US3870025A

US3870025A - Method and apparatus for improving the fuel injection characteristics of internal combustion engines

Info

Publication number: US3870025A
Application number: US269231A
Authority: US
Inventors: Harold Elden Anderson; Perry Lester Kruckenberg
Original assignee: Mcculloch Corp
Current assignee: Mcculloch Corp
Priority date: 1972-07-05
Filing date: 1972-07-05
Publication date: 1975-03-11
Anticipated expiration: 1992-03-11
Also published as: AU466789B2; CA975234A; JPS5738782B2; JPS4957227A; FR2191608A5; GB1421367A; DE2324476A1; AU5539973A; BE801860A

Abstract

A method and apparatus for improving the fuel injection characteristics of internal combustion engine means, particularly in relation to diesel engines operating on the spaced burning loci principle as featured in United States Kruckenberg et al. U.S. Pat. No. 3,543,735. associated This improvement is practiced in systems where the time increment of injection of an injection nozzle is longer than the time increment of the pumping stroke of a fuel pump. In such systems, at relatively lower engine speed and/or load conditions, the volume of a fuel increment displaced by a fuel pump during each working engine stroke is increased and a portion of fuel is diverted between the fuel pump piston means and injection nozzle means of the engine. In a system such as this, at relatively higher engine speed and/or load conditions, a relatively lower volume of fuel is displaced during each pumping increment of the fuel pump and at least the full diversion of fuel does not take place. In another aspect of the invention, and at lower engine speed and/or load conditions, the injection nozzle is caused to generate a generally billowing or diverging spray pattern, while at higher or normal engine speed and/or load conditions the injection nozzle is caused to generate relatively solid streams of fuel. Preferably, these ''''solid'''' streams are directed into individualized or discrete agitation zones and burning loci associiated therewith.

Description

United States Patent [1 1 Anderson et al.

[ 1 Mar. 11, 1975 1 1 METHOD AND APPARATUS FOR IMPROVING THE FUEL INJECTION CHARACTERISTICS OF INTERNAL COMBUSTION ENGINES [75] Inventors: Harold Elden Anderson, Playa del Rey; Perry Lester Kruckenberg, Los Angeles, both of Calif.

[73] Assignee: McCulloch Corporation, Los

Angeles, Calif.

[22] Filed: July 5, 1972 [21] Appl. No.: 269,231

[52] US. Cl... 123/139 AF, 123/32 H, 123/139 AT,

123/140 A, 123/140 J, 123/32 B, 239/563 [51] Int. Cl. F02d l/04, F02d 1/06, F02m 39/00 [58] Field of Search..... 123/139 AF, 139 AS, 140 J,

123/140 MC, 139 AW, 32 JV, 139 AT; 239/563, 562

[56] References Cited UNITED STATES PATENTS 1,811,731 6/1931 Petty 239/533 y1 5 8 1 7/1932 Dilg 123/139 AF 2,794,397 6/1957 Burman .[411/311 3,489,093 l/l970 Thornber 123/139 AL 3,543,735 12/1970 Kruckenberg 123/32 B 3,672,343 6/1972 Biechl et al 123/140 MC FOREIGN PATENTS OR APPLICATIONS 933,374 9/1946 France 123/32 JV 159,669 11/1954 Australia 123/32 .lV

Primary Examiner-Charles J. Myhre Assistant Examiner-Ronald B. Cox

l ABSTRACT A method and apparatus for improving the fuel injection characteristics of internal combustion engine means, particularly in relation to diesel engines operating on the spaced burning loci principle as featured in United States Kruckenberg et al. US. Pat. No. 3,543,735. associated This improvement is practiced in systems where the time increment of injection of an injection nozzle is longer than the time increment of the pumping stroke of a fuel pump. In such systems, at relatively lower engine speed and/or load conditions, the volume of a fuel increment displaced by a fuel pump during each working engine stroke is increased and a portion of fuel is diverted between the fuel pump piston means and injection nozzle means of the engine. In a system such as this, at relatively higher engine speed and/or load conditions, a relatively lower volume of fuel is displaced during each pumping increment of the fuel pump and at least the full diversion of fuel does not take place.

'these solid streams are directed into individualized or discrete agitation zones and burning loci associiated therewith.

20 Claims, 10 Drawing Figures Mathis F l FUEL PUMP {I00 4 'i Eiii WORKING "5 l CONTROL CHAMBER I L l |25 ae itiiist TLE T0 LOW PRESSURE ZONE PMENTED BAR l 1 1975 SHEET 6 0H5 TIME PRAY A NORMAL and/Or fmME) I HIGHER-ENGINE I SPEED and/Or LOAD B CONTROL 7 E x (DEGREES OI CRANKSHAFT ROTATION) E LOWER ENGINE I' ITIME) SPEED and/or LOAD (PRIOR) xIOEOREEs ofCRAN KSHAFT ROTATION) 1 LOWER ENGINE I SPEED OHd/OI'LOAD V (PRESENT F INVENTION) I x (DEGREES of CRANKSHAFT ROTATION) FIG. 10

METHOD AND APPARATUS FORIMPROVING THE FUEL INJECTION CHARACTERISTICS OF INTERNAL COMBUSTION ENGINES RELATED CASES This invention is directed to improved fuel injection techniques which are intended to improve the fuel combustion characteristics of internal combustion engines, particularly those of the type described in United States Kruckenberg et al application Ser. No. 93,269 now abandoned, filed Nov. 27, 1970, and entitled Improved Combustion System for Internal Combustion Engines and in the United States Kruckenberg et al. US. Pat. No. 3,543,735. the aforesaid Kruckenberg patent and application are each assigned to the assignee of the present application.

This present invention involves, in a combination sense and in relation to certain embodiments, the utili zation of a modified injection spray concept which is the subject matter of a United States patent application filed of even data herewith, entitled Modified Injection Spray Characteristics for Spaced Burning Loci Engines, identifying Harold Elden Anderson and Perry Lester Kruckenberg as coinventors, and assigned to the assignee of this present application.

GENERAL BACKGROUND, OBJECTS AND SUMMARY OF INVENTION In United States Kruckenberg et al. US. Pat. No. 3,543,735, and in United States Kruckenberg et al. application Ser. No. 93,269, a unique type of engine and mode of engine operation are described.

Fundamentally, the concept featured in this Kruckenberg et a] patent and application pertains to the generation ofa series of spaced burning loci in the interior or working chamber of an internal combustion engine. Peripherally confined agitation zones are individually associated with these loci. During the working or down, stroke of a piston within the engine working chamber and at a normal speed and/or load condition, fuel is injected in the form of relatively solid streams, with individual streams being directed into individual agitation zones and burning loci associated therewith. The bulk of the fuel is injected during the working or downstroke.

The benefits produced by this spaced burning loci principle are substantial and entail a reduction in peak combustion chamber pressure, a reduction in the rate of pressure rise in the chamber, a reduction in engine noise level, a reduction in engine exhaust and combustion temperatures, a reduction in the generation of noxious oxides of nitrogen, a reduction in carbonization tendencies, an improvement in specific fuel consumption, an improvement in starting characteristics, and an overall ability to reduce the size of an engine in relation to a desired horsepower output.

To the extent that the mass flow rate of heated gas varies or increases as it flows through the agitation zones associated with the burning loci during the working stroke of a piston, the aforesaid Kruckenberg et al. application Ser. No. 93,269, contemplates a further and significantly improved aspect. In general, this aspect entails the increasing of the rate of injection of fuel into agitation zones as the mass flow rate of heated, combustion supporting gas flowing into the agitation zones increase.

Such significant advances in the engine art notwithstanding, it has been discovered that further steps, when implemented, will improve the operating characteristics of an engine, particularly an engine of the type featured in the aforesaid Kruckenberg patent and application during low load and/or engine speed conditions.

In certain conventional injection systems, the pumping increment of a fuel pump, during each working stroke of an engine, is less than the duration of the injection increment at the injection nozzle. ln systems of this type, the time duration of the injection increment at the injection nozzle itself is more or less a function of the volume of fuel pumped during each pumping increment or cycle of the fuel pump. 7

Since a significant and important operating characteristic of the spaced burning loci engine entails a prolongation of fuel burning, it is desirable that fuel burning remain controlled by burning loci and agitation zones for a particular and generally constant control increment of crankshaft rotation, i.e., a particular increment of piston movement. Thus, it becomes important to maintain, as nearly as possible, a generally continuing or constant relationship between the duration of fuel injection at the injection nozzle and the desired control increment of crankshaft rotation or piston movement each expressed in terms of piston movement.

However, with a fuel injection system of the type heretofore described, where the time of fuel injection is a function of the volume of the injection charge, this desired match between piston movement increment and injection increment have heretofore been impaired at lower engine speed and/or load conditions, where the engine was optimized to provide the desired match at normal or higher engine speed and/or load conditions.

The reason for this impairment resides in the fact that at lower speed and/or load conditions, for a given charge of fuel, the increment of piston movement corresponding to the duration of the increment of injection of fuel into the engine is reduced. This resulting mismatch" is further aggravated when the volume of the charge is reduced.

The present invention substantially alleviates this mismatch condition.

In alleviating, or at least significantly offsetting, an improper or unacceptable balance between injection increment and piston movement control increment, the present invention contemplates a method wherein a fuel pump piston means is caused to displace an incre ment of fuel. This displaced increment of fuel is transmitted through passage means which lead from the fuel pump piston means to fuel injection nozzle means. The fuel injection nozzle means is itself operable to pass fuel into the interior of the engine. However, the fuel is discharged from the nozzle means into the engine interior at a rate which is different from and slower than the rate of displacement of the fuel increment from the fuel pump means into the passage means.

At a relatively lower speed for any given load condition of the engine, a relatively larger volume fuel increment is displaced during each engine stroke from the fuel pump means into the passage means. However, fuel is also diverted from the passage means between the piston means and the injection nozzle means.

At a relatively higher speed for any given load condition of the engine, a relatively smaller volume fuel increment is displaced during each working stroke of the engine and the aforementioned fuel diversion, at least to its former extent, is prevented.

In the context of this method, and where a plurality of working chambers are included in the engine and a single, multiple output, fuel pump is employed, it is desirable for the fuel to be diverted, as above noted, from a location in the passage means which is in common communication with fuel flow paths leading to all of the injection nozzles associated with the various working chambers.

In conjunction with these method aspects of the invention, and as an independently significant factor, the present invention contemplates various combinations of apparatus means which uniquely interact to perform the aforesaid methods.

While the burning loci principle is uniquely advantageous, particularly at'normal and high speed and/or load conditions, it has been unexpectedly discovered that at low speed and/or load conditions it may be preferable to modify the manner in which fuel is transmitted into the agitation zones which determine the location of and are operable to generate the aforesaid burning loci.

At normal or high speed and/or load conditions, fuel is injected as individualized, generally cohesive or solid streams directed straight into the various individual agitation zones and burning loci.

However, at low speed and/or load conditions, it is now believed desirable to forego injection of solid fuel streams, as above noted, and instead inject fuel into a precompression chamber communicating with the agitation zones in the form of a diverging or billowing spray. (The term precompression chamber, as here used, means a chamber, auxiliary to the working chamber, which receives compressed gas on the piston compression stroke and from which compressed gas is passed to the working chamber during the piston working stroke). In short, at a low speed and/or load condi tion- (i.e., at an idle or near idle condition), i.e., where the temperautre of the working or combustion chamber is relatively .low, the burning loci engine appears to perform more smoothly and enjoy more even and complete burning if the degree of fuel atomization occurring between the exit orifices of the injection nozzle and the agitation zones is increased.

This increase in atomization at low speed and/or load conditions is achieved through this invention by producing a generally radial pattern of fuel flow leading to the injection nozzle orifice means. This radial inflow pattern produced a generally diverging, or billowing, and thus relatively atomized spray of fuel exiting from the orifice means and passing into the precompression chamber which communicates with the aforesaid agitation zones. At relatively higher or normal speed and/or load conditions, the radial flow pattern is supplanted by a more or less axial flow of fuel leading to the orifice means and, as a result of this relatively axial flow pattern, generally solid or discrete fuel streams are ejected from the nozzle orifice means.

Here again, the invention contemplates various combinations of apparatus means which are able to perform these method steps and attain the improvements in engine operating characteristics above noted.

In describing the invention, reference will be made to certain preferred embodiments, it being understood that this reference is by way of example and is not intended to be restrictive in relation to the scope of the invention.

DRAWINGS The appended drawings illustrate structural details of certain preferred embodiments of the invention. In the Drawings FIG. 1 provides a schematic view of the overall improved injection system of the invention, displayed in the context of a spaced burning loci type engine;

FIG. 2 provides a schematic, partially sectioned illustration of a single working chamber engine of the burning loci type and illustrates one form of a burning loci engine;

FIG. 3 provides an enlarged, partially sectioned, fragmentary and perspective view of a precompression and control zone of the FIG. 2 engine, illustrating the injection of solid fuel streams into peripherally confined agitation zones;

FIG. 4 provides a top plan view of the piston of the FIG. 2 engine, schematically illustrating the manner in which burning loci are generated and maintained, particularly and principally during the working stroke of the piston;

FIG. 5 provides a transversely sectioned view of the FIG. 3 precompression chamber and further illustrates the burning loci phenomena in a schematic sense;

FIG. 6 schematically illustrates a conventional fuel injection pump which has been modified to permit the diversion of fuelfrom passage means communicating with each of multiple, output fuel flow paths of the P p;

FIG. 7 provides an enlarged longitudinally sectioned view of the modified injection nozzle incorporated in the FIG. 1 system, which modification is operable to produce a billowing or diverging injection pattern at lower speed and/or load conditions and a generally or relatively solid stream pattern at higher or normal speed and/or load conditions; 7

FIG. 8 provides a still further enlarged, longitudinally sectioned view of the tip of the FIG. 7 nozzle, illustrating the position of the injection nozzle valve at a low load condition;

FIG. 9 provides a still further enlarged longitudinally sectioned view of the tip of the FIG. 7 nozzle, illustrating the position of the injection nozzle valve at a higher or normal load condition;

FIG. 10 illustrates certain relationships existing between the time duration required for the injection of a fuel charge from a nozzle into an engine in relation to a desired control increment of piston movement expressed in terms of degrees of crankshaft rotation and illustrates this relationship at a higher load engine condition as well as at a lower load condition.

INTRODUCTION Before discussing the novel and advantageous features of this invention, it is appropriate to review the context within which the invention may be most advantageously practiced.

While aspects of the invention may be utilized in conjunction with a variety of engines, it is believed that particularly significant results will be achieved when the present invention is employed to improve the operating characteristics of the spaced burning loci type engine described in the aforesaid United States Kruckenberg et al. U.S. Pat. No. 3,543,734, and the aforesaid Kruckenberg et al. application Ser. No. 93,269.

The disclosures of the Kruckenberg et al. U.S. Pat. No. 3,543,735, and Kruckenberg et al application Ser. No. 93,269, are incorporated herein by reference. With respect to significant variations in engine structural characteristics which may be employed in practicing the invention and with respect to dimensional and operational parameters, attention is invited in particular to disclosure of the aforesaid Kruckenberg et al application.

GENERAL CHARACTERISTICS SPACED BURNING LOCI ENGINE General operating characteristics of a spaced burning loci engine will now be briefly reviewed with reference to FIGS. 2, 3, 4 and 5.

The exemplary spaced burning loci engine 1 depicted in FIG. 2 includes a working cylinder 2 and an air pumping cylinder 3, both of which are connected with and communicate with a crankcase 4. A working piston 5 is reciprocably mounted in cylinder 2 while an air pumping piston 6 is reciprocably mounted in pumping cylinder 3. Connecting rods 7 and 8 extend respectively from

pistons

5 and 6 to a crankshaft 9.

An air transfer conduit 10 extends from outlet port 11 of pumping cylinder 2 to an air inlet port 12 of the working cylinder 2.

Air enters the pumping cylinder 3 through air inlet port means 13. Exhaust gas exits from working cylinder 2 through exhaust port means 14.

The mode of operation of cylinders 2 and 3 along with

pistons

5 and 6, which cause the pumping of air to working cylinder 2 is described in detail in the aforesaid Kruckenberg U.S. Pat. No. 3,543,735.

An engine operated fuel pump 15 is connected by conduit means 16 to an injection nozzle 17. The injection nozzle l7includes a terminus 18 having a plurality of fuel discharging orifices positioned in a precompression cavity or chamber 19.

Precompression cavity or chamber 19 is located in cylinder head 20 of working cylinder 2.

As shown in FIGS. 2 and 3, working piston 5 includes a wafer-like protrusion 21 projecting from the piston head 22 toward the precompression cavity 19.

Protrusion 21 is operable to be telescopingly received within the precompression chamber 19 during the end of the compression stroke of the piston 5 and the beginning of the working stroke.

A series of circumferentially spaced and generally longitudinally extending slots 23, which may be axially oriented or generally inclined, are formed on the periphery of protrusion 21. With the protrusion received within the precompression chamber 19, as generally shown in FIG. 2, the slots 23 cooperate with the side wall 24 of the precompression chamber 19 to peripherally confine and generally define a series of agitation zones 25 which are circumferentially spaced about the axis of reciprocation of piston 2.

While such agitation zone defining cooperation exists between the protrusion 21 and the precompression chamber wall 24, fuel outlet orifices 26 at the tip of the injection nozzle 18 are operable to direct generally solid streams of fuel individually into these agitation zones 25. Thus, for example, a representative fuel stream 27, shown in FIG. 3, is directed individually into one agitation zone 28 of the plurality of zones 25. As is described in the aforesaid Kruckenberg et al. patent and application, the inlet mouth 29 of each agitation zone 25, including zone 28, is sufficiently large as to receive a fuel stream 27 throughout the period of time that the slots 23 of the protrusion 21 are telescopingly received within the wall 24 so as to define the agitation zones 25.

Commencing at or just shortly before the top dead center crankshaft position of the piston 2, the injection nozzle 18 commences to inject fuel from orifices 26 into the precompression chamber such that the preponderance of fuel is directed into the agitation zones 25 during the initial part of the down stroke of the piston 2.

A consequence of this phenomena is the generation of spaced burning loci or centers 30, which are schematically depicted in FIGS. 4 and 5. These burning centers 30 are spaced and generally discrete in nature and are maintained during the working stroke of the piston while fuel is being injected.

Thus, the mode of operation of engine 1 is such that within the cylinder 2, the plurality of spaced burning loci 30 are generated, with these loci 30 remaining generally mutually distinct or discrete and defining spaced centers of burning. These spaced centers of burning are located generally adjacent and in energy communicating relation with the head 22 of the piston 5.

During a working or down stroke of the piston 5, combustion supporting gas, heated by compression and some limited combustion within the precompression chamber, is transmitted from the precompression chamber 19 through the agitation zones 25 and into the burning loci 30. In addition and concurrently, the fuel streams 27 are generated and transmitted into these burning centers.

Thus, during the working stroke, heated combustion supporting gas, i.e., air with some products of combustion, and fuel streams pass through the agitation zones 25 where intensified fuel-air heating and mixing occurs. This phenomena, coupled with the peripherally confining effect of the agitation zones, produces and generates the burning centers or loci 30, with each individual loci 30 and its associated agitation zone 25 receiving at least one individual solid fuel stream and at least some heated gas.

As is described in the aforesaid Kruchenberg et al application, it is believed that burning is initiated during each working stroke of the piston 5 through ignition of fringe portions of each stream 27 at the commencement of each individual fuel injection cycle as effected by the nozzle 18. By controlled operation of the fuel injection system, the time duration of the generation of the fuel streams 27 is limited so at least the majority of fuel in the streams 27 passes into the loci 30 during the working or down stroke of the piston 5.

The spaced wall means or slots 23 thus each function to peripherally confine and define an individual fuel and heated gas agitation zone 25 which is individually associated with and communicates with a burning loci. Each such agitation zone 25 and the burning loci 30 associated therewith receives fuel from at least one fuel stream directed thereinto during the working stroke of the piston 5. The spaced and generally discrete relation of the burning loci 30 are maintained during the working stroke of the piston 5 and the energy generated through the operation of the burning loci is utilized to induce the working stroke of the piston 5.

As is described in the aforesaid Kruckenberg et al. application, it is believed that the mass flow rate of combustion supporting gas flowing through each agitation zone 25 increases as the working stroke continues. This results due to an effective reduction in impedance to flow resulting from an enlargement of the flow capacity of each agitation zone 25, as the protrusion 21 moves out of the percompression chamber 19 and progressively exposes a larger radially outwardly directed portion 31 of each agitation zone 21. Even at the point in time where the size of the laterally directed outlet 31 exceeds the size of the generally axially directed inlet 29 of each agitation zone, it is believed that this increase in flow capacity of the agitation zone 25 will continue. This increase is believed to be due to factors including an increase in heating in the chamber 19 which will produce an increase in flow rate due to a pressure increase and is doubtless also due to a continued reduction in impedance of flow resulting from the continued enlargement of the outlet 31.

In any event, it has been determined through engine operations that a progressive increase in the mass flow rate of fuel flowing in each stream 27 during the working stroke of the piston 5, for at least the initial majority of the time during which the fuel streams 27 are passing through the agitation zones 25 and the burning loci, will produce smoother combustion characteristics and improved fuel consumption.

Various devices and techniques which may be employed to produce such progressive increase in the mass flow rate of fuel in the streams 27 are described in the aforesaid Kruckenberg et al. application Ser. No. 93,269.

For the purpose of the ensuing discussion, it will be assumed that this progressive increase in the mass flow rate of fuel is achieved by employing a particular fuel pump and a particular nozzle 18 operating under appropriate cam control so as to produce such a flow rate increase in the streams 27.

Specific components which may be employed for this purpose include a fuel pump Model 1 PFM, manufactured by Allis Chalmer Engines and having and address at Harvey, Ill. U.S.A., and by employing an injection nozzle holder Model AlCB-355-24 and a nozzle tip Model QDL 1305-30, both manufactured by American Bosch Corporation, and having an address at Springfield, Mass., U.S.A. Alternatively, a nozzle as subsequently described with reference to FIGS. 7 through 9 of the present application may be employed. A general type of cam which may be employed to achieve this aforesiad increase in mass flow rate of fuel, is designated pump type APF-A, cam profile No. 3 medium by American Bosch Corporation of Springfield, Mass., U.S.A., and actuates the pump.

A representative spaced burning loci engine has now been reviewed, such that the preferred context of the practice of this invention has been established. Thus, it now becomes appropriate to consider the technique presented through this invention for improving the balance condition or match" between the increment'of fuel injection at the nozzle and the desired control increment of engine operation. This control increment is the increment of a cycle of engine operation during which burning is to be controlled. In the case of the spaced burning loci engine, the control increment is defined by the existence of the agitation zones and their associated burning loci.

MODIFICATION OF FUEL PUMP DISPLACEMENT VOLUME AND FUEL DIVERSION TECHNIQUE With reference to FIGS. 1, 6 and 10, the general technique presented through this invention for appropriately matching or balancing nozzle injection increments and engine cycle control increments will now be described.

As is shown schematically in FIG. 1, the basic system includes, as principal components, a fuel pump 100, an injection nozzle 101 and passage means 102. The passage means 102 extend between fuel pump piston means housed by the fuel pump and outlet orifice means 103 of the injection nozzle means 101. As is shown schematically in FIG. 1, passage means 102 extends from the fuel pump working chamber means 100a.

When the injection nozzle means 101 is being operated to generate a plurality of generally solid or discrete streams of fuel 104 issuing from orifices 103, each such fuel stream 104 is directed into a peripherally confined agitation zone 105 and transmits fuel through the agitation zone into a burning loci 106.

Each agitation zone 105 and burning loci 106 corresponds generally in a functional sense, to an agitation zone25 and burning loci 30, as previously considered, but may be structurally and dimensionally defined and varied by various techniques.

These loci 105 are contained within the interior of an internal combustion engine 107 and are disposed in energy communicating relation with a movable piston means 108.

A diversion valve 109 is mounted in communicating relation with passage means 102 and is operable to divert flow from the passage means 102, between the piston means of the fuel pump 100 and the injection nozzle orifices 103, and permit this diverted flow to return to a sump or fuel supply or possibly to the inlet side of a metering valve or control valve which may be associated with the fuel pump 100.

Diversion valve 109 may comprise a valve body 110 having an interior cavity 111 communicating with passage or conduit 102 by way of a branch conduit I12.

Valve 109 may include a valve seat 113 operable to be closed by a valve member 114. As shown in FIG. 1, valve member 114 may comprise a ball valve and may be biased into a seated or valve closing position against seat 113 by a conventional coil spring 115.

With this arrangement, the valve 114 will open when the pressure in passage means 102 andll2 is sufficient to overcome the biasing influence of the coil spring 115.

Controlled opening of the valve member 114 may be achieved by operation of a holding or valve disabling plunger 116. Plunger 116 is reciprocably mounted in the valve body 110 and its position may be determined by a rotary cam 117 which may be mounted on a rotatable shaft 118. Shaft 118 may be journalled in a bracket portion 119 of the valve body 110 and its movement may be controlled by a crank arm 120. Crank arm movement, in turn, may be determined by a conventional linkage means 121 extending in a conventional manner to a throttle actuating mechanism 125 associated with the engine 107.

Thus, with the cam 117 disposed in the position shown in FIG. 1, the valve member 114 may open in response to fuel pressure in passage means 102 and 112 so as to divert fuel out of the passage means 102 and permit this fuel to flow through passage means 112 and the interior 111 of the valve 110, around the plunger 116, and out of a discharge conduit 122. This discharge conduit 122 may extend to a low pressure fuel zone in the system such as the fuel reservoir, the inlet side of a metering valve associated with fuel pump 110, etc.

By rotating the cam 117 ina counterclockwise direction, as shown in FIG. 1, the plunger 116 will move toward the valve member 114 and hold it firmly against valve seat 113. In this throttle controlled, closed valve position, opening movement of the valve member 114 is affirmatively prevented.

The volume of each increment pumped out of chamber 100a for transmittal to an engine working chamber for an engine working stroke may be varied by controlling the stroke of the fuel pump portion or by metering the flow of fuel to the fuel pump, or by other means. Such control over the pumped fuel increments is regulated in accordance with engine speed and/or load and is coordinated with the operation of diverters valve means 109, as is subsequently more fully explained.

If the flow of fluid to the inlet side of the fuel pump 100 is to be regulated or throttled to achieve this pumped fuel volume control, the displaced fuel volume control means 123 may comprise a metering valve of a conventional nature. As is well understood, such a metering valve 123, in essence, will determine the rate of flow to the pump 100 and thus will determine the volume of each increment pumped by the piston means of the pump 100 during each working stroke of the piston means 108.

Appropriate manipulation of the metering or control valve 123 may be effected by conventional linkage means 124. Such linkage means may extend to and be acutated by a speed responsive mechanism 125a of the type, for example, used in speed governor mechanisms.

Thus, through means of conventional linkage mechanisms, the control valve 123 and the diversion valve 109 may be concurrently operable.

This linkage arrangement will be employed to ensure that during relatively lower speed and/or engine load conditions including at, or near idle condition, the metering valve 123 will be opened at least to some extent so as to, in effect, enlarge the volume of each fuel increment discharged by the pump 100 into the passage means 102 and also ensure that, at least to some extent, the diversion valve 109 will be opened.

During relatively higher engine speed and/or load conditions (including normal speed and load conditions) the linkage mechansisms 124 and 121 will be operable to concurrently at least partially close down the valve 123 so as to partially restrict the flow through metering valve 123 and at least partially, and possibly fully, close the diversion valve 109 through operation of the plunger 116.

Thus, in operation of the system shown in FIG. 1, the piston means of fuel pump means 100 will displace an increment of fuel into passage means 102 during each working stroke of the piston means 108.

In this connection, it will be understood that the passage means 102 may include internal passage portions of pump 100, internal passage portions of injection nozzle 101, and any interconnecting conduit means extending between the exterior of the fuel pump and the exterior of the injection nozzle 101.

Each such displaced fuel increment will be transmitted through the passage means 102 from the pump 100 to the injection nozzle 101, with the injection nozzle orifice means 103 being operable to direct or pass the fuel streams 104 into the interior of the engine 107, and preferably into agitation zones 105 and their associated burning loci 106.

In this connection, it is contemplated that the pump 100, conduit means 102, and nozzle 101 will be of the injection system type which functions more or less in the manner of an accumulator such that fuel will be discharged through the orifices 103 at a rate which is different from, and slower than, the rate of displacement of fuel increments from the pump 100 into passage means 102. The time of fuel injection at the nozzle, in general, will be a direct function of the volume of the increment displaced by the fuel pump.

Thus, at a relatively lower engine speed and/or load condition, the linkage means 121 and 124 will be operated so as to, in essence, open the valve means 123 to a wider open position and open the diversion valve 109. This concurrent opening of the valve means 123 and 109 will cause the pump 100 to displace a relatively larger volume fuel increment, per working stroke of the piston means 108, into the passage means 102 while a portion of fuel in the passage means 102 is being di verted out of this passage means.

At a relatively higher speed and/or load condition of the engine 101, the linkage means 124 and 121 will be operated to concurrently move the valve 123 to a more restricted position and close, or at least restrict, the diversion valve 109. This will cause the pump 100 to displace a relatively smaller volume increment per working stroke of piston means 108 into passage means 102 and prevent or at least reduce the degree of diversion of fuel from passage means 102 through the diversion valve 109. In certain instances, the closing of the diversion valve 109 or prevention of diversion may entail a partial flow through the valve 109 but a prevention of the full diversion condition employed at lower speed and/or load conditions. Where such partial diversion is effected, the linkage 121 may position cam 117 so as to appropriately limit the opening of ball 114 through the cam controlled positions of plunger 116.

Through empirical evaluation the flow condition of the diversion valve 109 and the operation of displacement volume control means 123 may be properly correlated with a variety of engine speed and/or load conditions and ranges so as to maintain a desired balance condition over an entire range of operating conditions.

In this connection, it will be recognized that such correlation could entail manual operation of diversion means 109 and displacement volume control means 123 without reliance upon connections with the throttle 125 and/or speed response means 125a. It will be understood that a computerized correlation and control could be effected, utilizing a variety of mechanical, electrical, and/or fluid control systems to appropriately acutate means 109 and/or 123.

Assuming that, through empirical observations and evaluations, the opening and restricting movements of the valve 123 and the opening and restricting movements of the diversion valve 109 are properly correlated, the net result of the operation of this system will be maintain a generally constant or at least acceptably balanced relationship between the periods of time that burning control is to be exercised by agitation zones 105 and loci 106 and the time durations of injection of the sprays 104, with this balance or match being maintained at both relatively lower and relatively higher engine speed and/or load conditions.

this phenomena will result when the engine is optimized for normal or even further higher engine speed and/or load conditions, with this optimization involving the relatively more restricted valve position of the valve means 123 and the relatively more closed position of the diversion valve 109.

At the present time, it is believed that, where a single diverter 109 is associated with a single injection nozzle, this optimization of performance is enhanced by positioning the diverter relatively close to the nozzle.

The explanation of this balancing phenomena may be understood with reference to FIG. 10. However, in relation to the foregoing and following discussion, it will be understood that reference to the displacement volume control means 123 as a metering valve means is by way of example, and that volume control could be effected by other means such .as regulation of the effective stroke of the fuel pump piston means, etc. Balance Phenomena As shown in FIG. 10, increments of duration of the spray streams 104 and the increments of movement of the piston means 108 during which the controlling influence of the agitation zones 105 is to be provided are displayed on an abcissa scale in terms of time.

For relatively higher speed and/or load conditions,

line A illustrates the time duration of a spray 104 which corresponds to a desired control increment X of piston movement. This control increment of piston movement is indicated by the line B. Thus, lines A and B are reflective of a desired match or balance condition between injection and agitation zone control as determined for normal or even further higher engine speed and/or load conditions.

' Lines C and D are reflective of a mismatch" or imbalance condition which would result if the system shown in FIG. 1 were not available in the context of an accumulator-type injection arrangement. Lines C and D are reflective, respectively, of spray duration increments and piston control movement increments during relatively lower speed and load conditions.

FIGS. C and D represent, respectively, the time duration of the sprays 104 and the time duration of the desired piston movement control increment, i.e., X degrees of crankshaft rotation.

Recalling that the time duration of injection of the spray stream 104 is more or less a function of the volume of the pumped fuel increment in an accumulator system, and that a low speed and low load conditions the pumped fuel increment per cycle will be of a smaller volume, the time increment represented by line C will be shortened in relation to line A. Further, since the engine speed is reduced, a longer period of time will be required for the piston to move through the increment of X degrees such that line D becomes longer, in a time sense, in relation to line B.

The net result is that the fuel injection increment reflected by line C does not extend to an acceptable degree throughout the increment of piston movement represented by the line D such that a mismatch or imbalance condition results.

This mismatch or imbalance condition results in the injection of fuel during only a portion of the existence of the controlling agitation zones 105 and loci 106 and creates an unwarranted intensification of fuel injection during an initial portion of the control increment X degrees. This phenomena is believed to produce undesired, localized chilling and rough or erratic burning of fuel.

Such undesired phenomena are avoided at these relatively lower speed and load conditions when the system of FIG. 1 is operated.

Lines E and F illustrate the manner in which the balance'of match condition is restored, at lower speed and/or load condition, so as to avoid the localized chilling and erratic burning characteristics which could be attributed to the conditions reflected by lines C and D.

With the fuel volume increment pumped by pump increased, the time duration of the spray streams 104 reflected by line E will be extended so as to better correlate, in a time framework, with the time duration of the piston control movement increment of X degrees.

Since, during low speed and/or load conditions it would not be desirable for this increased volume of fuel to be injected into the engine interior, the operation of the diversion valve 109 will reduce the volume of fuel actually transmitted to the orifices 103 so that the desired, reduced volume of fuel will be injected into the engine. This reduced volume of fuel will in fact be less than the volume of fuel injected during higher (including normal) load conditions represented by line A.

Even though the operation of the diversion valve 109 is in essence reducing the volume of fuel passing through orifices 103, the increased time duration of injection of the streams through orifices 103 attributed to the larger volume of fuel injected by pump 100 into passage means 102 will not necessarily be reduced. An excessive, or indeed any, reduction in time need not take place because the opening of thediversion valve 109 will reduce the pressure in the passage means 102 and this reduction in pressure will tend to prolong the injection time and offset the tendencyto reduce injection time which would result from the removal of fuel from the passage means 102.

In practicing this invention, it will be recognized that operational parameters will vary, depending upon particular components of the system being employed. Empirical efforts, guided by this disclosure, will be required in connection with each diverse system to appropriately balance the operation of the valve means 123 and the operation of the valve means 109.

It will also be recognized that improved results will be obtained to the extent to which any significant mismatch between increments represented by lines C and D is brought toward a closer condition of balance as reflected by lines E and F, even though the optimum balance reflected by lines E and F is not achieved in an absolute sense.

while basic characteristics of the system have been described in relation to an engine having a single working chamber, consideration should also be given to how the invention could be most advantageously practiced where a multiple working chamber engine was involved.

It would be possible to employ an individual diversion valve 109 in each conduit leading from a fuel pump to the injection nozzle associated with each piston or working chamber. Nevertheless, the problems which would be involved in attempting to balance the mode of operation of such a multiple diiversion valve system could advantageously be avoided by practicing the concept exemplified by the FIG. 6 arrangement.

FIG. 6 depicts a convertional, commercially available, multiple output fuel pump 200.

FIG. 6 depicts in sectional format basic elements of a rotary fuel pump Model DB Roosa Master manufactured by The Standard Screw Company, Hartford Division, having an address at Hartford, Conn., USA.

This pump 200 of FIG. 6 operates in accordance with the basic principles described in U.S. Roosa Pat. No. 2,641,238.

By way of brief description, the pump 200 includes an engine-driven rotor 201 supporting a plurality of radial, pumping piston means 202.

Fuel is supplied to a pumping chamber 203 through a passage means 203a which is connected with a fuel source, the flow of which is controlled by a metering valve. Such a throttle controlled metering valve is shown in FIG. 3 of the aforesaid Roosa U.S. Pat. No. 2,641,238 and is identified by the reference numeral 10 in this FIG. 3 of the Roosa patent. Such a metering valve may comprise the metering means 123 of the FIG. 1 system.

Fuel displaced by the radial piston means 202 during rotation of the rotor 291 is transmitted through a discharge control valve area 204 to distributor passage means 205 and then sequentially to individual output flow paths 206. One such output flow path 206 is shown in FIG. 6 and extends to a single injection nozzle associated with a single piston of a multi-piston engine.

The diversion valve 109previously described is connected with the multiple output pump 200 such that the diversion passage means 112, previously noted, is formed in th body of the pump 200 and communicates with an annular groove 207 formed on the periphery of the rotor 201. This annular groove 207 communicates, via a transverse passage 208, with the fuel discharge control area 204 (only schematically shown) which in turn is in common communication with the distribution passage means 205 and all of the various output flow paths 206 (when these flow paths are in communication with the discharge zone 204 during the appropriate increment of rotation of the rotor 201).

Thus, in the arrangement shown in FIG. 6, the diversion valve 109 operates to divert fuel from a manifold area 207 within the fuel pump which is in common communication with each of the output flow paths 206 such that a constant degree of fuel diversion will be effected in relation to each of the output flow paths and injection nozzles of the multiple piston system.

This principal may be employed with a wide variety of multiple output fuel pumps by merely positioning the diversion valve so that it communicates with a manifold area of the fuel pump which is in common communication with the various output flow paths at the approproate time of operation of the pump.

While this overall diversion principle is believed to be uniquely effective in improving engine operating characteristics, particularly at low load and/or ideal condi tions, still further improvements may be achieved by modifying the spray characteristics of the streams 104 at low speed and/or load conditions.

A technique for effecting such a modification of the spray stream characteristics will now be discussed.

MODIFICATION OF SPRAY CHARACTERISTICS Through this invention it has been discovered that at lower load and/or speed conditions, when an engine is relatively cool, a spaced burning loci engine which has been optimized for higher (including normal) speed and/or load operation may, at times, not operate as smoothly as would be desired.

Through this invention a technique has been developed for improving or modifying the spray characteristics of fuel injected at low speed and/or load conditions (i.e., at or near idle), when the working chamber is relatively cool, so as to reduce the generation of excessive, unburned fuel and generally reduce engine knocking and rough engine performance. This technique has been developed in light of the fact that a conventional, constant dimension orifice will tend to generate a needle-like spray at a low load and/or speed condition and thus tend to lose the fuzz or peripheral spray which is normally associated with the solid" fuel stream core at normal and/or high engine load and/or speed conditions.

The manner in which the fuel stream sprays are modified to attain this improvement in engine performance will now be described with reference to FIGS. 7, 8 and 9.

FIG. 7 depicts a modified fuel injection nozzle 300 which may be employed as the fuel injection nozzle means in connection with the spaced burning loci engine described in the aforesaid Kruckenberg at al. U.S. Pat. No. 3,543,735, in the aforesaid Kruckenberg et al application Serial No. 93,269, and in the preceding discussion of the present invention.

Injection nozzle 300, which may function as the aforesaid injection nozzle means 101, may include an outer body or housing 301 within which an internal body means 302 is telescopingly mounted.

Nozzle body 302 may include, at its lower end, a plurality of downwardly or outwardly directed spray defining orifices 303. One such orifice would be provided in relation to each agitation zone 25 described in connectionwith FIGS. 3, 4 and 5, or in connection with each agitation zone described in connection with FIG. 1 of the present discussion.

Internal body 302 may be secured in position by a threaded fitment 304. A pin 305 may be telescopingly received within aperture means of

elements

304 and 302 so as to permit controlled rotational positioning of the body 302 relative to the fitment 304. This alignment function will ensure that a fuel passage 306 of internal body 302 is disposed in communicating relation with an inlet fuel passage 307 of fitment 304.

A valve member 308 may be telescopingly received within a cylinder portion 309 of fitment 302 and project downwardly through fuel passage 310. Passage 310 may provide communication between the transfer passage 306 and a valve seat 311.

Valve seat 311 is generally frustoconical in nature and is intersected at its lower end by the orifices 303.

A frustoconical valve member tip 312 is operable to matingly and conformingly engage the seat 311, in the seated position of the valve 308, and overlap and close the inlet mouths 313 of the orifices 303.

A piston-like extension 314 projects upwardly (as shown in FIG. 7), from valve body 308 through a wafer or disc-like valve stop 315. Valve stop 315 has an annular shoulder means 316 which is operable to engage a ledge 317, carfied by theupper end of the valve member 308, so as to limit and define the uppermost or fully open valve position.

An inverted, mushroom-shaped, fitment 318 may abuttingly engage protrusion 314 and be pressed or biased toward this protrusion by a coil spring 319.

In a conventional manner, a vent 320 may be provided in fitment 304. This vent would communicate with a cavity 321 within which the spring 319 is mounted. The function of the vent 320 would be to remove from the nozzle that fuel which leaks around the portion of-the valve 308 which is received within a a vqbo uyl d l HQEQMQQ: a a

As will be notedfrom FIG 7, piston-like portion 322 of valve 308 which may be provided and received within the cylinder portion 309 may be somewhat larger in diameter than a lower valve portion 323 which projects into the cavity 310. This difference in diameter permits the valve member 308 to raise in response to the pressure of fuel in the cavity 310 so as to permit the las ff slthta i thso fisss l i At normal or relatively higher engine speed and/or load conditions, and particularly in a system where the aforesaid diversion valve 109 is in a relatively closed or restricted position, the pressure of fuel in the cavity 310 would be at a relatively higher level so that the valve 308 would tend to stabilize in a fully open position, with the stop 3 l l eng a g ing the ab utment 316.

This fully opened valve position is depicted in FIG. 9. As shown in FIG. 9, the frustoconical surface 312 has been displaced from its FIG. 7 position of overlying cooperation with the orifice inlets 313. As is schematically shown in FIG. 9, with the valve 308 thus raised, fuel enters the inlets 313 in a generally axial pattern and fuel exits from the orifices 303 in the form of generally solid or discrete fuel streams 322, albeit possibly nificatly less than the pressure existing in this cavity at normally/higher load and/o'rspeed conditions. Thus by Needle Lift Diameter of Orifice 303 Length of Orifice 303 Slope of Axis of Orifice 303 Relative to Longitudinal Axis of Valve 308 Slope of Surfaces 3] l and 3l2 Relative to Longitudinal Axis of Valve 308 Axial Height of Frustoconical Tip 3l2 omized or widely diverging flow stream 333 will issue- .fr 0m the orifices 303. i

This relatively billowing stream 333 is significantly more atomized than the generally cohesive or solid stream 332 generated in the fully open valve position depicted in FIG. 9.

Thus, with this arrangement, and at relatively lower speed and/or load conditions of the engine, the FIG. 8 valve position will automatically result due to the lower fuel pressure acheived through operation of the diversion valve 109. This valve positioning will improve the performance of the burning loci engine at this engine range by maki ignition ,m9r ia9ile The two-stage characteristics of the nozzle depicted in FIGS. 7, 8 and 9 will also tend to produce an enhanced fuzziness" or degree of atomization during the initial opening of the injection valve, even at normal or relatively even higher engine speed and/or load conditions. This phenomena, in and of itself, will tend to improve and facilitate the commencement of fuel burning or ignition during each working cycle of the spaced 999M529 95199- All this notwithstanding, and even with the use of the two-stage injection nozzle as above described, the burning loci engine, for the most part, will certainly during normal and even higher engine speed and/or load conditions, operate with the burning loci being generated and maintained substantially in the manner described in the Kruckenberg et al. U.S. Pat. No. 3,543,735 and the Kruckenberg et al. application Ser. 925 2 9...

By way of example, it is contemplated that the twostage phenomena may be advantageously accomplished within the following dimensional parameters:

Lower Loud Higher Load (FIG. 8) (FIG. 9)

(.004"-.005"): (.0l6".0l8"l:

per r tsl ellisaaanuq n of it.

'spring 31 9, this lower pressure in cavity 310 may becaused to only partially elevate the valve 308 so that it assumes the intermediate position schematically depicted in FIG. 8. Such a position of valve 308 could be a onsequence of the open position of valve 109.

In this intermediate valve position, the fuel pressure in cavity 310 acting on the valve body piston portion 322 would be such as to only partially overcome the force of spring 319 and not sufficient to fully overcome this spring force to the extent necessary to raise the step 317 into abutting engagement with the abutment higher, engine load andjor speed conditions.

MAJOR ADVANTAGES AND SUMMARY 0F 9 INVENTION The concept presented through this invention entailing modifications of displacement increment of fuel pumps, coupled with the diversion phenomena, produces a significantly enhanced and smoother performance characteristic for the burning loci type engine, particularly at lower engine speed and/or load conditions.

ignificantly, all of this is achieved without adversely affecting the basic advantages of the burning loci type engine where they are most important, i.e. at normal and even higher engine loads.

The concept of increasing fuel pump injection increment volume coupled with the use of fuel diversion, so as to maintain a better balance between spray increment duration and the control increment provided by agitation zones, is achieved in direct contradiction of the teaching of prior patents such as Burman U.S. Pat. No. 2,794,397.

To the extent that Burman teaches diversion, but emphasizes the maintenance of a constant pumping volume increment, the art is led away from the present invention and its attendant advantages.

In the context of a multiple working chamber engine, the manifold location of the diversion valve, in relation to the fuel pump, eliminates the necessity of attempting to balance a plurality of separate diversion valves.

The two-phase spray characteristic phenomena contributes to ease of ignition of burning under all engine conditions and is believed to provide smoother engine performance at low load conditions.

Somewhat surprisingly, it has also been discovered that the two-phase concept of this invention tends to minimize the clogging of fuel nozzles. In fact, it has been noted in certain instances that effectively operable nozzle orifice life, prior to clogging, may be extended from somewhere on the order of five to thirty hours up to on the order of 250 hours, and more.

This increase in nozzle operating life may be due to the fact that the fuel flow through the orifices, which produces the billowing spray pattern, tends to flush pockets ofstagnant" fuel out of the orifice. Such quiescent zones could tend to form adjacent longitudinally intermediate orifice wall zones due to a contracted nature of solid fuel stream flow in such areas. The formation of such stagnant" or quiescent zones would be conducive to fuel oxidation, thereby inducing orifice clogging.

Those skilled in the fuel injection art are aware that two-phase injection nozzles, which operate in a different manner at different conditions of valve position, are known. For example, a Kenworthy US. Pat. No. 1,833,080 discloses a two-stage nozzle where at a condition of partial lift a frustoconical tip opens some orifrees, while at a full lift condition still other orifices are open. A similar disclosure is contained in a Lang US. Pat. No. 2,757,967. However, art such as this does not suggest the two-stage concept of the present invention or the context of the spaced burning loci engine. If anything, since the basic operating characteristic of the burning loci engine involves the use of relatively solid fuel streams, one would not expect or anticipate recourse to two-stage nozzles, with one stage involving a billowing spray, where the burning loci engine was concerned.

The overall consequence of the employment of these various aspects of the invention in the context of a spaced burning loci engine entails not merely an improvement in engine operating characteristic but a significant reduction in the generation of noxious oxides of nitrogen.

Tests conducted thus far indicate that the NO, con tent of exhaust gas may be reduced to somewhere on the order of 300 parts per million when the present invention is practiced. This constitutes a significant rcduction in the generation of nitrous oxides and is believed to be attributable primarily to the basic operating characteristics of the spaced burning loci engine. However, these characteristics are also believed to be further enhanced through the present invention.

While a variety of modifications with respect to apparatus and techniques have been presented in, and suggested through, this disclosure, as well as the disclosures-of the aforesaid Kruckenberg et al. U.S. Pat. No. 3,543,735 and the Kruckenberg et al. application Ser. No. 93,269, those skilled in the art and familiar with the present disclosure may well envision other modifications, additions, deletions, substitutions or changes which would fall within the purview of the invention as set forth in the appended claims.

What is claimed is: 1. In a method of effecting combustion in internal combustion engines, which method is characterized by: generating, within internal combustion engine means, and in energy communicating relation with engine piston means movable in cylinder means of said engine means, a plurality of generally mutually distinct burning loci, with said burning loci defining generally spaced centers of burning; concurrently, and during a working stroke of said engine piston means, transmitting combustion supporting gas, heated by compression and combustion, into said burning loci, and generating and transmitting streams of combustible fuel into said burning loci, each said burning loci substantially receiving at least one of said fuel streams and at least some of said heated gas; limiting the time duration of the generation of said fuel streams so that at least the majority of fuel in said streams passes into said burning loci during a working stroke of said engine piston means; providing a plurality of spaced wall means, with each such wall means peripherally confining and definmg a fuel and heated gas agitation zone individually associated with and communicating with a said burning loci; each said peripherally confined agitation zone and a burning loci associated therewith receiving fuel from at least one fuel stream directed thereinto during said working stroke of said engine piston means; maintaining the existence and a generally discrete relation of said burning loci during said working stroke of said engine piston means; and utilizing energy generated through operation of said burning loci to induce said working stroke of said engine piston means; the improvement comprising:

causing fuel pump piston means to displace an increment of fuel from fuel pump means; transmitting said displaced increment of fuel through passasge means leading from said fuel pump piston means to fuel injection nozzle means operable to generate said fuel streams, with said fuel injection nozzle means being operable to pass said fuel streams into said agitation zones and burning loci associated therewith; discharging said fuel streams from said nozzle means into said agitation zones and burning loci associated therewith at a rate different from, and slower than, the rate of displacement of said fuel increment from said fuel pump means into said passage means; and at a relatively lower engine speed for any given load condition displacing a relatively larger volume fuel increment per working stroke of said engine piston means from said fuel pump means into said passage means, and diverting fuel delivered by the fuel pump means into said passage means, between said fuel pump piston means and said injection nozzle means, from said passage means, and at a relatively higher engine speed for any given load condition displacing a relatively smaller volume fuel increment per working stroke of said engine piston means from said fuel pump means into said passage means, and at least reducing the degree of said diversion of fuel from said passage means, and i said steps of displacing and diverting being operable to substantially avoid an undesirable mismatching of the time duration of discharge of said fuel streams into said agitation zones, in relation to a desired increment of movement of said enginepiston means. 2. A method as set forth in claim 1, further comprismg:

providing in said fuel injection nozzle means a plurality of injection nozzles, each individually associated with a separate working chamber of said internal combustion engine means; providing through said passage means a plurality of separate fuel paths, each leading individually to one of said injection nozzles; during said relatively lower engine speed for any given load condition, diverting said fuel from a portion of said passage means which is in common communication with said plurality of separate fuel paths; and l effecting said displacement of said relatively larger volume fuel increment during each working stroke of engine piston means individually associated with each of said separate working chambers of said internal combustion engine means. 3. A method as described in claim 1 further comprisduring said relatively lower engine speed for any given load condition, partially obstructing orifice means of said fuel injection nozzle means to produce a generally radial flow pattern of fuel leading to said orifice means, and produce a generally diverging spray of fuel leading from said orifice means; and during said relatively higher engine speed for any given load condition providing a generally axial flow of fuel leading to said orifice means, and forming a generally solid configuration of fuel streams leaving said orifice means and comprising said fuel stream received by said agitation zones and burning loci associated therewith.

4. A method as described in claim 1, further comprising, at least during said relatively higher engine speed for any given load condition:

providing, through said spaced wall means, flow path means in said engine means which comprise said agitation zones and define the location of said burning loci;

during at least a portion of said working stroke of said engine piston means, generally enlarging the flow capacity of said flow path means;

progressively increasing amass flow rate off combustion supporting gas transmitted to said burning loci and passing into said flow path means during said working stroke of said engine piston means as said flow path means generally enlarge their flow capacity; and

at least during said working stroke of said piston means, progressively increasing the mass flow rate of combustible fuel transmitted to said burning loci, with said progressive increase in the mass flow rate of fuel continuing for at least a majority of the time during'which said fuel streams are received by said agitation zones and burning loci associated therewith.

5. A method as set forth in claim 1, further comprising:

effecting operation of a plurality of working chambers of said internal combustion engine by providing in said fuel injection nozzle means a plurality of injection nozzles, each individually associated with a separate working chamber of said internal combustion engine means, providing through said passage means a plurality of separate fuel paths, each leading individually to one of said injection nozzles, during said relatively lower engine speed for any given load condition diverting said fuel from a portion of said passage means which is in common communication with said plurality of separate fuel paths, and effecting said displacement of said relatively larger volume fuel increment during each working stroke of engine piston means individually associated with each of said separate working chambers of said internal combustion engine means; modifying the spray characteristics of said fuel injection nozzle means by during said relatively lower engine speed for any given load condition, partially obstructing orifice means of said fuel injection nozzle means to produce a generally radial flow pattern of fuel leading to said orifice means, and produce a generally diverging spray of fuel leading from said orifice means, and during said relatively higher engine speed for any given load condition providing a generally axial flow of fuel leading to said orifice means, and forming a generally solid configuration of fuel streams leaving said orifice means and comprising said fuel stream received by said agitation zones and burning loci associated therewith; and

at least during said relatively higher engine speed for any given load condition providing, through said spaced wall means, flow path means in said engine means which comprise said agitation zones and define the location of said burning loci,

during at least a portion of said working stroke of said engine piston means, generally enlarging the flow capacityof said flow path means,

progressively increasing a mass flow rate of combustion supporting gas transmitted to said burning loci and passing into said flow path means during said working stroke of said engine piston means as said flow path means generally enlarge their flow capacity, and

at least during said working stroke of said piston means, progressively increasing the mass flow rate of combustible fuel transmitted to said burning loci, with said progressive increase in the mass flow rate of fuel continuing for at least a majority of the time during which said fuel streams are received by said agitation zones and burning loci associated therewith.

6. A method of modifying the injection characteristics of fuel injection nozzle means, said method comprising:

. 25 causing fuel pump piston means to displace an increcondition of said internal combustion engine means displacing a relatively larger volume fuel increment per working stroke of said engine means from said fuel pump means into said passage means, and diverting fuel delivered by the fuel pump means into said passage means, between said piston means, from said passage means; and at a relatively higher speed for any given load condition of said internal combustion engine means displacing a relatively smaller fuel increment per working stroke of said engine means from said fuel pump means into said passage means, and at least reducing the degree of said diversion of fuel from said passage means, and said steps of displacing and diverting being operable to substantially avoid an undesirable mismatching of the time duration of discharge of said fuel streams into said agitation zones, in relation to a desired increment of movement of said engine piston means. 7. A method of modifying the injection characteristics of fuel injection nozzle means as set forth in claim 6, further comprising:

providing in said fuel injection nozzle means a plurality of injection nozzles, each individually associated with a separate working chamber of said internal combustion engine means;

providing through said passage means a plurality of separate fuel paths, each leading individually to one of said injection nozzles; and

during said relatively lower engine speed for any given load condition, diverting said fuel from a portion of said passage means which is in common communication with said plurality of separate fuel paths; and

effecting said displacement of said relatively larger volume fuel increment during each working stroke of engine piston means individually associated with each of said separate working chamber of said in ternal combustion engine means.

8. A method for modifying the injection characteristics of fuel injection nozzle means, as set forth in claim 6, further comprising:

during said relatively lower engine speed for any given load condition, partially obstructing orifice means of said fuel injection nozzle means to produce a generally radial flow pattern of fuel leading to said orifice means, and

produce a generally diverging spray of fuel leading from said orifice means and passing into said interior of said internal combustion engine means; and

during said relatively higher engine speed for any given load engine condition providing a generally axial flow of fuel leading to said orifice means, and

forming generally solid fuel stream means leaving said orifice means and passing into said interior of said internal combustion engine means.

9. A method of modifying the injection characteristics of fuel injection nozzle means as set forth in claim 6, further comprising:

providing flow path means in said engine means which define and at least partially confine, fuel and gas agitation zones; during at least a portion of a working stroke of engine piston means of said engine means, generally enlarging the flow capacity of said flow path means;

progressively increasing a mass flow rate of combustion supporting gas passing through said flow path means during said working stroke of said engine piston means as said flow path means generally enlarge their flow capacity; and

at least during said working stroke of said engine piston means, progressively increasing the mass flow rate of combustible fuel discharged from said injection nozzle means, and directing said fuel streams into said agitation zones.

10. A method of modifying the injection characteristics of fuel injection nozzle means as set forth in claim 6, further comprising:

effecting operation of a plurality of working chambers of said internal combustion engine by providing in said fuel injection nozzle means a plurality of injection nozzles, each individually associated with a separate working chamber of said internal combustion engine means,

providing through said passage means a plurality of separate fuel paths, each leading individually to one of said injection nozzles,

during said relatively lower engine speed for any given load condition, diverting said fuel from a portion of said passage means which is in cornmon communication with said plurality of separate fuel paths, and effecting said displacement of said relatively larger volume fuel increment during each working stroke of engine piston means individually associated with each of said separate working chamber of said internal combustion engine means; modifying the spray characteristics of said fuel injection nozzle means by during said relatively lower engine speed for any given load condition and in conjunction with said diversion of fuel, partially obstructing orifice means of said fuel injection nozzle means to produce radial flow pattern of fuel leading to said orifice means, and produce a generally diverging spray of fuel leading from said orifice means and passing into said interior of said internal combustion engine means; and during said relatively higher engine speed for any given load engine condition and while preventing said diversion of fuel providing a generally axial flow of fuel leading to said orifice means, and forming generally solid fuel stream means leaving said orifice means and passing into said interior of said internal combustion engine means; and at least during said relatively higher engine speed for any given load condition providing flow path means in said engine means which define and at least partially confine, fuel and gas agitation zones, during at least a portion of a working stroke of engine piston means of said engine means, generally enlarging the flow capacity of said flow path means, progressively increasing a mass flow rate of combustion supporting gas passing through said flow path means during said working stroke of said engine piston means as said flow path means generally enlarge their flow capacity, and at least during said working stroke of said engine piston means, progressively increasing the mass flow rate of combustible fuel discharged from said-injection nozzle means, and directing said fuel streams into said agitation zones.

1 1. In an apparatus for effecting combustion in internal combustion engines, which apparatus is characterized by:

means for generating, within internal combustion engine means, and in energy communicating relation with engine piston means movable in cylinder means of said engine means, a plurality of generally mutually distinct burning loci, with said burning loci defining generally spaced centers of burning;

means for concurrently, and during a working stroke of said engine piston means,

transmitting combustion supporting gas, heated by compression and combustion, into said burning loci, and

generating and transmitting streams of combustible fuel into said burning loci,

each said burning loci substantially receiving at least one of said fuel streams and at least some of said heated gas;

means for limiting the time duration of the generation of said fuel streams so that at least the majority of fuel in said streams passes into said burning loci during a working stroke of said engine piston means; means providing a plurality of spaced wall means, with each such wall means peripherally confining and defining a fuel and heated gas agitation zone individually associated with and communicating with a said burning loci; each said peripherally confined agitation zone and a burning loci associated therewith receiving fuel from at least one fuel stream directed thereinto during said working stroke of said engine piston means; means maintaining the existence and a generally discrete relation of said burning loci during said working stroke of said engine piston means; and means utilizing energy generated through operation of said burning loci to induce said working stroke of said engine piston means; the improvement comprising:

fuel pump means; fuel pump piston means operable to displace an increment of fuel from said fuel pump means; fuel injection nozzle means operable to generate said fuel streams; passage means for transmitting said displaced increment of fuel from said fuel pump piston means to said fuel injection nozzle means, with said fuel injection nozzle means being operable to pass said fuel streams into said agitation zones and burning loci associated therewith; means for discharging said fuel streams from said nozzle means into said agitation zones and burning loci associated therewith at a rate different from, and slower than, the rate of displacement of said fuel increment from said fuel pump means into said passage means; means operable, at a relatively lower engine speed for any given load condition, to displace a relatively larger volume fuel increment per working stroke of said engine piston means from said fuel pump means into said passage means, and divert fuel delivered by the fuel pump means into said passage means, between said fuel pump piston means and said injection nozzle means, from said passage means; and means operable, at a relatively higher engine speed for any given load condition, to displace a relatively smaller volume fuel increment per working stroke of said engine piston means from said fuel pump means into said passage means, and at least reduce the degree of said diversion of fuel from said passage means, and said means to displace and divert being operable to substantially avoid an undesirable mismatching of the time duration of discharge of said fuel streams into said agitation zones, in relation to a desired increment of movement of said engine piston means. 12. An apparatus as set forth in claim 11, further comprising:

a plurality of injection nozzles included in said fuel injection nozzle means each being individually as sociated with a separate working chamber of said internal combustion engine means;

means providing through said passage means a plurality'of separate fuel paths, each leading individually to one of said injection nozzles;

means operable during said relatively lower engine speed for any given load condition, to divert said fuel from a portion of said passage means which is in common communication with said plurality of separate fuel paths; and

means for effecting said displacement of said relatively larger volume fuel increment during each working stroke of engine piston means individually associated with each of said separate working chambers of said internal combustion engine means.

13. An apparatus as described in claim 11 further comprising:

orifice means included in said fuel injection nozzle means;

means operable during said relatively lower engine speed for any given load condition, to partially obstruct said orifice means of said fuel injection nozzle means and produce a generally radial flow pattern of fuel leading to said orifice means, and produce a generally diverging spray of fuel leading from said orifice means; and means operable during said relatively higher engine speed for any given load condition to provide a generally axial flow of fuel leading to said orifice means, and

form a generally solid configuration of fuel streams leaving said orifice means and comprising said fuel stream received by said agitation zones and burning loci associated therewith.

14. An apparatus as described in claim 11, further comprising:

flow path means in said engine means provided by said spaced wall means which comprise said agitation zones and define the location of said burning loci;

means operable during at least a portion of said working stroke of said engine piston means, to generally enlarge the flow capacity of said flow path means;

means operable to progressively increase a mass flow rate of combustion supporting gas transmitted to said burning loci and passing into said flow path means during said working stroke of said engine piston means as said flow path means generally enlarge their flow capacity; and

means operable at least during said working stroke of said piston means, to progressively increase the mass flow rate of combustible fuel transmitted to i said burning loci, with said progressive increase in the mass flow rate of fuel continuing for at least a majority of the time during which said fuel streams are received by said agitation zones and burning loci associated therewith.

15. Apparatus as set forth in claim 11, further comprising:

means for effecting operation of a plurality of working chambers of said internal combustion engine and including a plurality of injection nozzles included in said fuel injection nozzle means, each being individually associated with a separate working chamber of said internal combustion engine means,

means providing through said passage means a plurality of separate fuel paths, each leading individually to one of said injection nozzles,

means operable during said relatively lower engine speed for any given load condition to divert said fuel from a portion of said passage means which is in common communication with said plurality of separate fuel paths, and

means for effecting said displacement of said relatively larger volume fuel increment during each working stroke of engine piston means individually associated with each of said separate working chambers of said internal combustion engine means;

means for modifying the spray characteristics of said fuel injection nozzle means and including flow path means in said engine means provided by said spaced wall means which comprise said agitation zones and define the location of said burning loci,

means operable during at least a portion of said working stroke of said engine piston means, to generally enlarge the flow capacity of said flow path means,

means operable to progressively increase a mass flow rate of combustion supporting gas transmitted to said burning loci and passing into said flow path means during said working stroke of said ongine piston means as said flow path means generally enlarge their flow capacity, and

means operable at least during said working stroke of said piston means, to progressively increase the mass flow rate of combustible fuel transmitted to said burning loci, with said progressive increase in the mass flow rate of fuel continuing for at least a majority of the time during which said fuel streams are received by said agitation zones and burning loci associated therewith.

16. An apparatus for modifying injection characteristics of fuel injection nozzle means, said apparatus comprising:

fuel pump means;

fuel pump piston means operable to displace an increment of fuel from said fuel pump means;

fuel injection nozzle means operable to generate said fuel streams;

passage means for transmitting said displaced increment of fuel from said fuel pump piston means to said fuel injection nozzle means, with said fuel injection nozzle means being operable to pass fuel into the interior of internal combustion engine means;

means for discharging fuel from said nozzle means into the interior of said internal combustion engine means at a rate different from, and slower than, the rate of displacement of said fuel increment from said fuel pump means into said passage means;

means operable at a relatively lower engine speed for any given load condition of said internal combustion engine means to displace a relatively larger volume fuel increment per working stroke of said engine means from

Claims

1. In a method of effecting combustion in internal combustion engines, which method is characterized by: generating, within internal combustion engine means, and in energy communicating relation with engine piston means movable in cylinder means of said engine means, a plurality of generally mutually distinct burning loci, with said burning loci defining generally spaced centers of burning; concurrently, and during a working stroke of said engine piston means, transmitting combustion supporting gas, heated by compression and combustion, into said burning loci, and generating and transmitting streams of combustible fuel into said burning loci, each said burning loci substantially receiving at least one of said fuel streams and at least some of said heated gas; limiting the time duration of the generation of said fuel streams so that at least the majority of fuel in said streams passes into said burning loci during a working stroke of said engine piston means; providing a plurality of spaced wall means, with each such wall means peripherally confining and defining a fuel and heated gas agitation zone individually associated with and communicating with a said burning loci; each said peripherally confined agitation zone and a burning loci associated therewith receiving fuel from at least one fuel stream directed thereinto during said working stroke of said engine piston means; maintaining the existence and a generally discrete relation of said burning loci during said working stroke of said engine piston means; and utilizing energy generated through operation of said burning loci to induce said working stroke of said engine piston means; the improvement comprising: causing fuel pump piston means to displace an increment of fuel from fuel pump means; transmitting said displaced increment of fuel through passasge means leading from said fuel pump piston means to fuel injection nozzle means operable to generate said fuel streams, with said fuel injection nozzle means being operable to pass said fuel streams into said agitation zones and burning loci associated therewith; discharging said fuel streams from said nozzle means into said agitation zones and burning loci associated therewith at a rate different from, and slower than, the rate of displacement of said fuel increment from said fuel pump means into said passage means; and at a relatively lower engine speed for any given load condition displacing a relatively larger volume fuel increment per working stroke of said engine piston means from said fuel pump means into said passage means, and diverting fuel delivered by the fuel pump means into said passage means, between said fuel pump piston means and said injection nozzle means, from said passage means, and at a relatively higher engine speed for any given load condition displacing a relatively smaller volume fuel increment per working stroke of said engine piston means from said fuel pump means into said passage means, and at least reducing the degree of said diversion of fuel from said passage means, and said steps of displacing and diverting being operable to substantially avoid an undesirable mismatching of the time duration of discharge of said fuel streams into said agitation zones, in relation to a desired increment of movement of said engine piston means.

2. A method as set forth in claim 1, further comprising: providing in said fuel injection nozzle means a plurality of injection nozzles, each individually associated with a separate working chamber of said internal combustion engine means; providing through said passage means a plurality of separate fuel paths, each leading individually to one of said injection nozzles; during said relatively lower engine speed for any given load condition, diverting said fuel from a portion of said passage means which is in common communication with said plurality of separate fuel paths; and effecting said displacement of said relatively larger volume fuel increment during each working stroke of engine piston means individually associated with each of said separate working chambers of said internal combustion engine means.

3. A method as described in claim 1 further comprising: during said relatively lower engine speed for any given load condition, partially obstructing orifice means of said fuel injection nozzle means to produce a generally radial flow pattern of fuel leading to said orifice means, and produce a generally diverging spray of fuel leading from said orifice means; and during said relatively higher engine speed for any given load condition providing a generally axial flow of fuel leading to said orifice means, and forming a generally solid configuration of fuel streams leaving said orifice means and comprising said fuel stream received by said agitation zones and burning loci associated therewith.

4. A method as described in claim 1, further comprising, at least during said relatively higher engine speed for any given load condition: providing, through said spaced wall means, flow path means in said engine means which comprise said agitation zones and define the location of said burning loci; during at least a portion of said working stroke of said engine piston means, generally enlarging the flow capacity of said flow path means; progressively increasing a mass flow rate of combustion supporting gas transmitted to said burning loci and passing into said flow path means during said working stroke of said engine piston means as said flow path means generally enlarge their flow capacity; and at least during said working stroke of said piston means, progressively increasing the mass flow rate of combustible fuel transmitted to said burning loci, with said progressive increase in the mass flow rate of fuel continuing for at least a majority of the time during which said fuel streams are received by said agitation zones and burning loci associated therewith.

5. A method as set forth in claim 1, further comprising: effecting operation of a plurality of working chambers of said internal combustion engine by providing in said fuel injection nozzle means a plurality of injection nozzles, each individually associated with a separate working chamber of said internal combustion engine means, providing through said passage means a plurality of separate fuel paths, each leading individually to one of said injection nozzles, during said relatively lower engine speed for any given load condition diverting said fuel from a portion of said passage means which is in common communication with said plurality of separate fuel paths, and effecting said displacement of said relatively larger volume fuel increment during each working stroke of engine piston means individually associated with each of said separate working chambers of said internal combustion engine means; modifying the spray characteristics of said fuel injection nozzle means by during said relatively lower engine speed for any given load condition, partially obstructing orifice means of said fuel injection nozzle means to produce a generally radial flow pattern of fuel leading to said orifice means, and produce a generally diverging spray of fuel leading from said orifice means, and during said relatively higher engine speed for any given load condition providing a generally axial flow of fuel leading to said orifice means, and forming a generally solid configuration of fuel streams leaving said orifice means and comprising said fuel stream received by said agitation zones and burning loci associated therewith; and at least during said relatively higher engine speed for any given load condition providing, through said spaced wall means, flow path means in said engine means which comprise said agitation zones and define the location of said burning loci, during at least a portion of said working stroke of said engine piston means, generally enlarging the flow capacity of said flow path means, progressively increasing a mass flow rate of combustion supporting gas transmitted to said burning loci and passing into said flow path means during said working stroke of said engine piston means as said flow path means generally enlarge their flow capacity, and at least during said working stroke of said piston means, progressively increasing the mass flow rate of combustible fuel transmitted to said burning loci, with said progressive increase in the mass flow rate of fuel continuing for at least a majority of the time during which said fuel streams are received by said agitation zones and burning loci associated therewith.

6. A method of modifying the injection characteristics of fuel injection nozzle means, said method comprising: causing fuel pump piston means to displace an increment of fuel from fuel pump means; transmitting said displaced increment of fuel through passage means leading from said fuel pump piston means to fuel injection nozzle means, with said fuel injection nozzle means being operable to pass fuel into the interior of internal combustion engine means; discharging fuel from said nozzle means into the interior of said internal combustion engine means at a rate different from, and slower than, the rate of displacement of said fuel increment from said fuel pump means into said passage means; at a relatively lower engine speed for any given load condition of said internal combustion engine means displacing a relatively larger volume fuel increment per working stroke of said engine means from said fuel pump means into said passage means, and diverting fuel delivered by the fuel pump means into said passage means, between said piston means, from said passage means; and at a relatively higher speed for any given load condition of said internal combustion engine means displacing a relatively smaller fuel increment per working stroke of said engine means from said fuel pump means into said passage means, and at least reducing the degree of said diversion of fuel from said passage means, and said steps of displacing and diverting being operable to substantially avoid an undesirable mismatching of the time duration of discharge of said fuel streams into said agitation zones, in relation to a desired increment of movement of said engine piston means.

7. A method of modifying the injection characteristics of fuel injection nozzle means as set forth in claim 6, further comprising: providing in said fuel injection nozzle means a plurality of injection nozzles, each individually associated with a separate working chamber of said internal combustion engine means; providing through said passage means a plurality of separate fuel paths, each leading individually to one of said injection nozzles; and during said relatively lower engine speed for any given load condition, diverting said fuel from a portion of said passage means which is in common communication with said plurality of separate fuel paths; and effecting said displacement of said relatively larger volume fuel increment during each working stroke of engine piston means individually associated with each of said separate working chamber of said internal combustion engine means.

8. A method for modifying the injection characteristics of fuel injection nozzle means, as set forth in claim 6, further comprising: during said relatively lower engine speed for any given load condition, partially obstructing orifice means of said fuel injection nozzle means to produce a generAlly radial flow pattern of fuel leading to said orifice means, and produce a generally diverging spray of fuel leading from said orifice means and passing into said interior of said internal combustion engine means; and during said relatively higher engine speed for any given load engine condition providing a generally axial flow of fuel leading to said orifice means, and forming generally solid fuel stream means leaving said orifice means and passing into said interior of said internal combustion engine means.

9. A method of modifying the injection characteristics of fuel injection nozzle means as set forth in claim 6, further comprising: providing flow path means in said engine means which define and at least partially confine, fuel and gas agitation zones; during at least a portion of a working stroke of engine piston means of said engine means, generally enlarging the flow capacity of said flow path means; progressively increasing a mass flow rate of combustion supporting gas passing through said flow path means during said working stroke of said engine piston means as said flow path means generally enlarge their flow capacity; and at least during said working stroke of said engine piston means, progressively increasing the mass flow rate of combustible fuel discharged from said injection nozzle means, and directing said fuel streams into said agitation zones.

10. A method of modifying the injection characteristics of fuel injection nozzle means as set forth in claim 6, further comprising: effecting operation of a plurality of working chambers of said internal combustion engine by providing in said fuel injection nozzle means a plurality of injection nozzles, each individually associated with a separate working chamber of said internal combustion engine means, providing through said passage means a plurality of separate fuel paths, each leading individually to one of said injection nozzles, during said relatively lower engine speed for any given load condition, diverting said fuel from a portion of said passage means which is in common communication with said plurality of separate fuel paths, and effecting said displacement of said relatively larger volume fuel increment during each working stroke of engine piston means individually associated with each of said separate working chamber of said internal combustion engine means; modifying the spray characteristics of said fuel injection nozzle means by during said relatively lower engine speed for any given load condition and in conjunction with said diversion of fuel, partially obstructing orifice means of said fuel injection nozzle means to produce a generally radial flow pattern of fuel leading to said orifice means, and produce a generally diverging spray of fuel leading from said orifice means and passing into said interior of said internal combustion engine means; and during said relatively higher engine speed for any given load engine condition and while preventing said diversion of fuel providing a generally axial flow of fuel leading to said orifice means, and forming generally solid fuel stream means leaving said orifice means and passing into said interior of said internal combustion engine means; and at least during said relatively higher engine speed for any given load condition providing flow path means in said engine means which define and at least partially confine, fuel and gas agitation zones, during at least a portion of a working stroke of engine piston means of said engine means, generally enlarging the flow capacity of said flow path means, progressively increasing a mass flow rate of combustion supporting gas passing through said flow path means during said working stroke of said engine piston means as said flow path means generally enlarge their flow capacity, and at least during said working stroke of said engine piston means, progressively increasing the mAss flow rate of combustible fuel discharged from said injection nozzle means, and directing said fuel streams into said agitation zones.

11. In an apparatus for effecting combustion in internal combustion engines, which apparatus is characterized by: means for generating, within internal combustion engine means, and in energy communicating relation with engine piston means movable in cylinder means of said engine means, a plurality of generally mutually distinct burning loci, with said burning loci defining generally spaced centers of burning; means for concurrently, and during a working stroke of said engine piston means, transmitting combustion supporting gas, heated by compression and combustion, into said burning loci, and generating and transmitting streams of combustible fuel into said burning loci, each said burning loci substantially receiving at least one of said fuel streams and at least some of said heated gas; means for limiting the time duration of the generation of said fuel streams so that at least the majority of fuel in said streams passes into said burning loci during a working stroke of said engine piston means; means providing a plurality of spaced wall means, with each such wall means peripherally confining and defining a fuel and heated gas agitation zone individually associated with and communicating with a said burning loci; each said peripherally confined agitation zone and a burning loci associated therewith receiving fuel from at least one fuel stream directed thereinto during said working stroke of said engine piston means; means maintaining the existence and a generally discrete relation of said burning loci during said working stroke of said engine piston means; and means utilizing energy generated through operation of said burning loci to induce said working stroke of said engine piston means; the improvement comprising: fuel pump means; fuel pump piston means operable to displace an increment of fuel from said fuel pump means; fuel injection nozzle means operable to generate said fuel streams; passage means for transmitting said displaced increment of fuel from said fuel pump piston means to said fuel injection nozzle means, with said fuel injection nozzle means being operable to pass said fuel streams into said agitation zones and burning loci associated therewith; means for discharging said fuel streams from said nozzle means into said agitation zones and burning loci associated therewith at a rate different from, and slower than, the rate of displacement of said fuel increment from said fuel pump means into said passage means; means operable, at a relatively lower engine speed for any given load condition, to displace a relatively larger volume fuel increment per working stroke of said engine piston means from said fuel pump means into said passage means, and divert fuel delivered by the fuel pump means into said passage means, between said fuel pump piston means and said injection nozzle means, from said passage means; and means operable, at a relatively higher engine speed for any given load condition, to displace a relatively smaller volume fuel increment per working stroke of said engine piston means from said fuel pump means into said passage means, and at least reduce the degree of said diversion of fuel from said passage means, and said means to displace and divert being operable to substantially avoid an undesirable mismatching of the time duration of discharge of said fuel streams into said agitation zones, in relation to a desired increment of movement of said engine piston means.

12. An apparatus as set forth in claim 11, further comprising: a plurality of injection nozzles included in said fuel injection nozzle means each being individually associated with a separate working chamber of said internal combustion engine means; means providing through said passage means a plurality of sEparate fuel paths, each leading individually to one of said injection nozzles; means operable during said relatively lower engine speed for any given load condition, to divert said fuel from a portion of said passage means which is in common communication with said plurality of separate fuel paths; and means for effecting said displacement of said relatively larger volume fuel increment during each working stroke of engine piston means individually associated with each of said separate working chambers of said internal combustion engine means.

13. An apparatus as described in claim 11 further comprising: orifice means included in said fuel injection nozzle means; means operable during said relatively lower engine speed for any given load condition, to partially obstruct said orifice means of said fuel injection nozzle means and produce a generally radial flow pattern of fuel leading to said orifice means, and produce a generally diverging spray of fuel leading from said orifice means; and means operable during said relatively higher engine speed for any given load condition to provide a generally axial flow of fuel leading to said orifice means, and form a generally solid configuration of fuel streams leaving said orifice means and comprising said fuel stream received by said agitation zones and burning loci associated therewith.

14. An apparatus as described in claim 11, further comprising: flow path means in said engine means provided by said spaced wall means which comprise said agitation zones and define the location of said burning loci; means operable during at least a portion of said working stroke of said engine piston means, to generally enlarge the flow capacity of said flow path means; means operable to progressively increase a mass flow rate of combustion supporting gas transmitted to said burning loci and passing into said flow path means during said working stroke of said engine piston means as said flow path means generally enlarge their flow capacity; and means operable at least during said working stroke of said piston means, to progressively increase the mass flow rate of combustible fuel transmitted to said burning loci, with said progressive increase in the mass flow rate of fuel continuing for at least a majority of the time during which said fuel streams are received by said agitation zones and burning loci associated therewith.

15. Apparatus as set forth in claim 11, further comprising: means for effecting operation of a plurality of working chambers of said internal combustion engine and including a plurality of injection nozzles included in said fuel injection nozzle means, each being individually associated with a separate working chamber of said internal combustion engine means, means providing through said passage means a plurality of separate fuel paths, each leading individually to one of said injection nozzles, means operable during said relatively lower engine speed for any given load condition to divert said fuel from a portion of said passage means which is in common communication with said plurality of separate fuel paths, and means for effecting said displacement of said relatively larger volume fuel increment during each working stroke of engine piston means individually associated with each of said separate working chambers of said internal combustion engine means; means for modifying the spray characteristics of said fuel injection nozzle means and including flow path means in said engine means provided by said spaced wall means which comprise said agitation zones and define the location of said burning loci, means operable during at least a portion of said working stroke of said engine piston means, to generally enlarge the flow capacity of said flow path means, means operable to progressively increase a mass flow rate of combustion supporting gas transmitted to said burning loci and passing into said flow path means during said working stroke of said engine piston means as said flow path means generally enlarge their flow capacity, and means operable at least during said working stroke of said piston means, to progressively increase the mass flow rate of combustible fuel transmitted to said burning loci, with said progressive increase in the mass flow rate of fuel continuing for at least a majority of the time during which said fuel streams are received by said agitation zones and burning loci associated therewith.

16. An apparatus for modifying injection characteristics of fuel injection nozzle means, said apparatus comprising: fuel pump means; fuel pump piston means operable to displace an increment of fuel from said fuel pump means; fuel injection nozzle means operable to generate said fuel streams; passage means for transmitting said displaced increment of fuel from said fuel pump piston means to said fuel injection nozzle means, with said fuel injection nozzle means being operable to pass fuel into the interior of internal combustion engine means; means for discharging fuel from said nozzle means into the interior of said internal combustion engine means at a rate different from, and slower than, the rate of displacement of said fuel increment from said fuel pump means into said passage means; means operable at a relatively lower engine speed for any given load condition of said internal combustion engine means to displace a relatively larger volume fuel increment per working stroke of said engine means from said fuel pump means into said passage means, and divert fuel delivered by the fuel pump means into said passage means, between said fuel pump piston means and said injection nozzle means, from said passage means; and means operable, at a relatively higher speed for any given load condition of said internal combustion engine means, to displace a relatively smaller volume fuel increment per working stroke of said engine means from said fuel pump means into said passage means, and at least reduce the degree of said diversion of fuel from said passage means, and said means to displace and divert being operable to substantially avoid an undesirable mismatching of the time duration of discharge of said fuel streams into said agitation zones, in relation to a desired increment of movement of said engine piston means.

17. An apparatus for modifying the injection characteristics of fuel injection nozzle means as set forth in claim 16, further comprising: a plurality of injection nozzles included in said fuel injection nozzle means, each being individually associated with a separate working chamber of said internal combustion engine means; means providing through said passage means a plurality of separate fuel paths, each leading individually to one of said injection nozzles; means operable during said relatively lower engine speed for any given load condition, to divert said fuel from a portion of said passage means which is in common communication with said plurality of separate fuel paths; and means for effecting said displacement of said relatively larger volume fuel increment during each working stroke of engine piston means individually associated with each of said separate working chamber of said internal combustion engine means.

18. An apparatus for modifying the injection characteristics of fuel injection nozzle means, as set forth in claim 16, further comprising: orifice means included in said fuel injection nozzle means; means operable during said relatively lower engine speed for any given load condition, to partially obstruct orifice means of said fuel injection nozzle means and produce a generally radial flow pattern of fuel leading to said orifice means, and produce a generally diverging spray of fuel leading from said orifice means and passing into said interior of said internal combustion engine means; and means operable during said relatively hiGher engine speed for any given load engine condition to provide a generally axial flow of fuel leading to said orifice means, and form generally solid fuel stream means leaving said orifice means and passing into said interior of said internal combustion engine means.

19. An apparatus for modifying the injection characteristics of fuel injection nozzle means as set forth in claim 16, further comprising: flow path means in said engine means operable to define and at least partially confine, fuel and gas agitation zones; means operable during at least a portion of a working stroke of engine piston means of said engine means, to generally enlarge the flow capacity of said flow path means; means operable to progressively increase a mass flow rate of combustion supporting gas passing through said flow path means during said working stroke of said engine piston means as said flow path means generally enlarge their flow capacity; and means operable at least during said working stroke of said engine piston means, to progressively increase the mass flow rate of combustible fuel discharged from said injection nozzle means, and direct said fuel streams into said agitation zones.