EP0683314B1 - Kraftstoffdruckerzeugende Kolbenanordnung für eine druckgezündete Brennkraftmaschine - Google Patents

Kraftstoffdruckerzeugende Kolbenanordnung für eine druckgezündete Brennkraftmaschine Download PDF

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Publication number
EP0683314B1
EP0683314B1 EP95107461A EP95107461A EP0683314B1 EP 0683314 B1 EP0683314 B1 EP 0683314B1 EP 95107461 A EP95107461 A EP 95107461A EP 95107461 A EP95107461 A EP 95107461A EP 0683314 B1 EP0683314 B1 EP 0683314B1
Authority
EP
European Patent Office
Prior art keywords
plunger
fuel
axial bore
injector
fuel injector
Prior art date
Legal status (The legal status 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 status listed.)
Expired - Lifetime
Application number
EP95107461A
Other languages
English (en)
French (fr)
Other versions
EP0683314A1 (de
Inventor
Dan K. Hickey
J. Victor Perr
David M. Rix
Joseph C. Bentz
Thomas M. Yonushonis
Malcolm G. Naylor
Katsuhiro Shinosawa
John C. Carroll Iii
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toshiba Corp
Cummins Inc
Original Assignee
Toshiba Corp
Cummins Engine Co Inc
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 Toshiba Corp, Cummins Engine Co Inc filed Critical Toshiba Corp
Publication of EP0683314A1 publication Critical patent/EP0683314A1/de
Application granted granted Critical
Publication of EP0683314B1 publication Critical patent/EP0683314B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/023—Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical
    • F02M57/024—Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical with hydraulic link for varying the piston stroke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/023—Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/445—Selection of particular materials

Definitions

  • the present invention is directed generally toward a fuel pressurizing plunger assembly for a compression ignition engine (Diesel engine) fuel injector operable with Diesel fuel that may contain abrading particles and lubricity lowering contaminants, and particularly to a fuel pressurizing plunger assembly with the features of the precharacterizing part of claim 1.
  • Diesel engine Diesel engine
  • Fuel injector plungers are required to operate under extremely adverse environmental conditions in a fuel injector assembly. With a mechanical drive train, heavy mechanical loads are applied to the plunger in both axial and tangential directions. The plunger must reciprocate within a bore in the injector body that is often distorted so the original diametral clearance is not maintained, and the plunger is forced against the bore wall during injector operation, resulting in scuffing. Additionally, low quality and contaminated fuels contribute to the creation of an adverse plunger operating environment.
  • the plunger material has been modified throughout the years in an effort to make a plunger that is both scuff-resistant and wear-resistant and capable of functioning as required under the adverse conditions of the fuel injector environment.
  • third body debris interferes with efficient injector function.
  • Third body debris includes particles harder than the plunger or injector body bore which are not intended to be present within the injector. These particles become embedded into the plunger surface and ultimately cause the plunger and body to be wedged together so that the plunger cannot reciprocate in the injector body bore and becomes friction welded.
  • the reduction of fuel lubricity which could be caused by water contamination of the fuel, and may be a characteristic of some alternative fuels, is also a factor contributing to the friction welding of the plunger and injector body together. Injector operation is, of course, prevented if this occurs.
  • the prior art plunger assembly defining the pre-characterizing part of claim 1 (JP - A - 60 104765) addresses those problems with a plunger assembly with a plunger formed of a scuff-resistant, wear-resistant ceramic material running in an axial bore of a body portion that is made of steel.
  • the abrasion resistance of ceramics is said to be an advantage in the particular surroundings.
  • a fuel pressurizing plunger assembly for a compression ignition engine (Diesel engine) fuel injector capable of operating efficiently in the presence of high axial and tangential loads on the plunger in view of fuel used that may contain abrading particles and lubricity lowering contaminants.
  • the plunger used is wear- and scuff-resistant and maintains an optimum diametral clearance so that it does not stick during fuel injector operation even under adverse engine operating conditions.
  • the injector plunger is formed from a ceramic material having a thermal expansion coefficient sufficiently correlated to the thermal expansion coefficient of the fuel injector body to provide optimum operating clearance between the plunger and injector body during engine operation while preventing fuel leakage around the plunger. Achieving the optimum fuel leakage around the plunger during engine operation is critical. Instead of ceramics with low thermal expansion which allow excessive leakage, high thermal expansion ceramics are capable of maintaining fuel leakage within acceptable parameters.
  • the plunger in the fuel pressurizing plunger assembly of the invention is a means for causing a controlled volume of fuel to be injected from the fuel injector. In this context it is influencing the timing of the fuel injection. Only in a preferred embodiment it is to be understood as a timing plunger in a more narrowsense, i. e. a separate intermediate plunger in a multiplunger-arrangement controlling a timing chamber.
  • the fuel injector assembly can well be a unit fuel injector as well as an in-line fuel injector.
  • Fuel injector plunger scuffing and sticking is one cause of high injector RPH (repairs per hundred). High warranty costs may result from the replacement of failed and inoperable plungers.
  • the fuel injector body plunger assembly of the present invention provides a reliable wear-resistant plunger that is free from sticking and scuffing, even when exposed to extremely abusive engine operating conditions. Consequently, the present invention effectively lowers both the injector RPH and warranty costs occasioned by failed and inoperable plungers.
  • Fig. 1 illustrates, in cross section, an open nozzle unit fuel injector 10 with a plunger 12.
  • This type of fuel injector includes a body 14 and an injector nozzle 16.
  • the injector nozzle 16 and the body 14 are axially aligned and held together by a retainer 18.
  • An axial bore 20 extends throughout the length of the body 14.
  • a plurality of spaced injection orifices 22 in the nozzle 16 is provided at the injector cup terminus to optimize fuel injection.
  • the injector 10 includes a plunger 12 that reciprocates axially within the injector along with a link 24 that is engaged by one end of a rocker lever 26.
  • the other end of the rocker lever 26 is drivingly connected to the camshaft 28 via a pushtube 30.
  • the rocker lever 26 typically applies both axial and tangential loads to the plunger 12 during engine operation.
  • Arrow (A) represents the axial load applied to the plunger 12 by the rocker lever 26.
  • Arrow (B) represents the tangential or side load applied to the plunger 12 by the rocker lever 26.
  • the axial load applied by the rocker lever 26 to the plunger 12 as it reciprocates in the injector body 14 can be elevated to as high as 10,67 kN (2400 pounds).
  • the ceramic plunger 12 is sized relative to the injector body bore 20 to provide a diametral clearance of 1,93 to 3,25 ⁇ m (76-128 millionths of an inch).
  • the diametral clearance can be less than that of known plunger designs due to differences in thermal expansion between the currently available stainless steel plunger and the ceramic plunger 12.
  • the aforementioned loads on the plunger 12 and the clamp load on the injector body 14 often distort the axial bore, which decreases the diametral clearance.
  • the rocker lever generated side load (arrow B) then forces the plunger 12 against the wall of the body bore 20. Plunger scuffing and wear occur under such circumstances.
  • the presence of the third body debris in the injector body bore compounds the plunger problems under these loads.
  • a ceramic plunger presents many advantages.
  • the kinds of ceramic materials evaluated for use as plungers are much harder than the materials currently used for either the plunger or the injector body.
  • the ceramic material has a low reactivity and a low affinity to weld with petroleum lubricated metal counterfaces.
  • the optimum surface finish must be created for the best sliding wear performance.
  • Plungers made from high thermal expansion ceramics including zirconia, alumina-zirconia and alumina have been demonstrated to show significantly better scuffing resistance than plungers made from metal.
  • other ceramics most notably silicon nitride, also display superior scuff resistance
  • high thermal expansion ceramics have been found to be suitable for use in forming unit fuel injector plungers.
  • the preferred ceramic materials for use in forming fuel injector plungers are those with a thermal expansion coefficient greater than 6 x 10 -6 /°C and a hardness greater than 800 kg/mm 2 .
  • the thermal expansion coefficient of the ceramic selected for the plunger should match as closely as possible that of the metal forming the injector body.
  • Fig. 2 compares the diameters of the injector body bore 20 (Fig. 1) with the diameters of a plunger currently in use and two ceramic plungers with differing diametral clearances.
  • Curve A represents the diameter of the injector body bore over the range of temperatures studied.
  • Curve B shows the changes in plunger diameter when the plunger 12 is formed from stainless steel. The diametral clearance between the stainless steel plunger and the injector bore in the assembly tested was 5,0 ⁇ m.
  • Curves C and D demonstrate diametral changes in plunger diameter for two ceramic plungers at different clearances. The diametral clearance between the plunger and the bore for the assembly represented by curve C was 2,5 ⁇ m, while the clearance at the curve D plunger assembly was 5,0 ⁇ m.
  • Fig. 2 clearly demonstrates that a ceramic plunger in accordance with the present invention can have a smaller diametral clearance in the injector bore than a stainless steel plunger and still function effectively in the presence of the loads applied to the plunger during engine

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (5)

  1. Kraftstoff unter Druck setzender Plungerkolbenaufbau für einen Kraftstoffinjektor (10) eines druckgezündeten Motors (Dieselmotors), wobei der Kraftstoffinjektor mit Dieselkraftstoff betreibbar ist, der abscheuernde Partikel und die Schmierfähigkeit senkende Verschmutzungen enthalten kann,
    wobei der Plungerkolbenaufbau aufweist
    eine axiale Bohrung (20), die innerhalb eines Körperabschnitts (14) des Kraftstoffinjektors (10) angeordnet ist, wobei die axiale Bohrung (20) eine innere Oberfläche des Körperabschnitts (14) mit einem vorbestimmten Bohrungsdurchmesser definiert, wobei der Körperabschnitt (14) aus einem Metall mit einem vorbestimmten Wärmeausdehnungskoeffizienten gebildet ist,
    einen Plungerkolben (12), der zur hin- und hergehenden Bewegung innerhalb der axialen Bohrung (20) eingebaut ist, wobei dieser Plungerkolben (12) aus einem abriebfesten, verschleißresistenten Keramikmaterial gebildet ist, und
    ein Antriebszugmittel zur Ausübung einer periodischen, den Druck erzeugenden Kraft auf den Plungerkolben (12), wodurch ein gesteuertes Volumen an Kraftstoff aus dem Kraftstoffinjektor (10) in einen Motorzylinder an bzw. in gewünschten Intervallen während des Motorbetriebs eingespritzt wird, wobei diese druckerzeugende Kraft eine wesentliche Seitenbelastungskraft umfaßt, die dazu neigt, die äußere Oberfläche des Plungerkolbens (12) in Kontakt bzw. Anlage mit der umgebenden inneren Oberfläche der axialen Bohrung (20) zu drücken,
    wobei der Plungerkolben (12) einen vorbestimmten Plungerkolbendurchmesser aufweist, der etwas geringer als der vorbestimmte Bohrungsdurchmesser ist, um ein Durchmesserspiel zwischen der axialen Bohrung (20) und dem Plungerkolben (12) zu bilden,
    dadurch gekennzeichnet, daß
    das Durchmesserspiel zwischen dem Plungerkolben (12) und der axialen Bohrung (20) 1,93 bis 3,25 µm (76-128 Millionstel eines Inch) beträgt,
    das Keramikmaterial des Plungerkolbens (12) eine niedrige Reaktivität bzw. Reaktionsbereitschaft und eine geringe Affinität, mit der Kraftstoff geschmierten inneren Oberfläche der axialen Bohrung (20) zu verschweißen, und einen Wärmeausdehnungskoeffizienten, der im wesentlichen dem Wärmeausdehnungskoeffizienten des den Körperabschnitt (14) bildenden Metalls entspricht, aufweist,
    das verschleißresistente Keramikmaterial des Plungerkolbens (12) besitzt einen Wärmeausdehnungskoeffizienten, der größer als 6 · 10-6/°C ist, und eine Härte größer als 800 kg/mm2 aufweist.
  2. Plungerkolbenaufbau nach Anspruch 1, dadurch gekennzeichnet, daß das keramische Material des Plungerkolbens (12) aus der Gruppe, bestehend aus Zirkon(di)oxid-, Aluminiumoxid-Zirkon(di)oxid- und Aluminiumoxid-Keramiken, ausgewählt ist.
  3. Plungerkolbenaufbau nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Plungerkolben (12) axial betreibbar in dem Kraftstoffinjektorkörperabschnitt (14) zwischen einer Verbindung (24), die mit dem Antriebszug verbunden ist, und einem Düsenende der Kraftstoffinjektoreinheit (10) angeordnet ist.
  4. Plungerkolbenaufbau nach Anspruch 3, dadurch gekennzeichnet, daß der Antriebszug einen Kipphebel (26), eine Stoß- bzw. Stößelstange (30) aufweist, die sich betätigungsmäßig von einer Nockenwelle (28) zu einer Seite des Kipphebels (26) erstreckt, und die Verbindung (24) aufweist, die sich betätigungsmäßig von dem anderen Ende des Kipphebels (26) zu dem Plungerkolben (12) erstreckt, um den Plungerkolben (12) hin und her zu bewegen, wenn die Nockenwelle (28) rotiert, wobei eine hohe axiale Kraft auf den Plungerkolben (12) durch die Verbindung (24) ausgeübt wird, wenn der Plungerkolben (12) zur Einspritzdüse vorgeschoben wird, und gleichzeitig eine Seitenkraft auf den Plungerkolben (12) durch die Verbindung (24) ausgeübt wird, welche den Plungerkolben (12) zu der inneren Wand der axialen Bohrung (20) drückt.
  5. Plungerkolbenaufbau nach einem der voranstehenden Ansprüche, dadurch gekennzeichnet, daß der Plungerkolben (12) ein Zeitsteuerplungerkolben ist.
EP95107461A 1994-05-18 1995-05-17 Kraftstoffdruckerzeugende Kolbenanordnung für eine druckgezündete Brennkraftmaschine Expired - Lifetime EP0683314B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US24558994A 1994-05-18 1994-05-18
US245589 1994-05-18

Publications (2)

Publication Number Publication Date
EP0683314A1 EP0683314A1 (de) 1995-11-22
EP0683314B1 true EP0683314B1 (de) 1999-12-15

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EP95107461A Expired - Lifetime EP0683314B1 (de) 1994-05-18 1995-05-17 Kraftstoffdruckerzeugende Kolbenanordnung für eine druckgezündete Brennkraftmaschine

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EP (1) EP0683314B1 (de)
JP (1) JP3223072B2 (de)
DE (1) DE69513880T2 (de)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6149073A (en) * 1994-05-18 2000-11-21 Cummins Engine Company, Inc. Ceramic plunger for internal combustion engine high pressure fuel system
US6688536B2 (en) 1997-10-22 2004-02-10 Caterpillar Inc Free floating plunger and fuel injector using same
JP4551878B2 (ja) * 2006-03-16 2010-09-29 株式会社東芝 ディーゼルエンジン
CN104895722A (zh) * 2015-06-09 2015-09-09 资阳蜀达科技有限公司 一种电子喷油器试验台

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0677656A1 (de) * 1994-03-14 1995-10-18 Cummins Engine Company, Inc. Verschleissfester Kraftstoffeinspritzkolbenzusammenbau

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS572458A (en) * 1980-06-05 1982-01-07 Nippon Denso Co Ltd Fuel injection device
FR2487106A1 (fr) * 1980-07-15 1982-01-22 Commissariat Energie Atomique Installation de remplacement d'un organe d'un circuit de fluide contamine et procede de remplacement de cet organe
JPS60104765A (ja) * 1983-11-09 1985-06-10 Yanmar Diesel Engine Co Ltd 燃料噴射ポンプ
JPS6131659A (ja) * 1984-07-24 1986-02-14 Yanmar Diesel Engine Co Ltd 燃料噴射弁
JPS61283759A (ja) * 1985-06-07 1986-12-13 Hitachi Metals Ltd 燃料噴射ポンプ用セラミツクス部品
US4848286A (en) * 1988-09-28 1989-07-18 Cummins Engine Company, Inc. Ceramic tiped pivot rod and method for its manufacture
US5072709A (en) * 1990-03-29 1991-12-17 Cummins Engine Co., Inc. Fuel injection for an internal combustion engine

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0677656A1 (de) * 1994-03-14 1995-10-18 Cummins Engine Company, Inc. Verschleissfester Kraftstoffeinspritzkolbenzusammenbau

Also Published As

Publication number Publication date
DE69513880T2 (de) 2000-04-20
DE69513880D1 (de) 2000-01-20
JPH08105362A (ja) 1996-04-23
EP0683314A1 (de) 1995-11-22
JP3223072B2 (ja) 2001-10-29

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