EP1722098A1 - Fuel injection pump for internal combustion engine - Google Patents
Fuel injection pump for internal combustion engine Download PDFInfo
- Publication number
- EP1722098A1 EP1722098A1 EP05719961A EP05719961A EP1722098A1 EP 1722098 A1 EP1722098 A1 EP 1722098A1 EP 05719961 A EP05719961 A EP 05719961A EP 05719961 A EP05719961 A EP 05719961A EP 1722098 A1 EP1722098 A1 EP 1722098A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- diameter hole
- early stage
- suction
- small
- hole
- 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.)
- Withdrawn
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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
- 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
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
- F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
-
- 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
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
- F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
- F02M59/265—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders characterised by the arrangement or form of spill port of spill contour on the piston
-
- 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
- F02M59/20—Varying fuel delivery in quantity or timing
-
- 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
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0408—Pistons
-
- 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
- F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
- F04B11/0091—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using a special shape of fluid pass, e.g. throttles, ducts
Definitions
- the present invention relates to a fuel injection pump for an internal combustion engine which can reduce the generation of cavitation erosion.
- the inside of a pump chamber of a fuel injection pump for an internal combustion engine assumes an extremely high pressure.
- the pressure vibration having a high pressure peak is generated in a suction-and-overflow hole and an intake chamber and hence, air bubbles or hollow cavities are formed in the inside of the fuel and hollow cavities which are already formed with this high pressure peak rupture.
- the rupture of the hollow cavities occurs in the vicinity of a wall portion of the suction-and-overflow hole, the cavitation erosion is generated and a material which forms the pump is worn and when such a phenomenon takes place for a long period, functions of the pump are damaged.
- J-UT-B-7-54618 discloses a pump of a type having the constitution in which an early stage control groove is formed in a wall portion of a suction-and-overflow hole on a lower side opposite to an upper control edge portion, a control edge portion on a lower side of a pump plunger firstly skids on the early stage control groove and, thereafter, the control edge portion on the lower side of a pump plunger skids on a main transverse cross section of the suction-and-overflow hole, wherein a bottom portion of the early stage control groove extends upwardly in an inclined manner in the direction away from a skid surface of the pump plunger.
- a fuel injection flow which is generated in an early stage flows into the inside of the suction-and-overflow hole along the inclination of the bottom portion.
- a hollow cavity which is formed in the inside of the suction-and-overflow hole can be discharged toward the suction-and-overflow hole whereby it is possible to obtain an advantageous effect that the generation of the cavitation erosion which performs undesired actions in the inside of the suction-and-overflow hole can be avoided in these holes or at least reduced.
- a fuel injection pump for an internal combustion engine in which incoming and outgoing of fuel to at least one suction-and-overflow hole which is formed in a pump plunger bushing are controlled with an upper-side control edge portion and a lower-side control edge portion of a pump plunger reciprocating in the inside of the pump plunger bushing, and an early stage control groove is formed in a wall portion of the suction-and-overflow hole, wherein the suction-and-overflow hole includes a small-diameter hole having an opening which faces the inside of the pump plunger bushing at one end thereof and a large-diameter hole which is communicated with another end of the small-diameter hole, the suction-and-overflow hole is formed in a state that the early stage control groove extends toward the large-diameter hole from the opening of the small-diameter hole, and a bottom portion of the early stage control groove extends in an upwardly inclined manner in the direction away from the opening, and an inner surface
- high-pressure fuel which flows in the inside of the suction-and-overflow hole along the early stage control groove flows into the inside of the small-diameter hole along the inclination of the bottom portion of the early stage control groove and, when the high-pressure fuel is fed to the inside of the large-diameter hole, it is possible to ensure a large distance between the fed high-pressure fuel and a wall surface of the large-diameter hole due to an arcuate bottom surface shape of the large-diameter hole and hence, it is possible to remarkably reduce a cavitation erosion effect attributed to the rupture of a hollow cavity inside the high-pressure fuel whereby the lowering of a lifetime of the fuel injection pump can be effectively suppressed.
- Fig. 1 is a cross-sectional view showing one embodiment of a fuel injection pump according to the present invention.
- the fuel injection pump 1 serves to inject and supply pressurized high-pressure fuel into an internal combustion engine, wherein a pump plunger bushing 3 is fitted into the inside of the casing 2, a plunger chamber 5 is defined by the pump plunger bushing 3 and the pump plunger 4.
- Numeral 6 indicates a pressure valve and numeral 7 indicates a pressure valve casing, wherein the pressure valve casing 7 is fastened to the casing 2 by bolts.
- Suction-and-overflow holes 8 for fuel are formed in the pump plunger bushing 3, and suction-and-overflow chambers 9 are formed in the casing 2 in a state that the suction-and-overflow chambers 9 face the suction-and-overflow holes 8 in an opposed manner. Further, an early stage control groove 10 is formed in the suction-and-overflow hole 8.
- An upper-side control edge portion 11 and a lower-side control edge portion 12 are formed in the pump plunger 4, wherein due to the movement of the pump plunger 4 in the axial direction, these upper-side control edge portion 11 and lower-side control edge portion 12 skid on the early-stage control groove 10.
- the lower-side control edge portion 12 which defines the completion of supply firstly skids on the early stage control groove 10 which extends in an inclined manner at the time of completion of supply and, thereafter, the whole opening surface 14 of the suction-and-outflow hole 8 is opened.
- the pressure in the inside of the suction-and-overflow chamber 9 is increased relatively gently.
- two sets of suction-and-overflow holes 8 and suction-and-overflow chambers 9 are provided, wherein suction-and-overflow operations of the fuel are performed alternately with the phase difference of 180°.
- Fig. 2 is a cross-sectional view taken along a line A-A in Fig. 1
- Fig. 3 is a view as viewed from the direction of an arrow B in Fig. 2
- Fig. 4 is a cross-sectional view taken along a line C-C in Fig. 3.
- the suction-and-overflow hole 8 includes a cylindrical small-diameter hole 81 having an opening surface 14 which has one end 81A thereof opened on a pump plunger 4 side, and a large-diameter hole 82 which has one end 82A thereof opened on a suction-and-overflow chamber 9 side and has a diameter larger than a diameter of the small-diameter hole 81, wherein an inner surface of another end portion of the large-diameter hole 82 is formed into a spherical surface portion 82C which is formed into a spherical shape.
- another end 81B of the small-diameter hole 81 is communicated with the large-diameter hole 82 in a state that another end 81B faces the inside of the large-diameter hole 82 from a portion of the spherical surface portion 82C which is formed as a bottom surface in another end portion of the large-diameter hole 82.
- an axis 81x of the small-diameter hole 81 and an axis 82x of the large-diameter hole 82 are displaced from each other by a predetermined value k.
- This displacement direction is the direction in which the axis 82x is arranged opposite to the early stage control groove 10 with respect to the axis 81x.
- the early stage control groove 10 is formed as a trough-like groove having an arcuate cross-sectional bottom surface 10A in a portion of the small-diameter hole 81 and, at the same time, the bottom surface 10A of the early stage control groove 10 is inclined to make an angle ⁇ with respect to the axis 81x (see Fig. 4).
- the suction of the fuel is performed in a state that the pump plunger 4 is lowered and the upper-side control edge portion 11 allows the opening surface 14 of the small-diameter hole 81 to open to the plunger chamber 5.
- the pump plunger 4 is lifted so that the upper-side control edge portion 11 interrupts the opening surface 14 from the plunger chamber 5, the pressurizing of the fuel in the inside of the plunger chamber 5 starts, and when the lower-side control edge 12 starts opening of the early stage control groove 10, the high-pressure fuel which is obtained by pressurizing the fuel in the inside of the plunger chamber 5 flows into the inside of the suction-and-overflow hole 8 as the fuel injection flow along the early stage control groove 10.
- This fuel injection flow flows along the bottom surface 10A of the early stage control groove 10 and hence, the flow direction assumes a direction indicated by an arrow R which is parallel to the bottom surface 10A (see Fig. 4).
- the fuel injection flow which flows in from the small-diameter hole 81 is fed out to the inside of the large-diameter hole 82 vigorously.
- the axes 81x, 82x are displaced from each other by the predetermined value k and, at the same time, spherical surface portion 82C is formed on the bottom surface of another end portion of the large-diameter hole 82 and hence, a large spaces are ensured in front of the fuel injection flow which is fed out into the inside of the large-diameter hole 82.
- the hollow cavities which are generated in the inside of the high-pressure fuel enter the suction-and-overflow chamber 9 through this ensured large space.
- the provability that the hollow cavities which are generated in the high-pressure fuel in the inside of the suction-and-overflow hole 8 rupture in the vicinity of the inner wall surface of the large-diameter hole 82 can be remarkably lowered thus effectively suppressing the generation of the cavitation erosion.
- the fuel injection pump according to the present invention can effectively prevent the generation of the cavitation erosion in the suction-and-overflow hole and hence, the present invention is useful in improving the fuel injection pump for the internal combustion engine.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
- The present invention relates to a fuel injection pump for an internal combustion engine which can reduce the generation of cavitation erosion.
- The inside of a pump chamber of a fuel injection pump for an internal combustion engine assumes an extremely high pressure. As a result, in performing a discharge control of fuel, the pressure vibration having a high pressure peak is generated in a suction-and-overflow hole and an intake chamber and hence, air bubbles or hollow cavities are formed in the inside of the fuel and hollow cavities which are already formed with this high pressure peak rupture. When the rupture of the hollow cavities occurs in the vicinity of a wall portion of the suction-and-overflow hole, the cavitation erosion is generated and a material which forms the pump is worn and when such a phenomenon takes place for a long period, functions of the pump are damaged.
- To overcome this drawback, J-UT-B-7-54618 discloses a pump of a type having the constitution in which an early stage control groove is formed in a wall portion of a suction-and-overflow hole on a lower side opposite to an upper control edge portion, a control edge portion on a lower side of a pump plunger firstly skids on the early stage control groove and, thereafter, the control edge portion on the lower side of a pump plunger skids on a main transverse cross section of the suction-and-overflow hole, wherein a bottom portion of the early stage control groove extends upwardly in an inclined manner in the direction away from a skid surface of the pump plunger.
- According to this proposed constitution, a fuel injection flow which is generated in an early stage flows into the inside of the suction-and-overflow hole along the inclination of the bottom portion. As a result, a hollow cavity which is formed in the inside of the suction-and-overflow hole can be discharged toward the suction-and-overflow hole whereby it is possible to obtain an advantageous effect that the generation of the cavitation erosion which performs undesired actions in the inside of the suction-and-overflow hole can be avoided in these holes or at least reduced.
- However, recently, the use of low-viscosity fuel is increased and, conditions imposed on the use of fuel for cogeneration is becoming strict and hence, depending on the above-mentioned prior art, there may arise a drawback that the cavitation erosion is generated and such drawback occurs due to the use of the fuel injection pump for approximately 3000 to 5000 hours depending on cases.
- It is an object of the present invention to provide a fuel injection pump for an internal combustion engine which can overcome the above-mentioned problems of the related art.
- It is an object of the present invention to provide a fuel injection pump for an internal combustion engine which can further reduce the generation of the cavitation erosion by optimizing a shape of a suction-and-overflow hole formed in a plunger barrel of a fuel injection pump.
- According to the present invention, it is proposed a fuel injection pump for an internal combustion engine in which incoming and outgoing of fuel to at least one suction-and-overflow hole which is formed in a pump plunger bushing are controlled with an upper-side control edge portion and a lower-side control edge portion of a pump plunger reciprocating in the inside of the pump plunger bushing, and an early stage control groove is formed in a wall portion of the suction-and-overflow hole, wherein the suction-and-overflow hole includes a small-diameter hole having an opening which faces the inside of the pump plunger bushing at one end thereof and a large-diameter hole which is communicated with another end of the small-diameter hole, the suction-and-overflow hole is formed in a state that the early stage control groove extends toward the large-diameter hole from the opening of the small-diameter hole, and a bottom portion of the early stage control groove extends in an upwardly inclined manner in the direction away from the opening, and an inner surface of a communicating end portion of the large-diameter hole with the small-diameter hole is formed into a spherical surface. Here, an axis of the large-diameter hole may be displaced from an axis of the small-diameter hole in the direction opposite to the early stage control groove.
- According to the present invention, high-pressure fuel which flows in the inside of the suction-and-overflow hole along the early stage control groove flows into the inside of the small-diameter hole along the inclination of the bottom portion of the early stage control groove and, when the high-pressure fuel is fed to the inside of the large-diameter hole, it is possible to ensure a large distance between the fed high-pressure fuel and a wall surface of the large-diameter hole due to an arcuate bottom surface shape of the large-diameter hole and hence, it is possible to remarkably reduce a cavitation erosion effect attributed to the rupture of a hollow cavity inside the high-pressure fuel whereby the lowering of a lifetime of the fuel injection pump can be effectively suppressed.
-
- Fig. 1 is a cross-sectional view showing one embodiment of the present invention.
- Fig. 2 is a cross-sectional view taken along a line A-A in Fig. 1.
- Fig. 3 is a view as viewed from the direction of an arrow B in Fig. 2.
- Fig. 4 is a cross-sectional view taken along a line C-C in Fig. 3.
- To describe the present invention in more detail, the present invention is explained in conjunction with attached drawings.
- Fig. 1 is a cross-sectional view showing one embodiment of a fuel injection pump according to the present invention. The fuel injection pump 1 serves to inject and supply pressurized high-pressure fuel into an internal combustion engine, wherein a
pump plunger bushing 3 is fitted into the inside of thecasing 2, a plunger chamber 5 is defined by the pump plunger bushing 3 and thepump plunger 4. Numeral 6 indicates a pressure valve andnumeral 7 indicates a pressure valve casing, wherein thepressure valve casing 7 is fastened to thecasing 2 by bolts. Suction-and-overflow holes 8 for fuel are formed in the pump plunger bushing 3, and suction-and-overflow chambers 9 are formed in thecasing 2 in a state that the suction-and-overflow chambers 9 face the suction-and-overflow holes 8 in an opposed manner. Further, an earlystage control groove 10 is formed in the suction-and-overflow hole 8. - An upper-side
control edge portion 11 and a lower-sidecontrol edge portion 12 are formed in thepump plunger 4, wherein due to the movement of thepump plunger 4 in the axial direction, these upper-sidecontrol edge portion 11 and lower-sidecontrol edge portion 12 skid on the early-stage control groove 10. In this case, the lower-sidecontrol edge portion 12 which defines the completion of supply firstly skids on the earlystage control groove 10 which extends in an inclined manner at the time of completion of supply and, thereafter, the wholeopening surface 14 of the suction-and-outflow hole 8 is opened. As a result, due to the fuel injection flow which flows in an inclined manner in the early stage, the pressure in the inside of the suction-and-overflow chamber 9 is increased relatively gently. Here, in this embodiment, two sets of suction-and-overflow holes 8 and suction-and-overflow chambers 9 are provided, wherein suction-and-overflow operations of the fuel are performed alternately with the phase difference of 180°. - Next, the suction-and-
overflow hole 8 is explained in conjunction with Fig. 2 to Fig. 4. Here, Fig. 2 is a cross-sectional view taken along a line A-A in Fig. 1, Fig. 3 is a view as viewed from the direction of an arrow B in Fig. 2, and Fig. 4 is a cross-sectional view taken along a line C-C in Fig. 3. The suction-and-overflow hole 8 includes a cylindrical small-diameter hole 81 having anopening surface 14 which has oneend 81A thereof opened on apump plunger 4 side, and a large-diameter hole 82 which has oneend 82A thereof opened on a suction-and-overflow chamber 9 side and has a diameter larger than a diameter of the small-diameter hole 81, wherein an inner surface of another end portion of the large-diameter hole 82 is formed into aspherical surface portion 82C which is formed into a spherical shape. Further, anotherend 81B of the small-diameter hole 81 is communicated with the large-diameter hole 82 in a state that anotherend 81B faces the inside of the large-diameter hole 82 from a portion of thespherical surface portion 82C which is formed as a bottom surface in another end portion of the large-diameter hole 82. - In this embodiment, as can be easily understood from Fig .3 and Fig. 4, an axis 81x of the small-
diameter hole 81 and an axis 82x of the large-diameter hole 82 are displaced from each other by a predetermined value k. This displacement direction is the direction in which the axis 82x is arranged opposite to the earlystage control groove 10 with respect to the axis 81x. The earlystage control groove 10 is formed as a trough-like groove having an arcuatecross-sectional bottom surface 10A in a portion of the small-diameter hole 81 and, at the same time, thebottom surface 10A of the earlystage control groove 10 is inclined to make an angle θ with respect to the axis 81x (see Fig. 4). - Next, the manner of operations of suction, pressurizing and injection of the fuel in the fuel injection pump 1 is explained.
- The suction of the fuel is performed in a state that the
pump plunger 4 is lowered and the upper-sidecontrol edge portion 11 allows theopening surface 14 of the small-diameter hole 81 to open to the plunger chamber 5. When thepump plunger 4 is lifted so that the upper-sidecontrol edge portion 11 interrupts theopening surface 14 from the plunger chamber 5, the pressurizing of the fuel in the inside of the plunger chamber 5 starts, and when the lower-side control edge 12 starts opening of the earlystage control groove 10, the high-pressure fuel which is obtained by pressurizing the fuel in the inside of the plunger chamber 5 flows into the inside of the suction-and-overflow hole 8 as the fuel injection flow along the earlystage control groove 10. - This fuel injection flow flows along the
bottom surface 10A of the earlystage control groove 10 and hence, the flow direction assumes a direction indicated by an arrow R which is parallel to thebottom surface 10A (see Fig. 4). As a result, the fuel injection flow which flows in from the small-diameter hole 81 is fed out to the inside of the large-diameter hole 82 vigorously. As mentioned previously, the axes 81x, 82x are displaced from each other by the predetermined value k and, at the same time,spherical surface portion 82C is formed on the bottom surface of another end portion of the large-diameter hole 82 and hence, a large spaces are ensured in front of the fuel injection flow which is fed out into the inside of the large-diameter hole 82. - Accordingly, by allowing the fuel injection flow to flow into the inside of the suction-and-
overflow hole 8, the hollow cavities which are generated in the inside of the high-pressure fuel enter the suction-and-overflow chamber 9 through this ensured large space. As a result, the provability that the hollow cavities which are generated in the high-pressure fuel in the inside of the suction-and-overflow hole 8 rupture in the vicinity of the inner wall surface of the large-diameter hole 82 can be remarkably lowered thus effectively suppressing the generation of the cavitation erosion. Here, when it is possible to ensure a wide space which can reduce the influence of the cavitation erosion in front of the fuel injection flow fed out to the inside of the large-diameter hole 82 due to thespherical surface portion 82C, it is not always necessary to displace the axis 81x and the axis 82x and the predetermined value k may be set to 0. - As has been described heretofore, the fuel injection pump according to the present invention can effectively prevent the generation of the cavitation erosion in the suction-and-overflow hole and hence, the present invention is useful in improving the fuel injection pump for the internal combustion engine.
Claims (5)
- A fuel injection pump for an internal combustion engine in which incoming and outgoing of fuel to at least one suction-and-overflow hole which is formed in a pump plunger bushing are controlled with an upper-side control edge portion and a lower-side control edge portion of a pump plunger reciprocating in the inside of the pump plunger bushing, wherein
an early stage control groove is formed in a wall portion of the suction-and-overflow hole, the suction-and-overflow hole includes a small-diameter hole having an opening which faces the inside of the pump plunger bushing at one end thereof and a large-diameter hole which is communicated with another end of the small-diameter hole, the suction-and-overflow hole is formed in a state that the early stage control groove extends toward the large-diameter hole from the opening of the small-diameter hole, and a bottom portion of the early stage control groove extends in an upwardly inclined manner in the direction away from the opening, and an inner surface of a communicating end portion of the large-diameter hole with the small-diameter hole is formed into a spherical surface. - A fuel injection pump for an internal combustion engine according to claim 1, wherein an axis of the large-diameter hole is displaced from an axis of the small-diameter hole in the direction opposite to the early stage control groove by a predetermined value.
- A fuel injection pump for an internal combustion engine according to claim 1, wherein an axis of the large-diameter hole is displaced in a state that the axis of the large-diameter hole is shifted in parallel in the direction opposite to the early stage control grove with respect to an axis of the small-diameter hole.
- A fuel injection pump for an internal combustion engine according to claim 1, wherein the early stage control groove is a trough-shaped groove having an arcuate bottom surface shape in cross-section.
- A fuel injection pump for an internal combustion engine according to claim 1, wherein the bottom surface of the early stage control groove makes a predetermined angle with respect to the axis of the small-diameter hole.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004061643A JP4098738B2 (en) | 2004-03-05 | 2004-03-05 | Fuel injection pump for internal combustion engines |
PCT/JP2005/003664 WO2005085626A1 (en) | 2004-03-05 | 2005-02-25 | Fuel injection pump for internal combustion engine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1722098A1 true EP1722098A1 (en) | 2006-11-15 |
EP1722098A4 EP1722098A4 (en) | 2010-01-20 |
Family
ID=34918078
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05719961A Withdrawn EP1722098A4 (en) | 2004-03-05 | 2005-02-25 | Fuel injection pump for internal combustion engine |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP1722098A4 (en) |
JP (1) | JP4098738B2 (en) |
KR (1) | KR100781915B1 (en) |
CN (1) | CN100443715C (en) |
WO (1) | WO2005085626A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102021207001A1 (en) | 2021-07-05 | 2023-01-05 | Robert Bosch Gesellschaft mit beschränkter Haftung | Pump, in particular fuel injection pump |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1208635A (en) * | 1967-06-16 | 1970-10-14 | Bosch Gmbh Robert | Improvements in fuel injection pumps |
EP0372211A1 (en) * | 1988-11-26 | 1990-06-13 | Robert Bosch Gmbh | Fuel injection pump for injection internal-combustion engines |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS59184369U (en) * | 1983-05-27 | 1984-12-07 | 株式会社ボッシュオートモーティブ システム | row type fuel injection pump |
JPS62126564U (en) * | 1986-02-03 | 1987-08-11 | ||
DE3902764C2 (en) * | 1989-01-31 | 2002-10-17 | Bosch Gmbh Robert | Fuel injection pump |
DK176162B1 (en) * | 1997-04-21 | 2006-10-23 | Man B & W Diesel As | Fuel pump for internal combustion engines, especially large slow-moving marine diesel engines |
-
2004
- 2004-03-05 JP JP2004061643A patent/JP4098738B2/en not_active Expired - Lifetime
-
2005
- 2005-02-25 WO PCT/JP2005/003664 patent/WO2005085626A1/en active Application Filing
- 2005-02-25 CN CNB2005800070605A patent/CN100443715C/en active Active
- 2005-02-25 EP EP05719961A patent/EP1722098A4/en not_active Withdrawn
- 2005-02-25 KR KR1020067020440A patent/KR100781915B1/en active IP Right Grant
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1208635A (en) * | 1967-06-16 | 1970-10-14 | Bosch Gmbh Robert | Improvements in fuel injection pumps |
EP0372211A1 (en) * | 1988-11-26 | 1990-06-13 | Robert Bosch Gmbh | Fuel injection pump for injection internal-combustion engines |
Non-Patent Citations (1)
Title |
---|
See also references of WO2005085626A1 * |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102021207001A1 (en) | 2021-07-05 | 2023-01-05 | Robert Bosch Gesellschaft mit beschränkter Haftung | Pump, in particular fuel injection pump |
WO2023280482A1 (en) | 2021-07-05 | 2023-01-12 | Robert Bosch Gmbh | Pump, in particular fuel injection pump |
Also Published As
Publication number | Publication date |
---|---|
KR20060122975A (en) | 2006-11-30 |
JP4098738B2 (en) | 2008-06-11 |
CN100443715C (en) | 2008-12-17 |
JP2005248876A (en) | 2005-09-15 |
EP1722098A4 (en) | 2010-01-20 |
KR100781915B1 (en) | 2007-12-04 |
CN1961146A (en) | 2007-05-09 |
WO2005085626A1 (en) | 2005-09-15 |
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