air.

14. A control system as recited in claim 1 further including at least one mixing assembly comprising an air gas mixer structurally integrated with said throttle assembly, said throttle assembly disposed in fluid communication with said gaseous fuel supply and said air gas mixer disposed in gaseous fuel delivering relation with the intake air flow to the combustion section.

15. A control system as recited in claim 14 further comprising a gaseous fuel supply structured to retain and deliver the gaseous fuel under a positive pressure; said throttle assembly structured to direct a variable gaseous fuel flow under said positive pressure directly to said integrated air gas mixer there from to the intake air flow.

16. A control system for establishing gaseous fuel input for a compression ignition engine operative on a variable mixture of gaseous and distillate fuels, said control system comprising:

an electronic control module (ECU) operative to regulate a concentration of gaseous fuel within intake air flow to a combustion section of the CI engine,

a mass air flow measuring assembly comprising at least one mass air flow (MAF) sensor disposed in monitoring relation to the intake air flow,

said one MAF sensor operatively connected to said ECU and structured to transfer data signals to said ECU indicative of a mass flow rate of the intake air flow,

a gaseous fuel supply structured to retain and dispense the gaseous fuel under a positive pressure,

at least one mixing assembly comprising a structurally integrated throttle body and air gas mixer,

said throttle body structured to direct a variable gaseous fuel flow under the positive pressure directly to said integrated air gas mixer and there from to the intake air, and

said throttle body cooperatively structured with said ECU and operative therewith to establish a sufficient concentration of gaseous fuel delivered to said integrated air gas mixer and the intake air flow to comply with predetermined operating parameters of the CI engine.

17. A control system as recited in claim 16 wherein said predetermined operating parameters further comprise an input of a quantity of gaseous fuel sufficient to restrict the occurrence of engine knock.

18. A control system as recited in claim 17 further comprising a knock sensor assembly operatively disposed relative to the combustion section and structured to determine an occurrence of engine knock therein.

19. A control system as recited in claim 18 wherein said predetermined operating parameters comprise a maximum gaseous fuel input of 4.5% by volume of the mass flow rate of intake air.

20. A control system as recited in claim 19 wherein said ECU is cooperatively structured with said throttle body to deliver a diminished quantity of gaseous fuel to the intake air flow upon a determination of engine knock by said knock sensor assembly.

21. A control system as recited in claim 20 wherein said diminished quantity of gaseous fuel comprises an amount sufficiently less than 4.5% by volume of the mass flow rate of intake air to restrict engine knock in the combustion section.

22. A control system as recited in claim 1 wherein said one MAF sensor comprises a hot-wire MAF sensor.