System and method of optimizing fuel injection timing in locomotive engine

Abstract

Systems and methods for reducing engine emissions in a locomotive are presented. In an embodiment, a fuel injector or a fuel injection pump of a fuel injection mechanism includes a plunger with an upper helix whose angle changes between points on the plunger that correspond to an idle throttle position and a full throttle position. As such, injection timing is optimized, and engine emissions are reduced.

Description

BACKGROUND

1. Field

Embodiments of the present invention relate to systems and methods for reducing engine emissions in a diesel engine, such as a locomotive diesel engine.

2. Description of Related Art

Locomotive manufacturers and remanufacturers supply locomotive diesel engines to the rail transportation industry, which includes establishments furnishing transportation by line-haul railroad, as well as switching and terminal establishments. In recent years, Environmental Protection Agency (EPA) emissions standards for locomotive diesel engines have become increasingly demanding. In particular, standards enacted under the Federal Clean Air Act of 1998 require significant reductions of individual emission compounds, including oxides of nitrogen (NO x ). NO x gases, which include the compounds nitrogen oxide (NO) and nitrogen dioxide (NO 2 ), are a major component of smog and acid rain.

Exhaust from a locomotive diesel engine includes various gaseous constituents, such as NO x , carbon monoxide (CO), carbon dioxide (CO 2 ), and hydrocarbons (HC), as well as particulate matter. Severe environmental and economic consequences may ensue if locomotive engine emissions do not comply with applicable EPA standards.

U.S. Pat. No. 6,470,844 to Biess et al. discloses a system and method that automatically shuts down a primary engine of a locomotive after the primary engine has been idling for a predetermined period of time. A small secondary engine is started to perform useful functions on behalf of the shut-down primary engine. Because it reduces locomotive idle time, this approach reduces engine emissions. However, engine emissions remain a cause for concern when the primary engine is running.

Therefore, what is needed is a system and method for reducing engine emissions in a locomotive.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a partially broken away cross-sectional view of a fuel injector according to an embodiment of the present invention.

FIGS. 2A , 2 B, and 2 C illustrate a fuel injector plunger in various exemplary degrees of rotation according to an embodiment of the present invention.

FIGS. 3A , 3 B, and 3 C illustrate exemplary planar views of an axial portion of a plunger according to embodiments of the present invention.

FIG. 4 illustrates a selected portion of a plunger according to an embodiment of the present invention.

FIG. 5 illustrates a selected portion of a plunger according to an embodiment of the present invention.

FIGS. 6A and 6B illustrate exemplary plungers according to embodiments of the present invention.

FIG. 7 illustrates a process according to an embodiment of the present invention.

DETAILED DESCRIPTION

Systems and methods for an engine, such as a diesel engine in a locomotive, are presented. In various embodiments, a fuel injection mechanism includes a fuel injector (unit injector) or fuel injection pump. The fuel injector or fuel injection pump includes a plunger with an upper helix whose angle changes between points on the plunger that correspond to an idle throttle position and a full throttle position. As such, injection timing is optimized, and engine emissions are reduced.

In other embodiments, the fuel injection mechanism employs a nozzle tip formed of a chromium hot-work steel. Accordingly, reductions in engine emissions may be sustained over long periods of time.

FIG. 1 is a partially broken away cross-sectional view of a fuel injector 100 according to an embodiment of the present invention. In various embodiments, injector 100 may be a unit injector for a fuel system of an engine, such as a diesel engine manufactured by GM EMD (General Motors Electro-motive Division). EMD-type engines employ mechanical control of injection timing and may be implemented effectively in various settings, such as, for example, locomotive (line-haul, switcher, passenger, or road), marine propulsion, offshore- and land-based oil well drilling rigs, stationary electric power generation, nuclear power generating plants, and pipeline and dredge pump applications. In one embodiment, injector 100 is implemented in an EMD 567, 645, or 710 series engine.

For exemplary purposes, drawings herein depict a unit injector and associated plungers for EMD-type engines. However, it is to be understood that teachings herein may be similarly applied to engines that employ fuel injection pumps, such as diesel engines manufactured by GE Transportation Systems, including the GE 7FDL and 7HDL engines, and diesel engines manufactured by ALCO. In such engines, each fuel injection pump includes a plunger that supplies fuel to an injector via a high pressure fuel line. Helices of such plungers may be modified consistent with principles presented herein. A nozzle tip as described herein also may be utilized.

Fuel injector 100 includes a body 150 , a plunger 110 , a housing nut 115 , a bushing 120 , a nozzle tip 130 , and spray holes 140 . Other components of injector 100 are not shown in FIG. 1 and are known in the art. Injector 100 is located and seated in a hole of a cylinder head of an engine fuel system.

In an embodiment, nozzle tip 130 of injector 100 may be formed of a chromium hot-work steel. The steel may be substantially through-hardened, and may conform, for example, to the H11 specification of the American Iron and Steel Institute (AISI) or the T20811 specification of the Unified Numbering System (UNS). As such, nozzle tip 130 may create effective atomization for longer periods of time, without deterioration of spray holes 140 . Accordingly, injector 100 may have an extended life of use in an injection system.

Plunger 110 slidably fits within bushing 120 . Bushing 120 includes an upper port 160 and a lower port 170 . Upper port 160 and lower port 170 are pathways for fuel. The amount of fuel injected into a cylinder depends on the extent to which the ports are closed, as described below.

The specific form of plunger 110 , including diameter, roundness, and straightness thereof, may vary depending on the implementation. Diameters of plungers may vary depending on the amount of fuel that is needed for injection. In an exemplary implementation, plunger 110 may have a diameter of between about 8 and 22 mm. Materials for plunger 110 may be chosen to prevent plunger 110 from substantially wearing down over time, and thus to prevent performance of plunger 110 from being degraded. Plunger 110 may be formed, for example, of bearing quality or high alloy steel, such as a chromium/nickel alloy. For example, the steel may conform to the 51501 or 52100 specifications of the Society of Automotive Engineers (SAE). Use of appropriate metals may ensure that helices described below maintain their shape for longer periods of time.

Plunger 110 includes an upper helix 180 and a lower helix 190 . Upper helix 180 and lower helix 190 determine the opening and closing of upper port 160 and lower port 170 of bushing 120 . Upper helix 180 determines when injection starts, and lower helix 190 determines when injection ends. As such, the helices determine the volume of fuel that is injected.

Upper helix 180 and lower helix 190 include ridges that define a shallow fuel channel 195 encircling an axial portion of plunger 110 . Upper helix 180 and lower helix 190 may be formed in various ways. In some embodiments, upper helix 180 and/or lower helix 190 are formed as a part of a machining operation that produces plunger 110 . In other embodiments, an existing plunger is modified by a selective machining operation to produce upper helix 180 and/or lower helix 190 .

In particular, upper helix 180 includes a ridge portion that slopes from a first point on the plunger surface towards a second point on the plunger surface. Sloping may involve one or more instances of ascending, descending, or neither ascending nor descending, between the first and second points. In some embodiments, the first point may be associated with an idle throttle position of injector 100 , and the second point may be associated with a full throttle position of injector 100 . Changes in slope of the ridge portion imply that the ridge portion may include multiple segments of predetermined length and/or height. In some embodiments, changes in slope may occur gradually such that one or more portions of the ridge portion are curved in perspective; for such embodiments, segments of the ridge portion may be extremely short. In other embodiments, changes in slope may be abrupt such that the ridge portion appears to have one or more clearly distinct portions.

Plunger 110 may be given a constant stroke reciprocating motion by an injector cam acting through a rocker arm and plunger follower (not shown). Timing of the injection period during the plunger stroke may be set by an adjusting screw at the end of the rocker arm.

Plunger 110 may be rotated via a rack and gear (not shown), as known in the art. Rotation of plunger 110 regulates the time that upper port 160 and lower port 170 may open and close during the downward stroke, thus determining the quantity of fuel injected into the cylinder. As plunger 110 is rotated from idle throttle position to full throttle position, the pumping part of the stroke is lengthened, injection is started earlier, and more fuel is injected.

Proper atomization of fuel is accomplished by the high pressure created during the downward stroke of plunger 110 , which forces fuel past a needle valve (not shown), causing the needle valve to lift, thus forcing fuel out through spray holes 140 in nozzle tip 130 of injector 100 .

A “helix angle” of a helix is the angle between a tangent to the helix and a line perpendicular to the internal axis of the helix and intersecting the tangent point. Changes in helix angle generally correspond to changes in the observed slope of a helix of a plunger. That is, when the helix angle changes, one may observe a change in slope (also called “lead”) of the helix. For embodiments herein, for ease of explanation, a plunger is described as having one helix with multiple helix angles (i.e., multiple slopes or leads). However, it is to be understood that the upper helix of a plunger herein actually has one or more portions of respective helices that have associated helix angles.

According to various embodiments of the present invention, plunger 110 has an upper helix whose helix angle changes at least once from a first point on plunger 110 which corresponds to an idle throttle position to a second point on plunger 110 which correspond to a full throttle position. As such, injection timing of injector 100 may be optimized as plunger 110 is rotated within bushing 120 .

In some embodiments, the helix angle changes such as to advance injection timing. Alternatively or additionally, the helix angle changes such as to retard, or neither advance nor retard, injection timing. By optimizing injection timing, emissions and combustion efficiency may be improved for an engine.

In an EMD-type unit injector, degrees of rotation of plunger 110 within bushing 120 may be associated which predetermined discrete throttle positions. Table 1 lists exemplary association that may be implemented in a diesel-electric locomotive. Plunger 110 in Table 1 may have a diameter ranging from about 0.420 to 0.422 inches, for example.

TABLE 1
Degrees of Rotation and Throttle Positions
Degree of Rotation of
Plunger 110 Throttle Position
0°          Idle
25°         Notch 1
50°         Notch 2
75°         Notch 3
100°        Notch 4
125°        Notch 5
150°        Notch 6
175°        Notch 7
200°        Notch 8

As Table 1 illustrates, adjacent throttle positions are uniformly separated by 25°. For instance, when a locomotive engineer moves a throttle selector from notch 4 to notch 5 , the plunger 110 is rotated 25° within bushing 120 . Similarly, when the throttle selector is moved from notch 5 to notch 6 , plunger 110 is rotated another 25°.

It is to be appreciated that Table 1 represents an exemplary division into discrete throttle positions, and that 25° is an exemplary division. In other engine implementations, there may be more or fewer discrete throttle positions, and/or the divisions between discrete throttle positions need not be uniform. Moreover, in some embodiments, such as, for example, marine and stationary power embodiments, there may not be discrete throttle positions. For example, the operating of a lever may gradually and continuously increase or decrease the throttle, i.e., rotate a plunger within a bushing.

According to some embodiments of the present invention, helix angles on a plunger, and point(s) on the plunger at which transitions in helix angle occur are selected based on emissions data and/or empirical engine performance testing. For example, weighted emissions duty cycles or other relevant data may be studied. If, for example, it is demonstrated that emission levels are problematic for an engine running in idle, notch 1 , and notch 2 , then the upper helix of a plunger may have different helix angles at points on the plunger, such as points corresponding to those throttle settings, in order to retard or advance injection timing. The form of lower helix 190 also may be varied, which may impact upon the injection process.

Moreover, the effects of varying helix angles, which may be engine- and implementation-specific, may be studied to determine optimal helix angles and transition points on a plunger for throttle settings ranging from full to idle. Exemplary criteria for evaluating implementations may include emissions levels and combustion efficiency. In various embodiments, helix angles and transition points may be chosen to ensure compliance with regulatory emissions limits, while minimizing fuel penalties associated with compliance.

FIGS. 2A , 2 B, and 2 C illustrate plunger 110 in various degrees of rotation according to an embodiment of the present invention. Upper helix 180 generally slopes from a point 210 corresponding to an idle throttle position ( FIG. 2A ) to a point 240 corresponding to a notch 8 throttle position (FIG. 2 C).

More particularly, FIG. 2A shows that upper helix 180 generally slopes downward from point 210 . FIG. 2B shows a change in slope (helix angle) of upper helix 180 at a point 220 corresponding to a notch 5 throttle position, and another change in slope (helix angle) at a point 230 corresponding to a notch 6 throttle position. Finally, FIG. 2C shows upper helix 180 slope to a point 240 corresponding to a notch 8 throttle position.

It is to be appreciated that FIGS. 2A , 2 B, and 2 C are merely illustrative of an exemplary plunger 110 according to an embodiment of the present invention. The precise form of upper helix 180 , including the number of transitions in slope (helix angle), and the points on plunger 110 at which transitions occur, as well as the angular measurements of each helix angle, may vary depending on the implementation.

FIGS. 3A , 3 B, and 3 C illustrate planar views of an axial portion of plunger 110 between lines B and B′ of FIG. 2A according to embodiments of the present invention. Upper and lower helices are shown in each figure. Parallel lines identify points along the upper helix that correspond to particular throttle settings.

FIG. 3A shows a reference upper helix 310 and a reference lower helix 320 . Reference upper helix 310 has a helix angle that does not substantially change from idle (0°) to notch 8 (200°). As seen in FIG. 3A , the slope of reference upper helix 310 is substantially constant from idle to notch 8 .

FIG. 3B shows an exemplary upper helix 330 and lower helix 340 according to an embodiment of the present invention. For purposes of comparison, reference upper helix 310 and reference lower helix 320 of FIG. 3A are shown in dashed lines in FIG. 3 B. Portions of upper helix 330 that coincide with reference upper helix 310 are indicated with x's. Coinciding portions of lower helix 340 and reference lower helix 320 are similarly indicated.

Upper helix 330 has associated helix angles that change from idle to notch 8 . Specifically, from idle to notch 6 , upper helix 330 has an associated slope (helix angle). From notch 6 to notch 8 , upper helix 330 has a different slope (helix angle).

More particularly, from idle to notch 6 , the helix angle of upper helix 330 is greater than that of reference upper helix 310 . That is, between the parallel lines corresponding to idle and notch 6 in FIG. 3B , the slope of upper helix 330 (with respect to a line perpendicular to the internal axis of the helix) is greater than the slope of reference upper helix 310 . At idle, upper helix 330 is displaced towards a top of plunger 110 (away from reference lower helix 320 ) as compared with reference upper helix 310 . From notches 6 to 8 , the helix angle of upper helix 330 is substantially the same as that of reference upper helix 310 . That is, between the parallel lines corresponding to notch 6 and notch 8 , the slope of upper helix 330 and that of reference upper helix 310 are substantially the same, and the respective helices are coincident.

Accordingly, the exemplary design of upper helix 330 of FIG. 3B retards injection timing for idle to notch 6 relative to a design incorporating reference upper helix 310 . Such retarding may improve emissions for an engine whose fuel injection system includes plunger 110 .

FIG. 3C shows an exemplary upper helix 350 and lower helix 360 according to an embodiment of the present invention. For purposes of comparison, reference upper helix 310 and reference lower helix 320 of FIG. 3A are shown in dashed lines in FIG. 3 C. Portions of upper helix 350 that coincide with reference upper helix 310 are indicated with x's. Coinciding portions of lower helix 360 and reference lower helix 320 are similarly indicated.

Upper helix 350 has associated helix angles that change from idle to notch 8 . Specifically, from idle to notch 5 , upper helix 350 has an associated slope (helix angle). From notch 5 to notch 7 , upper helix 350 has a different slope (helix angle). From notch 7 to notch 8 , upper helix 350 has yet a different slope (helix angle).

More particularly, from idle to notch 5 , upper helix 350 is displaced towards a top of plunger 110 (away from reference lower helix 320 ) as compared with reference upper helix 310 . Between the parallel lines corresponding to idle and notch 5 in FIG. 3C , the slope of upper helix 350 is substantially the same as the slope of reference upper helix 310 . From notches 5 to 7 , the helix angle of upper helix 330 is greater than that of reference upper helix 310 . That is, between the parallel lines corresponding to notch 5 and notch 7 , the slope of upper helix 350 is greater than that of reference upper helix 310 .

From notches 7 to 8 , the helix angle of upper helix 330 is substantially the same as that of reference upper helix 310 . That is, between the parallel lines corresponding to notch 7 and notch 8 , the slope of upper helix 350 and that of reference upper helix 310 are substantially the same, and the respective helices are coincident.

Accordingly, the exemplary design of upper helix 350 of FIG. 3C retards injection timing for idle to notch 7 relative to a design incorporating reference upper helix 310 . Such retarding may improve emissions for an engine whose fuel injection system includes plunger 110 .

FIG. 4 illustrates a selected portion of plunger 110 according to another embodiment of the present invention. The portion shown corresponds to portion A identified in FIG. 1 . Upper helix 480 is generally shown in FIG. 4 . Parallel lines identify points along upper helix 480 that correspond to particular throttle settings. Although only portions of upper helix 480 corresponding to idle, notch 1 , notch 2 , and notch 3 throttle settings are shown, teachings herein may be applied for other throttle settings.

A reference helix 401 is shown for purposes of comparison. Reference helix 401 has an associated helix angle (slope) that does not change between an idle and notch 3 throttle setting.

Exemplary helices 420 and 410 are also shown in FIG. 4 . Helix 420 has a helix angle less than that of reference helix 401 . As such, helix 420 may retard injection timing for idle, notch 1 , notch 2 , and notch 3 settings as compared to a plunger that includes reference helix 401 . Alternatively, helix 410 has a helix angle greater than that of reference helix 401 . As such, helix 410 may advance injection timing for idle, notch 1 , notch 2 , and notch 3 settings as compared to a plunger that includes reference helix 401 .

FIG. 5 illustrates a selected portion of plunger 110 according to another embodiment of the present invention. The portion shown corresponds to portion A identified in FIG. 1 . Upper helix 580 is shown in FIG. 5 . Parallel lines identify points along upper helix 580 that correspond to particular throttle settings. Although only portions of upper helix 580 corresponding to idle, notch 1 , notch 2 , and notch 3 throttle settings are shown, teachings herein may be applied for other throttle settings.

Upper helix 580 has three associated helix angles (slopes) between idle and notch 3 settings. In particular, upper helix 580 has a first helix angle (slope) between the idle and notch 1 positions. At notch 1 , the helix angle increases—the illustrated slope becomes steeper—and injection timing is thus advanced. At notch 2 , the helix angle decreases—the illustrated slope becomes less steep—and injection timing is thus retarded. At notch 3 , the helix angle conforms to a helix angle of a reference helix (not shown), and timing is neither advanced nor retarded relative to the reference helix.

In various engines, helix timing changes may be complementary to flywheel timing changes. Accordingly, in some embodiments, both the design of an upper helix and flywheel timing adjustments may be employed to optimize injection timing. In an exemplary embodiment, helix angles for upper helix 580 of FIG. 5 may be chosen such that, exclusive of flywheel timing adjustments, injection timing is altered by about −2° relative to a reference helix (not shown) at notch 1 ; +2° at notch 2 ; and 0° at notch 3 . Further optimization of injection timing may be achieved by adjusting flywheel timing.

In an embodiment similar to FIG. 3B above, upper helix 330 may be modified such that, (1) from idle to notch 5 , the helix angle of upper helix 330 is greater than that of reference upper helix 310 , and at idle, upper helix 330 is displaced towards a top of plunger 110 ; and (2) from notches 5 to 8 , the helix angle of upper helix 330 is substantially the same as that of reference upper helix 310 , and those helices are coincident. Exemplary injection timing for such a modified injector is shown in Table 2. For purposes of comparison, timing values for an injector with reference upper helix 310 are also shown.

TABLE 2
Exemplary Injection Timings
		Injection
		Timing of
		Reference	Injection
		Injector	Timing of
		with	Injector with
		Reference	Upper Helix
	Throttle	Upper Helix	330 (as
	Position	310	modified)	Difference
	Notch 8	19° BTDC	19° BTDC	0°
		(Before Top
		Dead
		Center)
	Notch 7	17° BTDC	17° BTDC	0°
	Notch 6	15° BTDC	15° BTDC	0°
	Notch 5	14° BTDC	13° BTDC	−1°
	Notch 4	13° BTDC	11° BTDC	−2°
	Notch 3	9° BTDC	6.5° BTDC	−2.5°
	Notch 2	7° BTDC	4.5° BTDC	−2.5°
	Notch 1	5° BTDC	1.5° BTDC	−3.5°
	Idle	4° BTDC	0.5° ATDC	−4.5°
			(After Top
			Dead Center)

FIG. 6A illustrates a plunger 110 with an upper helix 610 according to an embodiment of the present invention. Upper helix 610 may optimize injection timing for an engine that includes plunger 110 . As shown, upper helix 610 somewhat resembles a staircase. The specific form of upper helix 610 may depend on emissions data and/or empirical engine performance testing, as described above. In some embodiments, transitions in steps may be related to transitions in discrete throttle settings. For instance, for certain embodiments, the width of certain steps may span about 25° of the circumference of plunger 110 . Height of the various steps may vary.

In other embodiments, it may be desirable to optimize injection timing at higher throttle settings. For example, in a line-haul locomotive, which travels at high speeds much of the time, much of the EPA weighted emissions duty cycle is associated with high notches. Accordingly, for engines in such locomotives and engines in other analogous contexts, the upper helix of a plunger may be modified, for example, such that injection timing is optimized for high notches. FIG. 6B illustrates an exemplary embodiment of a plunger 110 that includes an upper helix 650 and a reference helix 670 . Upper helix 650 may reduce emissions for higher notches as compared with reference helix 670 . In another exemplary embodiment (not shown), the helix angle of an upper helix may not substantially change or may change only slightly (resembling a straight line, for example) at lower notches, and then may change more substantially at higher notches to optimize injection timing at those notches.

FIG. 7 illustrates a manufacturing process 700 according to an embodiment of the present invention. In task 701 , an engine throttle setting in need of optimized injection timing is identified. In task 710 , a helix angle capable of optimizing injection timing for the identified engine throttle setting is determined. The determined helix angle may advance, retard, or not alter injection timing. In task 720 , a plunger for a fuel injector is formed. An upper helix of the plunger may include at least two segmented portions between points on the plunger respectively corresponding to a first and second throttle position. The segmented portions have unequal associated helix angles. One of the segmented portions may correspond to the throttle setting identified in task 701 and may have an associated helix angle substantially equal to the helix angle determined in task 710 . In task 730 , a fuel injector that includes the plunger is assembled. The fuel injector may include a through-hardened chromium hot-work steel nozzle tip such as that described above.

In some embodiments, a machining device, such as a programmable device, may be employed to manufacture the plunger. For instance, a plunger with an upper helix having multiple unequal helix angles may be formed from scratch. Alternatively, an existing plunger, such as a plunger whose upper helix has substantially one helix angle, may be modified, such that the modified plunger has an upper helix having multiple unequal helix angles at desired positions of the plunger.

The foregoing description of embodiments is provided to enable any person skilled in the art to make or use embodiments of the present invention. Various modifications to these embodiments are possible, and the generic principles presented herein may be applied to other embodiments as well. For instance, embodiments herein may be applied in conjunction with other apparatus and methods, such as other technologies for reducing engine emissions and/or improving engine performance.

It is to be appreciated that the specific form of the upper and lower helices of a plunger may be varied in any of a multitude of ways consistent with the teachings of the present application. Helix angles may be varied to achieve desired performance criteria for particular implementations.

As such, the present invention is not intended to be limited to the embodiments shown above but rather is to be accorded the widest scope consistent with the principles and novel features disclosed in any fashion herein.

Claims

1. An injection mechanism adapted for use in a particular type of engine, comprising:a plunger having an upper helix ridge and a lower helix ridge, the helix ridges defining a channel encircling an axial portion of the plunger, the helix ridges determining opening and closing of fuel ports of the injection mechanism, the upper helix ridge having a ridge portion sloping from a first point on the plunger surface towards a second point on the plunger surface, the first point being associated with an idle throttle position of an injection mechanism, the second point being associated with a full throttle position of the injection mechanism, wherein the ridge portion includes at least two segmented portions between the first and second points, the at least two segmented portions having unequal associated helix angles, said helix angles being angled based on emissions data derived from said type of engine.

2. The injection mechanism of claim 1, wherein:a first segmented portion among the at least two segmented portions retards injection timing for at least one predetermined throttle position of the injection mechanism relative to a reference injection mechanism, the reference injection mechanism including a plunger having an upper helix ridge with a ridge portion having substantially one associated helix angle between idle throttle and full throttle positions of the reference injection mechanism.

3. The injection mechanism of claim 2, wherein a second segmented portion among the at least two segmented portions neither advances nor retards timing for a second predetermined throttle position of the injection mechanism relative to the reference injection mechanism.

4. The injection mechanism of claim 1, wherein:a first segmented portion among the at least two segmented portions advances injection timing for at least one predetermined throttle position of the injection mechanism relative to a reference injection mechanism, the reference injection mechanism including a plunger having an upper helix ridge with a ridge portion having substantially one associated helix angle between idle throttle and full throttle positions of the reference injection mechanism.

5. The injection mechanism of claim 4, wherein a second segmented portion among the at least two segmented portions retards timing for a second predetermined throttle position of the injection mechanism relative to the reference injection mechanism.

6. The injection mechanism of claim 1, wherein the ridge portion includes at least three segmented portions between the first and second points, the at least three segmented portions having unequal associated helix angles.

7. The injection mechanism of claim 1, wherein the engine is a diesel engine.

8. The injection mechanism of claim 7, wherein the engine is mounted in a locomotive.

9. The injection mechanism of claim 1, further comprising a nozzle tip formed, at least in part, of a chromium hot-work steel.

10. The injection mechanism of claim 9, wherein the steel is substantially through hardened.

11. The injection mechanism of claim 10, wherein the steel conforms to the H11 specification of the American Iron and Steel Institute (AISI).

12. The injection mechanism of claim 1, wherein helix angles of the ridge portion do not substantially retard injection timing for a full throttle position of the injection mechanism relative to a reference injection mechanism, the reference injection mechanism including a plunger having an upper helix ridge with a ridge portion having substantially one associated helix angle between idle throttle and full throttle positions of the reference injection mechanism.

13. The injection mechanism of claim 1, wherein a helix angle of the ridge portion changes at a point on the plunger surface that substantially corresponds to a transition between a first throttle position and a second throttle position.

14. The injection mechanism of claim 1, wherein the injection mechanism is a fuel injector.

15. The injection mechanism of claim 1, wherein the injection mechanism includes a fuel injection pump, the plunger being positioned in the fuel injection pump.

16. A method comprising:identifying at least one engine throttle setting for which a reduced engine emission level is needed; determining a helix angle capable of optimizing injection timing for the at least one engine throttle setting; and forming a plunger for a fuel injection mechanism of the engine, the plunger having an upper helix ridge and a lower helix ridge, the upper helix ridge having a ridge portion sloping from a first point on the plunger surface towards a second point on the plunger surface, the first point being associated with an idle throttle position of an injection mechanism, the second point being associated with a full throttle position of the injection mechanism, wherein the ridge portion includes at least two segmented portions between the first and second points, the at least two segmented portions having unequal associated helix angles, and wherein a first segmented portion among the at least two segmented portions corresponds to the identified at least one throttle setting and has the determined helix angle.

17. The method of claim 16, wherein the determined helix angle retards injection timing for the at least one engine throttle setting.

18. The method of claim 16, wherein the determined helix angle advances injection timing for the at least one engine throttle setting.

19. The method of claim 16, wherein the forming includes machining at least a portion of the ridge portion to create the unequal associated helix angles.

20. The method of claim 19, wherein the forming includes programming a machining device to perform the machining.

21. The method of claim 19, wherein, prior to the machining, the ridge portion of the plunger has substantially one associated helix angle between the first and second points.

22. The method of claim 16, wherein the first segmented portion is associated with at least one predetermined throttle setting of the engine.

23. The method of claim 16, further comprising:forming a nozzle tip, at least in part, of a chromium hot-work steel.

24. The method of claim 23, wherein the steel is substantially through hardened.

25. The method of claim 24, wherein the steel conforms to the H11 specification of the American Iron and Steel Institute (AISI).

26. The method of claim 16, further comprising assembling the injection mechanism, the injection mechanism including the plunger.

27. The method of claim 16, wherein the ridge portion includes at least three segmented portions between the first and second points, the at least three segmented portions having unequal associated helix angles.

28. The method of claim 16, wherein the engine is a diesel engine.

29. The method of claim 28, wherein the engine is mounted in a locomotive.

30. The method of claim 16, wherein the injection mechanism is a fuel injector.

31. The method of claim 16, wherein the injection mechanism includes a fuel injection pump, the plunger being positioned in the fuel injection pump.

32. A diesel engine, comprising:a fuel system, the fuel system including a plurality of cylinders; a plurality of fuel injection mechanisms seated in respective cylinders, each injection mechanism including a body, a rotatable plunger slidably fitting within a bushing, and a nozzle tip, wherein the plunger has an upper helix ridge and a lower helix ridge, the helix ridges determining opening and closing of fuel ports of the injection mechanism, the upper helix ridge having a ridge portion sloping from a first point on the plunger surface towards a second point on the plunger surface, the first point being associated with a first throttle position, the second point being associated with a second throttle position, wherein the ridge portion includes at least two portions having unequal associated helix angles said helix angles being angled based on established emissions data; a rack and governor constructed and arranged to control rotation of the plunger; a fuel supply line to supply fuel to the injection mechanisms; and a fuel return line to return fuel to a fuel supply tank cooperating with the engine.

33. The diesel engine of claim 32, wherein the diesel engine is mounted in a locomotive.

34. The diesel engine of claim 32, wherein the injection mechanism is a fuel injector.

35. The diesel engine of claim 32, wherein the injection mechanism includes a fuel injection pump, the plunger being positioned in the fuel injection pump.

36. A method of manufacturing an emissions-efficient plunger for a fuel injection mechanism for a combustion engine, comprising:obtaining emissions data for said combustion engine at different throttle positions, said engine having different emissions at least at first and second throttle positions within said different throttle positions; determining a first helix angle for said plunger based on said emissions data for a first of said throttle positions, determining a second helix angle for said plunger based on said emissions data for a second of said throttle positions, said first helix angle being different from said second helix angle, and forming said plunger with a helix comprising at least a portion thereof with said first helix angle and a portion thereof with said second helix angle.

37. A method according to claim 36, further comprising:determining combustion efficiency at said different throttle positions; and utilizing said combustion efficiency in addition to said emissions data in determining said first helix angle and said second helix angle.

38. A method according to claim 37, wherein said throttle positions are discrete notch positions.

39. A method of manufacturing an emissions-efficient plunger for a fuel injection mechanism for a combustion engine, comprising:obtaining emissions data for said combustion engine at different throttle positions while using an injection mechanism with a reference plunger having a reference helix, said reference helix having a reference helix angle, said reference helix angle defining an injection timing; determining, based on said emissions data, emissions-efficient helix angles at least at a first and a second throttle position within said different throttle positions, said emissions-efficient helix angle at said first throttle position being different from said emissions-efficient helix angle at said second throttle position; and forming an emissions-efficient plunger that includes said different emissions-efficient helix angles.

40. A method according to claim 39, wherein said first throttle position is at a lower throttle position than said second throttle position, and wherein said forming comprises altering the emissions-efficient helix angle in comparison with said reference helix angle at said lower throttle position so that the injection timing is retarded in comparison with that for said reference helix.

41. A fuel injector for an engine fuel system, said engine fuel system having a plurality of throttle positions, said throttle positions having corresponding emissions characteristics, said fuel injector comprising:an injector body; a plunger within said body, said plunger having an upper helix ridge and a lower helix ridge, the helix ridges defining a channel and determining opening and closing of fuel ports of the injector, the upper helix ridge having a ridge portion extending from a first portion towards a second portion, the first portion being associated with an idle throttle position, the second portion being associated with a full throttle position, said ridge portion including at least two segmented portions between the first and second portions, the at least two segmented portions corresponding to associated throttle positions between said idle and full throttle positions, said at least two segmented portions having unequal associated helix angles, said unequal helix angles of the at least two segmented portions being angled in accordance with emissions characteristics of the engine at the associated throttle positions.