WO2002088545A1 - Pompe monobloc a deux lumieres, injecteur, et procedes touchant au rendement d'un moteur - Google Patents

Pompe monobloc a deux lumieres, injecteur, et procedes touchant au rendement d'un moteur Download PDF

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Publication number
WO2002088545A1
WO2002088545A1 PCT/US2002/013205 US0213205W WO02088545A1 WO 2002088545 A1 WO2002088545 A1 WO 2002088545A1 US 0213205 W US0213205 W US 0213205W WO 02088545 A1 WO02088545 A1 WO 02088545A1
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WO
WIPO (PCT)
Prior art keywords
fuel
unit pump
bleed
port
injection
Prior art date
Application number
PCT/US2002/013205
Other languages
English (en)
Other versions
WO2002088545B1 (fr
Inventor
Kenneth H. Klopfer
Mark Duquette
Original Assignee
Stanadyne Corporation
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Stanadyne Corporation filed Critical Stanadyne Corporation
Priority to EP02723977A priority Critical patent/EP1390617A4/fr
Priority to US10/475,255 priority patent/US20040136850A1/en
Publication of WO2002088545A1 publication Critical patent/WO2002088545A1/fr
Publication of WO2002088545B1 publication Critical patent/WO2002088545B1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders

Definitions

  • the invention relates to fuel metering control in a unit pump or unit injector designed to inject fuel pulses of variable quantity into the cylinder of an internal combustion engine and, more particularly, to refinements of the inlet port that improve the shape and timing of the injected fuel pulses.
  • unit pumps and unit injectors for internal combustion engines have been simple, low cost fuel systems with few options and little flexibility. Controlling the quantity and timing of each injection pulse have been difficult to implement. As the need for higher engine efficiency and pollution abatement have increased, it has become increasingly evident that there is a need to control not only the quantity of fuel injected and the timing of injection but also the rate shape (quantity of fuel injected per unit of time over the course of an injection pulse) of each injection pulse.
  • the prior art discloses various methods for controlling the quantity of fuel injected by altering the exterior profile of a unit pump plunger.
  • Providing a circumferential surface of the pump plunger in the form of a circumferential helix permits adjustment of injection duration and timing by rotation of the pumping plunger relative to the fuel inlet port defined by the unit pump body (also known as the fill/spill port).
  • the helix has an upper profile, the axial position of which determines when the inlet port is completely covered and a lower profile, the axial position of which determines when the inlet port will be uncovered.
  • the plunger is typically rotated by means of a control arm connected to a control rack.
  • the circumferential helix closes a fuel inlet port to define a sealed pumping chamber for generating a pulse of high- pressure fuel.
  • pressure in the pumping chamber increases until the pressure is sufficient to hydraulically actuate (unseat) a needle valve in the injector, which permits pressurized fuel to be injected into the combustion chamber of an engine cylinder.
  • start of injection is determined by the accumulation of sufficient pressure in the unit pump to unseat the needle valve in the injector.
  • end of injection is determined by release of pressure in the pumping chamber caused by opening of the inlet port by the lower profile of the helix. Opening the inlet port relieves pressure in the pumping chamber by hydraulically connecting the pumping chamber to the inlet port. The pressure in the pumping chamber falls below a pressure that will allow closure of the needle valve, which consequently closes, ending the injection event.
  • the shape of the helix surrounding the pumping plunger determines injection duration and, by that, the quantity of fuel injected.
  • the axial position of the upper profile helps to determine SOI, with an upper profile extending in the direction of plunger movement advancing SOI.
  • Rotation of the pumping plunger within the bore varies the timing and duration of injection by bringing different portions of the helix into axial alignment with the inlet port as is known in the art.
  • unit pump efficiency is inversely related to engine speed above, for example, 1 000 rpm. In other words, peak-pumping efficiency occurs at approximately 1000 rpm and decreases for the remainder of the engine rpm range. This causes a phenomenon called "fuel backup" in which greater quantities of fuel are injected at lower rpm's during reduction of engine speed from, for example rated speed to peak torque. This fuel backup has an adverse effect on emissions.
  • fuel backup there is a need in the art for modifications to a unit pump, which flatten the fuel delivery curve over an extended rpm range.
  • pe ed advance Another phenomenon called “spe ed advance" is caused by hydraulic interaction between the unit pump and the needle valve of the associated unit injector.
  • the first hydraulic pressure wave generated by the unit pump is insufficient to open the needle valve of the unit injector. Instead, this first hydraulic pressure wave is reflected and reinforced by a second hydraulic pressure wave, which now has sufficient energy to open the needle valve in the unit injector.
  • higher plunger velocities produce a stronger pumping event and, as a result, the first pump-generated pressure wave has enough energy to open the needle valve of the injector.
  • a fuel injection pulse is related to emissions of certain pollutants such as oxides of Nitrogen (NOx) . It is known that a slower initial rate of injection reduces emissions of NOx. The most desirable shape for the end of an injection pulse is an abrupt shutoff. Thus, there is a need in the art for more precise control over the shape of each fuel injection pulse and, more particularly, to shape a fuel injection pulse that has a slower initial rate of injection and an abrupt cutoff at the end of the injection pulse.
  • NOx oxides of Nitrogen
  • dual ports at the fuel inlet of the pumping chamber bore wall are provided in conjunction with an otherwise substantially standard unit pump.
  • a relatively small bleed port is located in spaced relation to the larger, main inlet port, thereby providing increased flexibility for controlling speed advance, fuel backup rate, and injection rate shaping.
  • the bleed port is located axially spaced (in the direction of pumping plunger travel) from the much larger main inlet port, otherwise known as the inlet port.
  • the bleed port may also be radially or angularly offset relative to the inlet port to permit bleed port masking at predetermined angular orientations of the pumping plunger relative to the unit pump body.
  • the axial spacing of the bleed port relative to the inlet port determines the distance of axial pump plunger travel between closure of the inlet port (beginning of pumping) and closure of the bleed port (end of bleed) . Greater axial spacing increases the time period that the bleed port is open after closure of the inlet port. In general, the longer the bleed port is open, the greater its effect on the pressure pulse produced by the unit pump. Under some circumstances, such as during engine startup (cranking) it is desirable that the bleed port be covered throughout the pumping cycle. An angular offset between the bleed port and inlet port permits the unit pump plunger helix to have features which mask or cover the bleed port at certain rotational positions of the plunger relative to the unit pump body. When covered, the bleed port has no effect on unit pump function.
  • the bleed port provides an upward shift in the engine rpm at which the speed advance phenomenon occurs.
  • the bleed port accomplishes this by sapping energy from the first pressure wave generated by the unit pump.
  • the first pressure wave is unable to move the unit injector needle valve until a higher engine speed, as will be further discussed below.
  • the bleed port modifies the volumetric efficiency of the unit pump in such a manner as to flatten the fuel delivery curve (reduce fuel backup).
  • a flattened fuel delivery curve provides greater flexibility in fuel control as will be further discussed below.
  • the bleed port has a desirable effect on the rate shape of each injection pulse. By slowing or reducing the energy of the beginning of each pumping stroke, the bleed port desirably reduces the initial rate of injection of each injection pulse.
  • An object of the present invention is to provide a new and improved unit pump or unit injector that economically enhances control over fuel delivery through an injector.
  • Another object of the present invention is to provide a new and improved unit pump or unit injector that reduce emissions of nitrous oxide and smoke from internal combustion engines.
  • a further object of the present invention is to provide a new and improved unit pump or unit injector that reduce the effects of fuel backup on control of fuel delivery.
  • a yet further object of the present invention is to provide a new and improved unit pump or unit injector that permit control of the "speed advance" phenomenon.
  • Figure 1 is a sectional view through a unit pump incorporating dual ports in accordance with the present invention
  • Figure 1 A is a sectional view through a portion of an internal combustion engine equipped with an injector suitable for use in conjunction with the unit pump of Figure 1 ;
  • Figure 2 is an exterior side view of a unit pump body illustrating one example of a dual port in accordance with the present invention;
  • Figure 3 is a layout view illustrating features on the exterior surface of the pumping plunger which interact with the inlet and bleed ports, including representations of the inlet and bleed ports superimposed over the left-hand portion of the Figure;
  • Figure 4 is a graph comparing unit pump fuel delivery relative to engine rpm for a unit pump with no bleed port to a unit pump with a bleed port
  • Figure 5 is a graph comparing unit pump fuel delivery relative to engine speed for a unit pump with a .01 4" bleed port to a unit pump with a .01 8" bleed port;
  • Figure 6 is a graph comparing the SOI in engine degrees over a range of engine speeds (rpm) of a unit pump with a .01 4" bleed port to a unit pump with a .01 8" bleed port;
  • Figure 7 is a graph comparing fuel injection rate relative to unit pump pressure and a top dead center reference over time measured in degrees of engine rotation;
  • Figure 8 is a layout view of the exterior surface of a pumping plunger illustrating the helix and its upper and lower profiles with representations of the inlet and bleed ports superimposed on the helix at particular angular orientations of the pumping plunger relative to the unit pump body;
  • Figure 9 is a sectional view through a unit injector incorporating a dual port in accordance with the present invention.
  • FIG. 1 is a sectional view through a unit pump assembly 10 extending from a cam follower at the bottom of the Figure through a discharge fitting 62 at the top of the Figure.
  • a pumping plunger 1 3 is rotatably and reciprocably retained in a bore 66 in the unit pump body 60.
  • a control arm 1 7 is attached to the pumping plunger 1 3 such that manipulation of the control arm rotates the pumping plunger relative to the unit pump body 60.
  • the outside surface of the head end of the pumping plunger 1 3 is provided with a helix 1 6 whose function is to cover the inlet port (also referred to herein as the inlet port) 1 4 for a portion of each pumping stroke, thereby defining the duration of each pumping cycle.
  • the basic functioning of a unit pump of this type is known in the art and will be described herein only as it relates to the present invention.
  • Figure 1 A illustrates an injector 100 appropriate for use in conjunction with the unit pump 10 of Figure 1 .
  • the injector is operatively connected to a discharge fitting 62 such that high- pressure fuel produced by the unit pump acts to hydraulically open the injector needle valve 1 1 0 to produce an injection event.
  • An injection event is characterized by the emission of a metered quantity of fuel under high pressure from the fuel injector 100 into the combustion chamber 200 of an internal combustion engine.
  • FIG. 9 is a sectional view through a unit injector 1 0a incorporating a dual port 1 2, 14 in accordance with the present invention.
  • the unit injector 1 0a incorporates a unit pump and injector into a single assembly as is known in the art. Discussion of the functionality of the unit pump and dual ports 1 2, 14 are equally applicable to both the illustrated unit pump 1 0 and the unit injector 10a.
  • a unit pump in accordance with the present invention comprises a bleed port 1 2 spaced from the main inlet port 14.
  • the bleed port 1 2 is positioned to be covered by the helix 1 6 after the inlet port 1 4 has been covered, or after the beginning of a pumping cycle.
  • Figures 1 and 2 of the present application show the location of the bleed port 1 2 in conjunction with the inlet port 1 4 on the unit pump body 60.
  • the bleed port 1 2 and inlet port 1 4 are shown generally laterally of the helix 1 6 on the pumping plunger 1 3 in Figure 1 .
  • Figure 2 illustrates one example of the relative positioning and size of the bleed port 1 2 relative to the inlet port 14.
  • Design options for configuring the ports 1 2, 1 4 in accordance with the present invention include bleed port diameter 1 8, axial offset 20 taken with reference to the assembly axis A and angular offset 22 taken with reference to the position of the main inlet port 1 4.
  • Figure 3 is a layout view showing the relationship of the bleed port 1 2 in the pumping chamber wall 68 to the helix lower and upper profiles 70, 72 on the pumping plunger 1 3.
  • the right hand portion of Figure 3 illustrates 1 80° of the outside surface of the pumping plunger 1 3, clearly showing the upper and lower profiles 72, 70 of the helix 1 6.
  • the left hand portion of Figure 3 shows the bleed and inlet ports 1 2, 1 4 superimposed on the helix 1 6 to illustrate the relative positioning at various angular positions of the plunger 1 3 relative to the unit pump body.
  • the plunger 1 3 is rotated by manipulation of the control arm 1 7. Rotation of the plunger 1 3 changes the axial relationship of the ports 1 2, 1 4 relative to the upper and lower profiles 72, 70 of the helix 1 6.
  • the full fuel region 24, throttle progression region 26 and light load advance region 28 are indicated.
  • the bleed port will either be covered 30 (no leakage), transitioning 32 (with partial leakage) or totally uncovered 34 (full leakage) for returning fuel back into the entrance of the fuel inlet port 1 4.
  • the lines 36, 38 represent the inlet port 1 4 center line at SOI and EOl, respectively, with the crossover point 40 representing the condition wherein the light load advance is, e.g., 5° .
  • Figure 4 illustrates the so-called "fuel backup" phenomenon that is characteristic of most pumps of any type, and is of particular significance in the design and operation of fuel injection pumps for internal combustion engines in motor vehicles.
  • a unit pump of the type shown in Figures 1 and 2 may have operational characteristics such as those shown in Figure 4, with a rated speed 80 at about 2,800 rpm, where the volumetric injection quantity is 57 mm 3 per injection.
  • the fuel pressure decreases and the pump in effect becomes more efficient such that the injection quantity increases to, e.g., about 70 mm 3 per injection at 1 ,700 rpm, where peak engine torque 82 is produced.
  • Figure 4 illustrates how implementing the present invention (i.e., providing a bleed port) flattens the fuel backup curve.
  • Figure 5 graphically compares the performance of a 0.01 4"
  • FIG. 6 graphically compares SOI in engine degrees as dependent on engine speed, for two examples of bleed port implementation (0.014" bleed port and 0.01 8" bleed port).
  • the graph clearly shows an upward shift 50 in the engine speed at which speed advance occurs in the 0.018" curve.
  • the maximum advance 52 is also indicated for the 0.01 8" curve. From Figure 6 it can be seen that the size of the bleed port influences the engine speed at which speed advance occurs with speed advance occurring later with a larger bleed port.
  • the axial spacing 20 between the inlet port 1 4 and bleed port 1 2 also influences this effect on speed advance, with a greater axial distance 20 increasing the engine speed at which speed advance occurs. It can be seen from Figure 6 that SOI advances approximately 3° of engine rotation in the space of approximately 100 rpm due to the first wave-second wave phenomenon previously described. Manipulation of bleed port sectional flow area (diameter 1 8) and axial spacing 20 permits the engine designer to control where this speed advance occurs in the engine's working rpm range.
  • Figure 7 is a graphical comparison of the rate shape 44 of injection for an injection pulse produced by an injector operatively connected to the representative unit pump 1 0 in accordance with the present invention.
  • the rate shape of injection 44 is compared to a curve illustrating pump pressure and illustrated relative to a top dead center piston reference (TDC REF) in terms of time illustrated in degrees of engine rotation. Leakage through the bleed port at SOI softens the rise or initial rate of injection as illustrated at 42. The rapid decline in the rate of injection at 46 results from the use of a relatively large main inlet port 1 4.
  • the associated pressure pulse 48 produced by the unit pump is also illustrated.
  • the rate shape of injection 44 is improved by inclusion of a bleed port 1 2 in addition to the inlet port 14 in accordance with the present invention.
  • Figure 8 is a layout view of an alternative helix shape and bleed port angular offset 22 configuration.
  • the Figure illustrates the positions of the inlet and bleed ports 1 4, 1 2 relative to the helix upper and lower profiles 72, 70 at particular rotational positions for the plunger 1 3 relative to the unit pump body 60.
  • the bleed and inlet ports 1 2, 1 4 are illustrated for each rotational position, with the rotational positions indicated by a vertical line through the center of the inlet port 1 4.
  • Each vertical line through the center of the inlet port 14 is labeled with a number representing the rotational position of the pumping plunger corresponding to a control rack position stated in millimeters.
  • the helix 1 6 includes an extension 1 6a for masking a radially offset bleed port 1 2 at a plunger rotational position corresponding to a 21 mm control rack position.
  • the bleed port 1 2 has an angular offset 22 relative to the inlet port 14. This offset permits an extension 1 6a of helix 1 6 to be positioned over the bleed port 1 2 at a predetermined plunger rotational position (in this case a 21 mm control rack position) .
  • This angular orientation of pumping plunger 1 3 relative to the unit pump body 60 is utilized only during cranking for the purpose of aligning the helix extension 1 6a over the bleed port 1 2.
  • the diameter of the inlet port 1 4 would most likely fall within the range of about 0.075" (1 .905mm) to 0.1 50"(3.81 mm) and the associated bleed port diameter 1 8 would likely fall within the range of about 0.0075"(.1 905mm) and 0.020" (.508mm).
  • the cross-sectional flow area of the bleed port 1 2 would most likely fall within the range of about 1 - 8% of the cross sectional flow area of the inlet port at the wall 69 of the pumping bore 66.
  • the axial offset 20 would likely fall in the range of 0.05"(1 .27mm) to 0.20" (5.08mm) and the radial offset 22 would likely fall in the range of 0.01 "(.254mm) to 0.03"(.762mm) .
  • the radial offset could alternatively be expressed as an angular offset, which in the illustrated embodiment would likely fall in the range of 0 to 10° (degrees) . These values are representative, not limiting.
  • One implementing example has an inlet port diameter 1 5 of about 0.1 20" (3.04mm), a bleed port diameter 1 8 of about 0.01 6"(.4064mm) and an axial offset 20 of 0.1 0"(2.54mm) and a radial offset 22 of about 0.020"(.508mm).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention porte sur une pompe monobloc (10) dont la lumière de purge (12) est distante de la lumière principale d'alimentation (14). La lumière de purge (12), qui améliore la forme de la courbe de débit d'injection traversant un injecteur associé en ralentissant le débit initial d'injection, permet de déplacer le régime du moteur auquel se produit l'ouverture prématurée (speed advance) de l'injecteur, et aplatit en outre la courbe d'abaissement du débit (fuel backup) en fonction de la vitesse. En modifiant la section (18) du passage de la lumière de purge, l'espacement axial entre la lumière de purge et la lumière d'admission (20), on permet au concepteur de faire varier (ou même d'éliminer) l'impact de la lumière de purge (12) sur les performances de ladite pompe (10).
PCT/US2002/013205 2001-04-26 2002-04-26 Pompe monobloc a deux lumieres, injecteur, et procedes touchant au rendement d'un moteur WO2002088545A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP02723977A EP1390617A4 (fr) 2001-04-26 2002-04-26 Pompe monobloc a deux lumieres, injecteur, et procedes touchant au rendement d'un moteur
US10/475,255 US20040136850A1 (en) 2002-04-26 2002-04-26 Dual port unit pump injector, and engine efficiency methods

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US28645601P 2001-04-26 2001-04-26
US60/286,456 2001-04-26

Publications (2)

Publication Number Publication Date
WO2002088545A1 true WO2002088545A1 (fr) 2002-11-07
WO2002088545B1 WO2002088545B1 (fr) 2003-01-03

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PCT/US2002/013205 WO2002088545A1 (fr) 2001-04-26 2002-04-26 Pompe monobloc a deux lumieres, injecteur, et procedes touchant au rendement d'un moteur

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WO (1) WO2002088545A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2537344A1 (de) * 1975-08-21 1977-03-03 Ckd Praha Einspritzpumpe insbesondere fuer brennkraftmaschinen
US5056469A (en) * 1990-06-29 1991-10-15 Ail Corporation Fuel injection system
US6273066B1 (en) * 1999-05-12 2001-08-14 Daimlerchrysler Ag Fuel injection for an internal combustion engine
US6336444B1 (en) * 1999-05-28 2002-01-08 Mack Trucks, Inc. Diesel engine fuel injection system
US6386185B1 (en) * 1999-09-28 2002-05-14 Delphi Technologies, Inc. Valve arrangement

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB926214A (en) * 1960-03-03 1963-05-15 Ingersoll Rand Co Improvements in infinite step controlling device for compressors
GB1292628A (en) * 1968-12-23 1972-10-11 Borg Warner Fuel injection system

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2537344A1 (de) * 1975-08-21 1977-03-03 Ckd Praha Einspritzpumpe insbesondere fuer brennkraftmaschinen
US5056469A (en) * 1990-06-29 1991-10-15 Ail Corporation Fuel injection system
US6273066B1 (en) * 1999-05-12 2001-08-14 Daimlerchrysler Ag Fuel injection for an internal combustion engine
US6336444B1 (en) * 1999-05-28 2002-01-08 Mack Trucks, Inc. Diesel engine fuel injection system
US6386185B1 (en) * 1999-09-28 2002-05-14 Delphi Technologies, Inc. Valve arrangement

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP1390617A4 *

Also Published As

Publication number Publication date
EP1390617A1 (fr) 2004-02-25
EP1390617A4 (fr) 2005-06-01
WO2002088545B1 (fr) 2003-01-03

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