EP0683314B1 - Fuel pressurizing plunger assembly for a compression ignition engine - Google Patents
Fuel pressurizing plunger assembly for a compression ignition engine Download PDFInfo
- 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
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Images
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
Description
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.
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. However,
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 types of fuels increasingly used in Diesel engines, particularly fuels with low lubricity.
alternative fuels and fuels which may be contaminated with water, require a
scuff-resistant fuel injector plunger to maintain efficient engine operation. 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.
With a mechanical drive train heavy mechanical loads on the plunger in both axial
and tangential directions result in additional requirements for the diametral clearance
of the plunger within the bore in the injector body.
In view of the above it is the object of the present invention to provide 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.
Above object is achieved by providing a fuel pressurizing plunger assembly with the
features of the pre-characterizing part of claim 1 in combination with the features of
the characterizing part of claim 1. 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.
Further improvements of the fuel pressurizing plunger assembly of the invention may
be obtained from the dependent claims. Further objects and advantages will be apparent
from the following description and drawings.
In the drawings
- Fig. 1
- is a schematic cross-sectional view of a fuel injector assembly in a Diesel engine incorporating a scuff-resistant anti-stick plunger of the present invention; and
- Fig. 2
- presents graphically the dimensions of the injector body bore and plunger of the present invention for different materials at different temperatures.
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. Moreover,
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.
Referring to the drawings, 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). In addition to these axial and tangential loads, pressures
as high as 1690 bar (24,500 psi) are generated by the plunger's downward stroke as it
travels toward the injector nozzle 16. This results in a load of 1690 bar (24,500 psi)
acting on the plunger 12 in an upward axial direction, away from the nozzle 16 and
toward the rocker lever 26, as shown by arrow (C).
The ceramic plunger 12 is sized relative to the injector body bore 20 to provide a
diametral clearance of 1,93 to 3,25 µm (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.
The severity of the plunger operating environment is further increased by low sulfur
and low lubricity fuels and fuels contaminated by water. 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. Moreover, the ceramic material has a low reactivity and a low affinity to weld
with petroleum lubricated metal counterfaces. However, 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. Although other ceramics, most notably silicon
nitride, also display superior scuff resistance, only 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/mm2. 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 µm. 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 µm, while the clearance at the
curve D plunger assembly was 5,0 µm. 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 operation.
Claims (5)
- A fuel pressurizing plunger assembly for a compression ignition engine (Diesel engine) fuel injector (10) operable with Diesel fuel that may contain abrading particles and lubricity lowering contaminants,characterized in thatwherein the plunger assembly includesan axial bore (20) located within a body portion (14) of the fuel injector (10), the axial bore (20) defined by an inner surface of the body portion (14) having a predetermined bore diameter, said body portion (14) being formed of a metal having a predetermined thermal expansion coefficient,a plunger (12) mounted for reciprocating axial movement within said axial bore (20), this plunger (12) being formed of a scuff resistant, wear-resistant ceramic material, anda drive train means for applying a periodic pressurization force to the plunger (12) for causing a controlled volume of fuel to be injected from the fuel injector (10) into an engine cylinder at desired intervals during engine operation, this pressurization force including a substantial side loading force which tends to bias the external surface of the plunger (12) into contact with the surrounding inner surface of the axial bore (20),wherein the plunger (12) has a predetermined plunger diameter slightly less than the predetermined bore diameter to form a diametral clearance between the axial bore (20) and the plunger (12),the diametral clearance between the plunger (12) and the axial bore (20) is 1,93 to 3,25 µm (76 to 128 millionths of an inch),the ceramic material of the plunger (12) has a low reactivity and a low affinity to weld with the fuel lubricated inner surface of the axial bore (20) and a thermal expansion coefficient which is substantially the same as the thermal expansion coefficient of the metal forming the body portion (14),the wear-resistant ceramic material of the plunger (12) has a thermal expansion coefficient greater than 6 · 10-6/°C and a hardness greater that 800 kg/mm2.
- Plunger assembly according to claim 1, characterized in that the ceramic material of the plunger (12) is selected from the group consisting of zirconia, alumina-zirconia and alumina ceramics.
- Plunger assembly according to claim 1 or 2, characterized in that the plunger (12) is operably positioned axially within the fuel injector body portion (14) between a link (24) connected to the drive train and a nozzle end of the unit fuel injector (10).
- Plunger assembly according to claim 3, characterized in that the drive train includes a rocker lever (26), a push tube (30) operatively extending from a camshaft (28) to one side of the rocker lever (26), the link (24) operatively extending from the other side of the rocker lever (26) to the plunger (12) to cause the plunger (12) to reciprocate as the camshaft (28) rotates, whereby a high axial force is imposed on the plunger (12) by the link (24) as the plunger (12) is advanced toward the injector nozzle and a side force is simultaneously imposed on the plunger (12) by the link (24) which biases the plunger (12) toward the inner wall of the axial bore (20).
- Plunger assembly according to any one of the preceding claims, characterized in that the plunger (12) is a timing plunger.
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 (en) | 1995-11-22 |
| EP0683314B1 true EP0683314B1 (en) | 1999-12-15 |
Family
ID=22927297
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP95107461A Expired - Lifetime EP0683314B1 (en) | 1994-05-18 | 1995-05-17 | Fuel pressurizing plunger assembly for a compression ignition engine |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP0683314B1 (en) |
| JP (1) | JP3223072B2 (en) |
| DE (1) | DE69513880T2 (en) |
Families Citing this family (4)
| 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 (en) * | 2006-03-16 | 2010-09-29 | 株式会社東芝 | diesel engine |
| CN104895722A (en) * | 2015-06-09 | 2015-09-09 | 资阳蜀达科技有限公司 | Electronic oil injector testing stand |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0677656A1 (en) * | 1994-03-14 | 1995-10-18 | Cummins Engine Company, Inc. | Wear resistant fuel injector plunger assembly |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS572458A (en) * | 1980-06-05 | 1982-01-07 | Nippon Denso Co Ltd | Fuel injection device |
| FR2487106A1 (en) * | 1980-07-15 | 1982-01-22 | Commissariat Energie Atomique | SYSTEM FOR REPLACING AN ORGAN OF A CONTAMINATED FLUID CIRCUIT AND METHOD OF REPLACING IT |
| JPS60104765A (en) * | 1983-11-09 | 1985-06-10 | Yanmar Diesel Engine Co Ltd | Fuel-injection pump |
| JPS6131659A (en) * | 1984-07-24 | 1986-02-14 | Yanmar Diesel Engine Co Ltd | Fuel injection valve |
| JPS61283759A (en) * | 1985-06-07 | 1986-12-13 | Hitachi Metals Ltd | Ceramic parts for fuel injection pump |
| 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 |
-
1995
- 1995-05-17 DE DE1995613880 patent/DE69513880T2/en not_active Expired - Lifetime
- 1995-05-17 EP EP95107461A patent/EP0683314B1/en not_active Expired - Lifetime
- 1995-05-18 JP JP11965195A patent/JP3223072B2/en not_active Expired - Fee Related
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0677656A1 (en) * | 1994-03-14 | 1995-10-18 | Cummins Engine Company, Inc. | Wear resistant fuel injector plunger assembly |
Also Published As
| Publication number | Publication date |
|---|---|
| DE69513880D1 (en) | 2000-01-20 |
| JPH08105362A (en) | 1996-04-23 |
| DE69513880T2 (en) | 2000-04-20 |
| JP3223072B2 (en) | 2001-10-29 |
| EP0683314A1 (en) | 1995-11-22 |
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