WO2023032253A1 - 燃料ポンプ - Google Patents
燃料ポンプ Download PDFInfo
- Publication number
- WO2023032253A1 WO2023032253A1 PCT/JP2022/004023 JP2022004023W WO2023032253A1 WO 2023032253 A1 WO2023032253 A1 WO 2023032253A1 JP 2022004023 W JP2022004023 W JP 2022004023W WO 2023032253 A1 WO2023032253 A1 WO 2023032253A1
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- WO
- WIPO (PCT)
- Prior art keywords
- valve
- relief valve
- chamber
- plunger
- fuel
- Prior art date
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- 239000000446 fuel Substances 0.000 title claims abstract description 198
- 230000007246 mechanism Effects 0.000 claims abstract description 103
- 230000007423 decrease Effects 0.000 claims abstract description 12
- 230000002093 peripheral effect Effects 0.000 claims description 16
- 230000006835 compression Effects 0.000 abstract 3
- 238000007906 compression Methods 0.000 abstract 3
- 230000010349 pulsation Effects 0.000 description 11
- 230000003628 erosive effect Effects 0.000 description 6
- 239000002828 fuel tank Substances 0.000 description 6
- 238000007789 sealing Methods 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 239000012530 fluid Substances 0.000 description 5
- 230000001174 ascending effect Effects 0.000 description 4
- 238000002485 combustion reaction Methods 0.000 description 4
- 238000004891 communication Methods 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 238000002347 injection Methods 0.000 description 3
- 239000007924 injection Substances 0.000 description 3
- 239000002184 metal Substances 0.000 description 3
- XKRFYHLGVUSROY-UHFFFAOYSA-N Argon Chemical compound [Ar] XKRFYHLGVUSROY-UHFFFAOYSA-N 0.000 description 2
- 230000006837 decompression Effects 0.000 description 2
- 230000006866 deterioration Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 239000010705 motor oil Substances 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- 229910052786 argon Inorganic materials 0.000 description 1
- 230000003111 delayed effect Effects 0.000 description 1
- 239000011261 inert gas Substances 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000007480 spreading Effects 0.000 description 1
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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
- F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
-
- 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
- F02M59/46—Valves
- F02M59/464—Inlet valves of the check valve type
-
- 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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/005—Pressure relief valves
-
- 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
- F02M59/46—Valves
- F02M59/462—Delivery valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
- F16K17/0406—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded in the form of balls
Definitions
- the present invention relates to a fuel pump that pressurizes fuel and supplies it to an engine.
- a fuel pump is disclosed, for example, in Japanese Unexamined Patent Application Publication No. 2002-200012.
- a high-pressure fuel supply pump disclosed in Patent Document 1 includes a housing, an intake valve, a discharge valve, and a relief valve.
- the housing has a cylinder, which is a stepped cylindrical space that accommodates a cylinder liner that slidably holds the plunger and that forms a pressure chamber.
- the intake valve opens when no current is supplied to the electromagnetic solenoid, and opens when the electromagnetic solenoid is supplied with current to suck fuel into the pressure chamber.
- the discharge valve is attached to the discharge valve housing portion of the housing, and the discharge valve housing portion communicates with the pressure chamber through the fuel discharge hole. High-pressure fuel pressurized in the pressurization chamber is supplied to the discharge valve.
- the discharge valve opens when the pressure of the supplied fuel reaches or exceeds a predetermined pressure, and the fuel that has passed through the discharge valve is pressure-fed to the pressure accumulator.
- the relief valve is assembled in a relief valve accommodating portion of the housing, and the relief valve accommodating portion communicates with the high pressure region downstream of the discharge valve and also communicates with the pressurizing chamber via the communication passage.
- the relief valve opens when the pressure of the fuel in the high-pressure region reaches a specific pressure or higher, and recirculates the high-pressure fuel to the pressurization chamber.
- the high-pressure fuel supply pump described in Patent Document 1 repeats the rise and fall of the pressure in the pressurization chamber by moving the plunger up and down.
- cavitation may occur in the vicinity of the relief valve seat located at the back of the pressurizing chamber when the plunger descends and the pressure in the pressurizing chamber decreases. The generated cavitation collapses when the plunger rises and the pressure in the pressurizing chamber increases.
- An object of the present invention is to provide a fuel pump that prevents cavitation from occurring in the vicinity of the seat member in the valve mechanism in consideration of the above problems.
- the fuel pump of the present invention comprises a reciprocating plunger, a pressurizing chamber whose volume increases and decreases according to the reciprocating motion of the plunger, and a relief for returning fuel to the pressurizing chamber. and a valve mechanism.
- the relief valve mechanism includes a relief valve and a seat member having a valve contact portion on which the relief valve is seated. The relief valve is arranged closer to the plunger than the seat member.
- the seat member has an annular groove forming a space communicating with the pressurizing chamber between the seat member and the fixed portion surrounding the outer peripheral surface of the seat member. The space is provided at a position farther from the plunger than the valve contact portion.
- FIG. 1 is an overall configuration diagram of a fuel supply system using a high-pressure fuel supply pump according to one embodiment of the present invention
- FIG. 1 is a longitudinal sectional view (Part 1) of a high-pressure fuel supply pump according to an embodiment of the present invention
- FIG. FIG. 2 is a longitudinal sectional view (No. 2) of the high-pressure fuel supply pump according to one embodiment of the present invention
- 1 is a horizontal cross-sectional view of a high-pressure fuel supply pump according to an embodiment of the present invention, viewed from above
- FIG. FIG. 3 is a longitudinal sectional view (No. 3) of the high-pressure fuel supply pump according to the embodiment of the present invention
- FIG. 2 is a vertical sectional view around a relief valve mechanism according to one embodiment of the present invention
- FIG. 4 is an explanatory diagram showing cavitation generation positions around a relief valve mechanism according to one embodiment of the present invention
- FIG. 1 is an overall configuration diagram of a fuel supply system using a high-pressure fuel supply pump according to this embodiment.
- the fuel supply system includes a high-pressure fuel supply pump (fuel pump) 100, an ECU (Engine Control Unit) 101, a fuel tank 103, a common rail 106, and a plurality of injectors 107.
- fuel pump fuel pump
- ECU Engine Control Unit
- Fuel tank 103
- common rail common rail
- injectors 107
- Components of the high-pressure fuel supply pump 100 are integrally incorporated into the pump body 1 .
- the fuel in the fuel tank 103 is pumped up by a feed pump 102 driven based on a signal from the ECU 101.
- the pumped fuel is pressurized to an appropriate pressure by a pressure regulator (not shown) and sent to the low-pressure fuel suction port 51 of the high-pressure fuel supply pump 100 through the low-pressure pipe 104 .
- the high-pressure fuel supply pump 100 pressurizes the fuel supplied from the fuel tank 103 and pumps it to the common rail 106 .
- a plurality of injectors 107 and a fuel pressure sensor 105 are attached to the common rail 106 .
- a plurality of injectors 107 are mounted according to the number of cylinders (combustion chambers), and inject fuel according to the drive current output from the ECU 101 .
- the fuel supply system of this embodiment is a so-called direct injection engine system in which the injector 107 directly injects fuel into the cylinder of the engine.
- the fuel pressure sensor 105 outputs the detected pressure data to the ECU 101.
- the ECU 101 determines an appropriate injection fuel amount (target injection fuel length) and an appropriate fuel pressure (target fuel pressure), etc.
- the ECU 101 also controls driving of the high-pressure fuel supply pump 100 and the plurality of injectors 107 based on calculation results such as the fuel pressure (target fuel pressure). That is, the ECU 101 has a pump control section that controls the high-pressure fuel supply pump 100 and an injector control section that controls the injector 107 .
- the high-pressure fuel supply pump 100 has a pressure pulsation reducing mechanism 9, an electromagnetic intake valve mechanism 3 that is a variable capacity mechanism, a relief valve mechanism 4 (see FIG. 2), and a discharge valve mechanism 8.
- the fuel flowing from the low-pressure fuel intake port 51 reaches the intake port 31b of the electromagnetic intake valve mechanism 3 via the pressure pulsation reducing mechanism 9 and the intake passage 10b.
- the fuel that has flowed into the electromagnetic suction valve mechanism 3 passes through the valve portion 32, flows through the suction passage 1d formed in the pump body 1, and then flows into the pressurization chamber 11.
- a plunger 2 is reciprocally inserted into the pressurizing chamber 11 .
- the plunger 2 reciprocates when power is transmitted by a cam 91 (see FIG. 2) of the engine.
- the pressurization chamber 11 fuel is sucked from the electromagnetic intake valve mechanism 3 during the downward stroke of the plunger 2, and is pressurized during the upward stroke.
- the discharge valve mechanism 8 is opened, and high pressure fuel is pressure-fed to the common rail 106 through the discharge passage 12a.
- the discharge of fuel by the high-pressure fuel supply pump 100 is operated by opening and closing the electromagnetic intake valve mechanism 3 .
- the opening and closing of the electromagnetic intake valve mechanism 3 is controlled by the ECU 101 .
- FIG. 2 is a vertical cross-sectional view (Part 1) of the high-pressure fuel supply pump 100 as seen in a cross section perpendicular to the horizontal direction.
- FIG. 3 is a vertical cross-sectional view (No. 2) of the high-pressure fuel supply pump 100 seen in a cross section perpendicular to the horizontal direction.
- FIG. 4 is a horizontal cross-sectional view of the high-pressure fuel supply pump 100 seen in a cross-section perpendicular to the vertical direction.
- FIG. 5 is a vertical cross-sectional view (part 3) of the high-pressure fuel supply pump 100 seen in a cross section perpendicular to the horizontal direction.
- FIG. 6 is an explanatory diagram showing the relief valve mechanism 4 in an enlarged manner.
- the pump body 1 of the high-pressure fuel supply pump 100 is formed in a substantially cylindrical shape. As shown in FIGS. 2 and 3, the pump body 1 is internally provided with a first chamber 1a, a second chamber 1b, a third chamber 1c, and a suction passage 1d. The pump body 1 is in close contact with the fuel pump mounting portion 90 and fixed with a plurality of bolts (screws) (not shown).
- the first chamber 1a is a cylindrical space provided in the pump body 1, and the centerline 1A of the first chamber 1a coincides with the centerline of the pump body 1.
- One end of a plunger 2 is inserted into the first chamber 1a, and the plunger 2 reciprocates within the first chamber 1a.
- the first chamber 1 a and one end of the plunger 2 form a pressure chamber 11 .
- the second chamber 1b is a cylindrical space provided in the pump body 1, and the centerline of the second chamber 1b is perpendicular to the centerline of the pump body 1 (first chamber 1a).
- a relief valve chamber in which the relief valve mechanism 4 is arranged is formed in the second chamber 1b.
- the diameter of the second chamber 1b (relief valve chamber) is smaller than the diameter of the first chamber 1a.
- the first chamber 1a and the second chamber 1b communicate with each other through a circular communication hole 1e. After passing through the relief valve mechanism 4, the fuel returns to the pressure chamber 11 through the communication hole 1e.
- the third chamber 1c is a cylindrical space provided in the pump body 1 and is continuous with the other end of the first chamber 1a.
- the centerline of the third chamber 1c coincides with the centerline 1A of the first chamber 1a and the centerline of the pump body 1, and the diameter of the third chamber 1c is larger than the diameter of the first chamber 1a.
- a cylinder 6 that guides the reciprocating motion of the plunger 2 is arranged in the third chamber 1c. As a result, the end surface of the cylinder 6 can be brought into contact with the stepped portion (flat portion) between the first chamber 1a and the third chamber 1c, thereby preventing the cylinder 6 from being displaced toward the first chamber 1a. can be prevented.
- the cylinder 6 is formed in a tubular shape, and its outer peripheral side is press-fitted into the third chamber 1c of the pump body 1 .
- One end of the cylinder 6 is in contact with the top surface of the third chamber 1c (the stepped portion between the first chamber 1a and the third chamber 1c).
- the plunger 2 is in slidable contact with the inner peripheral surface of the cylinder 6 .
- the pump body 1 is provided with a fixing portion 1x that engages with the substantially central portion of the cylinder 6 in the axial direction.
- the fixed portion 1x is formed to be plastically deformable. The fixed portion 1x presses the cylinder 6 upward (upward in FIG. 2).
- An O-ring 93 which is a specific example of a seat member, is interposed between the fuel pump mounting portion 90 and the pump body 1.
- the O-ring 93 prevents engine oil from leaking outside the engine (internal combustion engine) through between the fuel pump mounting portion 90 and the pump body 1 .
- a tappet 92 is provided at the lower end of the plunger 2 .
- the tappet 92 converts the rotational motion of the cam 91 attached to the camshaft of the engine into vertical motion and transmits it to the plunger 2 .
- the plunger 2 is urged toward the cam 91 by the spring 16 via the retainer 15 and pressed against the tappet 92 .
- the tappet 92 reciprocates as the cam 91 rotates.
- the plunger 2 reciprocates together with the tappet 92 to change the volume of the pressurization chamber 11 .
- a seal holder 17 is arranged between the cylinder 6 and the retainer 15 .
- the seal holder 17 is formed in a cylindrical shape into which the plunger 2 is inserted, and has an auxiliary chamber 17a at the upper end portion on the cylinder 6 side.
- the seal holder 17 holds a plunger seal 18 at the lower end on the retainer 15 side.
- the plunger seal 18 is in slidable contact with the outer circumference of the plunger 2, and when the plunger 2 reciprocates, it seals the fuel in the auxiliary chamber 17a and prevents the fuel in the auxiliary chamber 17a from flowing into the engine. there is The plunger seal 18 also prevents lubricating oil (including engine oil) that lubricates sliding parts in the engine from flowing into the pump body 1 .
- the plunger 2 reciprocates vertically. If the plunger 2 descend
- the plunger 2 has a large diameter portion 2a and a small diameter portion 2b.
- the large diameter portion 2a and the small diameter portion 2b are positioned in the auxiliary chamber 17a. Therefore, the volume of the auxiliary chamber 17a increases and decreases as the plunger 2 reciprocates.
- the sub-chamber 17a communicates with the low-pressure fuel chamber 10 through a fuel passage 10c (see FIG. 5).
- a fuel passage 10c see FIG. 5
- the plunger 2 moves downward, fuel flows from the auxiliary chamber 17a to the low-pressure fuel chamber 10.
- the plunger 2 moves upward, fuel flows from the low-pressure fuel chamber 10 to the auxiliary chamber 17a.
- the flow rate of fuel into and out of the high-pressure fuel supply pump 100 during the intake stroke or return stroke of the high-pressure fuel supply pump 100 can be reduced, and the pressure pulsation generated inside the high-pressure fuel supply pump 100 can be reduced.
- a low-pressure fuel chamber 10 is provided in the upper portion of the pump body 1 of the high-pressure fuel supply pump 100 .
- a suction joint 5 communicating with a low-pressure fuel chamber 10 is attached to a side portion of the pump body 1 .
- the suction joint 5 is connected to a low-pressure pipe 104 through which fuel supplied from a fuel tank 103 (see FIG. 1) passes. Fuel in the fuel tank 103 is supplied to the inside of the pump body 1 from the intake joint 5 .
- the suction joint 5 has a low-pressure fuel suction port 51 connected to the low-pressure pipe 104 and a suction passage 52 communicating with the low-pressure fuel suction port 51 .
- the fuel that has passed through the suction flow path 52 passes through a suction filter 53 provided inside the pump body 1 and is supplied to the low-pressure fuel chamber 10 .
- the suction filter 53 removes foreign matter present in the fuel and prevents the foreign matter from entering the high-pressure fuel supply pump 100 .
- the low-pressure fuel chamber 10 is provided with a low-pressure fuel passage 10a and an intake passage 10b (see FIG. 2).
- a pressure pulsation reduction mechanism 9 is provided in the low-pressure fuel flow path 10a.
- the pressure pulsation reducing mechanism 9 reduces pressure pulsation generated in the high-pressure fuel supply pump 100 from spreading to the low-pressure pipe 104 .
- the pressure pulsation reducing mechanism 9 is formed of a metal diaphragm damper in which two corrugated disk-shaped metal plates are pasted together at their outer periphery and an inert gas such as argon is injected inside.
- the metal diaphragm damper of the pressure pulsation reducing mechanism 9 absorbs or reduces pressure pulsation by expanding and contracting.
- the intake passage 10b communicates with the intake port 31b (see FIG. 2) of the electromagnetic intake valve mechanism 3, and the fuel that has passed through the low-pressure fuel passage 10a enters the intake port of the electromagnetic intake valve mechanism 3 through the intake passage 10b. 31b is reached.
- the electromagnetic suction valve mechanism 3 is inserted into a suction valve chamber 30 formed in the pump body 1.
- the intake valve chamber 30 is provided on the upstream side (on the side of the intake passage 10b) of the pressurization chamber 11, and is formed as a horizontal hole extending in the horizontal direction.
- the electromagnetic intake valve mechanism 3 includes an intake valve seat 31 press-fitted into the intake valve chamber 30, a valve portion 32, a rod 33, a rod biasing spring 34, an electromagnetic coil 35, and an anchor 36. .
- the intake valve seat 31 is formed in a cylindrical shape, and has a seating portion 31a on its inner periphery. Further, the intake valve seat 31 is formed with an intake port 31b reaching from the outer peripheral portion to the inner peripheral portion. The intake port 31b communicates with the intake passage 10b in the low-pressure fuel chamber 10 described above.
- a stopper 37 facing the seating portion 31 a of the intake valve seat 31 is arranged in the intake valve chamber 30 .
- a valve portion 32 is arranged between the stopper 37 and the seat portion 31a.
- a valve biasing spring 38 is interposed between the stopper 37 and the valve portion 32 . The valve biasing spring 38 biases the valve portion 32 toward the seat portion 31a.
- the valve portion 32 closes the communicating portion between the suction port 31b and the pressurizing chamber 11 by coming into contact with the seat portion 31a.
- the electromagnetic suction valve mechanism 3 is in the closed state.
- the valve portion 32 opens the communicating portion between the intake port 31b and the pressurizing chamber 11 by coming into contact with the stopper 37 .
- the electromagnetic suction valve mechanism 3 is in the open state.
- the rod 33 passes through the cylinder hole of the intake valve seat 31 and has one end in contact with the valve portion 32 .
- the rod biasing spring 34 biases the valve portion 32 in the valve opening direction toward the stopper 37 via the rod 33 .
- One end of the rod biasing spring 34 is engaged with the other end of the rod 33 .
- the other end of the rod biasing spring 34 is engaged with a magnetic core 39 arranged to surround the rod biasing spring 34 .
- the anchor 36 faces the end surface of the magnetic core 39 . Also, the anchor 36 is engaged with a flange provided in the intermediate portion of the rod 33 .
- the electromagnetic coil 35 is arranged around the magnetic core 39 .
- a terminal member 40 is electrically connected to the electromagnetic coil 35 , and current flows through the terminal member 40 .
- the rod 33 In a non-energized state in which no current flows through the electromagnetic coil 35, the rod 33 is urged in the valve opening direction by the urging force of the rod urging spring 34. Thereby, the rod 33 presses the valve portion 32 in the valve opening direction. As a result, the valve portion 32 is separated from the seat portion 31a and comes into contact with the stopper 37, and the electromagnetic suction valve mechanism 3 is in the open state. That is, the electromagnetic intake valve mechanism 3 is of a normally open type that opens when no power is supplied.
- the fuel in the intake port 31b passes between the valve portion 32 and the seat portion 31a, the plurality of fuel passage holes (not shown) of the stopper 37 and the intake passage 1d. It flows into the pressurization chamber 11 .
- the electromagnetic intake valve mechanism 3 When the electromagnetic intake valve mechanism 3 is open, the valve portion 32 is in contact with the stopper 37, so the position of the valve portion 32 in the valve opening direction is restricted.
- the gap between the valve portion 32 and the seat portion 31a in the open state of the electromagnetic intake valve mechanism 3 is the movable range of the valve portion 32, which is the valve opening stroke.
- the anchor 36 When the electromagnetic coil 35 is energized, the anchor 36 is pulled in the valve closing direction by the magnetic attraction force of the magnetic core 39 . As a result, the anchor 36 moves against the biasing force of the rod biasing spring 34 and contacts the magnetic core 39 .
- the anchor 36 moves in the valve closing direction, which is the side of the magnetic core 39 , the rod 33 with which the anchor 36 engages moves together with the anchor 36 .
- the valve portion 32 is released from the biasing force in the valve opening direction, and moves in the valve closing direction due to the biasing force of the valve biasing spring 38 .
- the electromagnetic intake valve mechanism 3 When the valve portion 32 contacts the seating portion 31a of the intake valve seat 31, the electromagnetic intake valve mechanism 3 is closed.
- the discharge valve mechanism 8 is arranged in a discharge valve chamber 80 provided on the outlet side (downstream side) of the pressurization chamber 11 .
- the discharge valve mechanism 8 includes a discharge valve seat 81 communicating with the pressurizing chamber 11, a valve portion 82 contacting and separating from the discharge valve seat 81, and a discharge valve spring 83 biasing the valve portion 82 toward the discharge valve seat 81 side. , and a discharge valve stopper 84 that determines the stroke (movement distance) of the valve portion 82 .
- the discharge valve mechanism 8 has a plug 85 that blocks leakage of fuel to the outside.
- the discharge valve stopper 84 is press-fitted into the plug 85 .
- the plug 85 is welded to the pump body 1 at a weld 86 .
- the discharge valve chamber 80 is opened and closed by a valve portion 82 .
- the discharge valve chamber 80 communicates with a discharge valve chamber passage 87 .
- the discharge valve chamber passage 87 is formed in the pump body 1 .
- a lateral hole communicating with the second chamber 1b (relief valve chamber) shown in FIG. 2 is provided in the pump body 1, and a discharge joint 12 is inserted into the lateral hole.
- the discharge joint 12 has the above-described discharge passage 12a communicating with the lateral hole of the pump body 1 and the discharge valve chamber passage 87, and a fuel discharge port 12b that is one end of the discharge passage 12a.
- a fuel discharge port 12 b of the discharge joint 12 communicates with the common rail 106 .
- the discharge joint 12 is fixed to the pump body 1 by welding with a welding portion 12c.
- the discharge valve mechanism 8 When the discharge valve mechanism 8 is opened, the (high-pressure) fuel in the pressurization chamber 11 passes through the discharge valve mechanism 8 and reaches the discharge valve chamber 80 (discharge valve chamber passage 87). The fuel reaching the discharge valve chamber passage 87 is discharged through the fuel discharge port 12b of the discharge joint 12 to the common rail 106 (see FIG. 1). With the configuration described above, the discharge valve mechanism 8 functions as a check valve that restricts the flow direction of the fuel.
- the relief valve mechanism 4 shown in FIGS. 2 and 6 is actuated when the common rail 106 or the members beyond it have some kind of problem and the pressure of the common rail 106 exceeds a predetermined pressure.
- 11 is a valve configured to return the fuel therein to the pressurization chamber 11 .
- the discharge passage 12 a communicates with the discharge valve chamber 80 via a discharge valve chamber passage 87 . Therefore, the pressure in the discharge passage 12a and the pressure in the discharge valve chamber 80 are equal.
- the relief valve mechanism 4 opens when the difference between the pressure in the discharge valve chamber 80 (discharge valve chamber passage 87) and the pressure in the second chamber 1b (relief valve chamber) exceeds a set value.
- the relief valve mechanism 4 has a relief spring 41 , a relief valve holder 42 , a relief valve 43 and a seat member 44 .
- the relief valve mechanism 4 is inserted from the discharge joint 12 and arranged in the second chamber 1b (relief valve chamber).
- the relief spring 41 is a coiled spring, and one end abuts against the pump body 1 (one end of the second chamber 1b). Also, the other end of the relief spring 41 is in contact with the relief valve holder 42 . The relief valve holder 42 is engaged with the relief valve 43 . The relief spring 41 is compressed to urge the relief valve holder 42 and the relief valve 43 toward the seat member 44 .
- the seat member 44 is press-fitted into the second chamber 1b (relief valve chamber).
- the seat member 44 has a fuel passage 44 a facing the relief valve 43 .
- the side of the fuel passage 44a opposite to the relief valve 43 communicates with the discharge passage 12a.
- the relief valve 43 is pressed by the biasing force of the relief spring 41 and comes into contact with the seat member 44 . Thereby, the relief valve 43 blocks the fuel passage 44 a of the seat member 44 . Movement of fuel between the pressurizing chamber 11 (upstream side) and the seat member 44 (downstream side) is interrupted by the relief valve 43 contacting (adhering to) the seat member 44 to block the fuel passage 44a.
- the electromagnetic intake valve mechanism 3 As described above, if the electromagnetic intake valve mechanism 3 is closed during the ascending stroke, the fuel sucked into the pressurization chamber 11 during the intake stroke is pressurized and discharged to the common rail 106 side. On the other hand, if the electromagnetic suction valve mechanism 3 is open during the ascending stroke, the fuel in the pressurization chamber 11 is pushed back toward the suction passage 1d and is not discharged to the common rail 106 side. Thus, the discharge of fuel by the high-pressure fuel supply pump 100 is controlled by opening and closing the electromagnetic intake valve mechanism 3 . The opening and closing of the electromagnetic intake valve mechanism 3 is controlled by the ECU 101 .
- the volume of the pressurization chamber 11 increases and the fuel pressure in the pressurization chamber 11 decreases.
- the fluid differential pressure between the intake port 31b and the pressurizing chamber 11 (hereinafter referred to as "fluid differential pressure across the valve portion 32") is reduced.
- the biasing force of the rod biasing spring 34 becomes greater than the differential pressure of the fluid across the valve portion 32, the rod 33 moves in the valve opening direction, and the valve portion 32 separates from the seating portion 31a of the intake valve seat 31. , the electromagnetic intake valve mechanism 3 is opened.
- the fuel in the intake port 31b passes between the valve portion 32 and the seat portion 31a, passes through a plurality of fuel passage holes (not shown) of the stopper 37, and enters the intake passage. It flows into the pressurization chamber 11 from 1d.
- the electromagnetic intake valve mechanism 3 is open, the valve portion 32 is in contact with the stopper 37, so the position of the valve portion 32 in the valve opening direction is restricted.
- the gap between the valve portion 32 and the seat portion 31a in the open state of the electromagnetic intake valve mechanism 3 is the movable range of the valve portion 32, which is the valve opening stroke.
- the difference between the biasing forces of the rod biasing spring 34 and the valve biasing spring 38 is set larger than the fluid force so that the electromagnetic suction valve mechanism 3 maintains the valve open state.
- the volume of the pressurization chamber 11 decreases as the plunger 2 rises. Therefore, the fuel sucked into the pressurization chamber 11 passes again between the valve portion 32 and the seat portion 31a and is returned to the suction port 31b, and the pressure inside the pressurization chamber 11 rises. There is no This stroke is called a return stroke.
- valve portion 32 When the anchor 36 (rod 33) moves in the valve closing direction, the valve portion 32 is released from the urging force in the valve opening direction, and the urging force of the valve urging spring 38 and the flow of the fuel flowing into the intake passage 10b are released. It moves in the valve closing direction by physical strength. When the valve portion 32 contacts the seating portion 31a of the intake valve seat 31 (the valve portion 32 is seated on the seating portion 31a), the electromagnetic intake valve mechanism 3 is closed.
- the pressure of the fuel in the pressure chamber 11 increases as the plunger 2 rises. See).
- This stroke is called a discharge stroke. That is, the upward stroke from the lower start point to the upper start point of the plunger 2 consists of a return stroke and a discharge stroke.
- the timing of energizing the electromagnetic coil 35 If the timing of energizing the electromagnetic coil 35 is advanced, the proportion of the return stroke during the upward stroke becomes smaller and the proportion of the discharge stroke becomes larger. As a result, less fuel is returned to the intake passage 10b, and more fuel is discharged at high pressure. On the other hand, if the timing of energizing the electromagnetic coil 35 is delayed, the proportion of the return stroke in the upward stroke increases and the proportion of the ejection stroke decreases. As a result, more fuel is returned to the intake passage 10b, and less fuel is discharged at high pressure. By controlling the timing of energization of the electromagnetic coil 35 in this way, the amount of fuel discharged at high pressure can be controlled to the amount required by the engine (internal combustion engine).
- FIG. 7 is an explanatory diagram showing cavitation generation positions around the relief valve mechanism 4. As shown in FIG.
- the relief valve 43 is pressed against the seat member 44 by the spring force of the relief spring 41 .
- the seat member 44 has a valve contact portion 44b with which the relief valve 43 contacts (seats).
- the relief valve mechanism 4 has a sealing function due to the tight contact between the relief valve 43 and the valve contact portion 44b of the seat member 44 . Therefore, when the relief valve 43 and the valve contact portion 44b of the seat member 44 are in close contact with each other, the pressure chamber 11 including the second chamber 1b and the discharge passage 12a are liquid-tightly sealed.
- the relief valve mechanism 4 Since the relief valve mechanism 4 has a sealing function, it becomes possible to pressurize the fuel in the pressurization chamber 11 when the plunger 2 (see FIG. 6) is raised. Further, since the relief valve mechanism 4 has a sealing function, even after the plunger 2 stops operating, the pressure of the fuel in the discharge valve chamber 80 and the pressure of the fuel in the common rail 106 can be maintained. Therefore, in order to maintain the fuel pressure in the common rail 106, the sealing function at the valve contact portion 44b is important.
- valve contact portion 44b of the seat member 44 is arranged at the innermost portion farthest from the plunger 2 in the pressurizing chamber 11 .
- cavitation occurs in the space 47 near the valve contact portion 44b.
- the plunger 2 rises and the fuel in the pressurization chamber 11 is pressurized the cavitation collapses.
- annular groove 45 is provided on the outer peripheral surface of one end of the seat member 44 .
- a substantially circular flange 46 is formed at one end of the seat member 44 .
- the collar portion 46 faces the relief valve holder 42 .
- the diameter of the collar portion 46 is smaller than the diameter of the second chamber 1b.
- a valve contact portion 44b that is continuous with the fuel passage 44a is provided at the center of the flange portion 46 .
- the valve contact portion 44b is formed as a ring-shaped tapered portion that is continuous with the fuel passage 44a.
- a space 47 surrounded by the relief valve holder 42, the relief valve 43 and the flange 46 is formed in the vicinity of the valve contact portion 44b of the flange 46.
- a space 48 is formed between the annular groove portion 45 and the second chamber 1b. The annular groove portion 45 and the space 48 are provided at a position farther from the plunger 2 than the valve contact portion 44b.
- the fuel in the pressurization chamber 11 is decompressed by the descent of the plunger 2 . This decompression of the fuel starts from the innermost part of the pressurization chamber 11 which is farthest from the plunger 2 . That is, the fuel in the pressurization chamber 11 is pulled from the innermost portion when the pressure is reduced. Therefore, cavitation can be preferentially generated in the space 48 . This can prevent cavitation from occurring in the space 47 near the valve contact portion 44b.
- a gap 61 a is formed between the flange portion 46 and the relief valve holder 42 .
- the area of the peripheral surface of the gap 61a that faces the second chamber 1b is the area of the opening that communicates the space 47 generated near the valve contact portion 44b with the plunger 2 side of the pressurization chamber 11 .
- the area of the peripheral surface of the gap 61a will be referred to as the "opening area of the gap 61a".
- a gap 61b is formed between the outer peripheral surface 46a of the flange portion 46 and the inner peripheral surface of the second chamber 1b.
- the area of the surface of the gap 61b perpendicular to the center line of the second chamber 1b is the area of the opening that communicates the space 48 and the pressurizing chamber 11 on the side of the plunger 2 .
- the area of the surface of the gap 61b perpendicular to the center line of the second chamber 1b will be referred to as the "opening area of the gap 61b".
- the opening area of the gap 61b is set to be larger than the opening area of the gap 61a. Increasing the opening area reduces the pressure loss. A pressure change occurs preferentially in a portion with a small pressure loss over a portion with a large pressure loss. That is, the pressure change occurs preferentially in the gap 61b than in the gap 61a.
- the opening area of the gap 61b is preferably set to, for example, 1.25 times or more the opening area of the gap 61a.
- the volume of the space 48 formed by the annular groove portion 45 is larger than the volume of the space 47 generated near the valve contact portion 44b. As a result, locations where cavitation occurs in the space 48 can be dispersed. As a result, the occurrence and collapse of cavitation are prevented from being repeated at the same place, and the number of occurrences of cavitation erosion in the annular groove portion 45 can be suppressed.
- the gap 61b is set to a size that does not allow foreign matter separated from the annular groove 45 due to cavitation erosion to pass through. That is, the gap 61b is preferably determined according to the size of the foreign matter that is not desired to flow from the space 48 toward the plunger 2 side of the pressurizing chamber 11 .
- the gap 61b is preferably set to 0.2 mm or less, for example. As a result, it is possible to prevent foreign matter larger than 0.2 mm from flowing into the pressurizing chamber 11 on the side of the plunger 2 . As a result, deterioration of the seat performance of the relief valve 43 can be suppressed, and the quality of the high-pressure fuel supply pump 100 can be improved.
- the distance from the second chamber 1b (pump body 1) to the valve contact portion 44b in the direction orthogonal to the center line of the second chamber 1b (moving direction of the relief valve 43) is defined as a distance 62a. Also, in the direction parallel to the center line of the second chamber 1b, the distance from the end face of the flange 46 of the seat member 44 to the end of the annular groove 45 opposite to the flange 46 is defined as a distance 62b.
- the fuel in the pressurization chamber 11 is decompressed by the descent of the plunger 2 . This decompression of the fuel starts from the innermost part of the pressurization chamber 11 which is farthest from the plunger 2 . Therefore, the distance 62b is set longer than the distance 62a. As a result, the fuel in the space 48 formed by the annular groove portion 45 begins to decompress earlier than the fuel in the space 47 . As a result, cavitation can be actively generated in the space 48 .
- the relief valve mechanism 4 is arranged in the pressurizing chamber 11 at the furthest position from the plunger 2 . Therefore, cavitation occurs in the relief valve mechanism 4 .
- the suction valve mechanism or the discharge valve mechanism is arranged at the farthest position from the plunger in the pressurization chamber, cavitation occurs in the suction valve mechanism or the discharge valve mechanism.
- a space similar to the space 48 according to this embodiment may be provided in the intake valve mechanism or the discharge valve mechanism.
- the high-pressure fuel supply pump 100 (fuel pump) of the above-described embodiment includes the reciprocating plunger 2, the pressurizing chamber 11 whose volume increases and decreases due to the reciprocating motion of the plunger 2, and the pressurizing chamber 11. and a relief valve mechanism 4 for returning fuel to the chamber 11 .
- the relief valve mechanism 4 includes a relief valve 43 and a seat member 44 having a valve contact portion 44b on which the relief valve 43 is seated.
- the relief valve 43 is arranged closer to the plunger 2 than the seat member 44 is.
- the sheet member 44 has an annular groove 45 forming a space 48 communicating with the pressure chamber 11 between the second chamber 1 b (fixed portion) surrounding the outer peripheral surface of the sheet member 44 .
- the space 48 is provided at a position farther from the plunger 2 than the valve contact portion 44b. Thereby, cavitation can be preferentially generated in the space 48 . As a result, it is possible to prevent cavitation from occurring in the space 47 near the valve contact portion 44b.
- the relief valve mechanism 4 of the high-pressure fuel supply pump 100 (fuel pump) according to the embodiment described above includes a relief valve holder 42 that holds the relief valve 43 .
- the area of the opening that communicates the space 48 with the plunger 2 side of the pressurizing chamber 11 (the opening area of the gap 61b) is the area of the opening that communicates the space 47 with the plunger 2 side of the pressurizing chamber 11 (the opening area of the gap 61a).
- the opening (gap 61b) that communicates the space 48 and the plunger 2 side of the pressurizing chamber 11 preferentially changes pressure over the opening (gap 61a) that communicates the plunger 2 side of the space 47 and the pressurizing chamber 11. occurs.
- cavitation can be generated more in the space 48 than in the space 47 .
- the volume of the space 48 of the relief valve mechanism 4 according to the embodiment described above is larger than the volume of the space 47 (valve contact portion side space).
- the seat member 44 of the relief valve mechanism 4 has a collar portion 46 facing the relief valve holder 42 .
- the collar portion 46 forms an opening that communicates the space 48 and the plunger 2 side of the pressurizing chamber 11 .
- the gap between the outer peripheral surface 46a of the flange portion 46 and the second chamber 1b (fixed portion) according to the embodiment described above is 0.2 mm or less. As a result, it is possible to prevent foreign matter larger than 0.2 mm from flowing into the pressurizing chamber 11 on the side of the plunger 2 . As a result, deterioration of the seat performance of the relief valve 43 can be suppressed, and the quality of the high-pressure fuel supply pump 100 can be improved.
- the end of the annular groove portion 45 on the side opposite to the relief valve holder 42 side. portion (distance 62b) is longer than the distance (distance 62a) from the second chamber 1b (fixed portion) to the valve contact portion 44b in the direction orthogonal to the movement direction of the relief valve 43.
- the fuel in the space 48 formed by the annular groove portion 45 begins to decompress earlier than the fuel in the space 47 .
- cavitation can be actively generated in the space 48 .
- the seat member 44 of the relief valve mechanism 4 is fixed to the second chamber 1 b of the pump body 1 .
- the relief valve mechanism 4 may be configured to provide a housing that integrally incorporates the relief spring, relief valve holder, relief valve, and seat member.
- the relief valve mechanism is fixed to the body of the high-pressure fuel supply pump as one assembled component.
- a space for preferentially generating cavitation is formed between the housing and the sheet member. This facilitates the assembly work of the relief valve mechanism.
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Abstract
Description
ハウジングは、プランジャを摺動自在に保持するシリンダライナを収容するとともに加圧室を形成する段付きの筒型状の空間であるシリンダを有している。吸入弁は、電磁ソレノイドに電流を供給しない状態で開弁し、電磁ソレノイドに電流を供給すると、開弁して加圧室に燃料を吸入する。
なお、上述した以外の課題、構成および効果は、以下の実施形態の説明により明らかにされる。
以下、本発明の一実施形態に係る高圧燃料供給ポンプについて説明する。なお、各図において共通の部材には、同一の符号を付している。
まず、本実施形態に係る高圧燃料供給ポンプ(燃料ポンプ)を用いた燃料供給システムについて、図1を用いて説明する。
図1は、本実施形態に係る高圧燃料供給ポンプを用いた燃料供給システムの全体構成図である。
次に、高圧燃料供給ポンプ100の構成について、図2~図6を用いて説明する。
図2は、高圧燃料供給ポンプ100の水平方向に直交する断面で見た縦断面図(その1)である。図3は、高圧燃料供給ポンプ100の水平方向に直交する断面で見た縦断面図(その2)である。図4は、高圧燃料供給ポンプ100の垂直方向に直交する断面で見た水平方向断面図である。図5は、高圧燃料供給ポンプ100の水平方向に直交する断面で見た縦断面図(その3)である。図6は、リリーフ弁機構4を拡大して示す説明図である。
すなわち、プランジャ2は、加圧室11の容積を拡大及び縮小させる方向に往復動するように配置されている。
次に、本実施形態に係る高圧燃料ポンプの動作について、図2、図4を用いて説明する。
次に、本実施形態に係るリリーフ弁機構4のシート部材44について、図6及び図7を用いて説明する。
図7は、リリーフ弁機構4周辺のキャビテーション発生位置を示す説明図である。
この場合は、吸入弁機構又は吐出弁機構において、本実施形態に係る空間48と同様の空間を設けてもよい。
以上説明したように、上述した実施形態の高圧燃料供給ポンプ100(燃料ポンプ)は、往復運動するプランジャ2と、プランジャ2の往復運動により容積が増減する加圧室11と、加圧室11に燃料を戻すリリーフ弁機構4とを有する。リリーフ弁機構4は、リリーフ弁43と、リリーフ弁43が着座する弁接触部44bを有するシート部材44とを備える。リリーフ弁43は、シート部材44よりもプランジャ2側に配置される。シート部材44は、シート部材44の外周面を囲う第2室1b(固定部)との間に加圧室11に連通する空間48を形成する環状溝部45を有する。空間48は、弁接触部44bよりもプランジャ2から遠い位置に設けられる。これにより、空間48において優先的にキャビテーションを発生させることができる。その結果、弁接触部44b付近の空間47においてキャビテーションが発生することを防止することができる。
15…リテーナ、 17…シールホルダ、 17a…副室、 18…プランジャシール、 30…吸入弁室、 42…リリーフ弁ホルダ、 43…リリーフ弁、 44…シート部材、 44a…燃料通路、 44b…弁接触部、 45…環状溝部、 46…鍔部、 46a…外周面、 47,48…空間、 51…低圧燃料吸入口、 52…吸入流路、 53…吸入フィルタ、 61a,61b…隙間、 62a,62b…距離、 100…高圧燃料供給ポンプ、 101…ECU、 102…フィードポンプ、 103…燃料タンク、 104…低圧配管、 105…燃料圧力センサ、 106…コモンレール、 107…インジェクタ
Claims (9)
- 往復運動するプランジャと、プランジャの往復運動により容積が増減する加圧室と、前記加圧室に燃料を戻すリリーフ弁機構と、を有する燃料ポンプであって、
前記リリーフ弁機構は、
リリーフ弁と、
前記リリーフ弁が着座する弁接触部を有するシート部材と、を備え、
前記リリーフ弁は、前記シート部材よりも前記プランジャ側に配置され、
前記シート部材は、前記シート部材の外周面を囲う固定部との間に前記加圧室に連通する空間を形成する環状溝部を有し、
前記空間は、前記弁接触部よりも前記プランジャから遠い位置に設けられる
燃料ポンプ。 - 前記リリーフ弁機構は、前記リリーフ弁を保持するリリーフ弁ホルダを備え、
前記リリーフ弁、前記リリーフ弁ホルダ及び前記シート部材によって囲まれた弁接触部側空間が形成されており、
前記空間と前記加圧室の前記プランジャ側を連通する開口の面積は、前記弁接触部側空間と前記加圧室の前記プランジャ側を連通する開口の面積よりも大きい
請求項1に記載の燃料ポンプ。 - 前記空間の体積は、前記弁接触部側空間の体積よりも大きい
請求項2に記載の燃料ポンプ。 - 前記シート部材は、前記リリーフ弁ホルダに対向する鍔部を有し、
前記鍔部は、前記空間と前記加圧室の前記プランジャ側を連通する開口を形成する
請求項2に記載の燃料ポンプ。 - 前記鍔部の外周面と前記固定部との間の隙間は、0.2mm以下である
請求項4に記載の燃料ポンプ。 - 前記リリーフ弁の移動方向において、前記シート部材の前記リリーフ弁ホルダに対向する端面から前記環状溝部の前記リリーフ弁ホルダ側と反対側の端部までの距離は、前記リリーフ弁の移動方向に直交する方向において、前記固定部から前記弁接触部までの距離よりも長い
請求項2に記載の燃料ポンプ。 - 前記固定部は、前記プランジャが挿入されるボディである
請求項1に記載の燃料ポンプ。 - 前記リリーフ弁機構は、前記リリーフ弁と前記シート部材を一体的に組み込むハウジングを備え、
前記固定部は、前記ハウジングである
請求項1に記載の燃料ポンプ。 - 往復運動するプランジャと、プランジャの往復運動により容積が増減する加圧室と、前記加圧室に連通する弁機構と、を有する燃料ポンプであって、
前記弁機構は、
弁と、
前記弁が着座する弁接触部を有するシート部材と、を備え、
前記弁は、前記シート部材よりも前記プランジャ側に配置され、
前記シート部材は、前記シート部材の外周面を囲う固定部との間に前記加圧室に連通する空間を形成する環状溝部を有し、
前記空間は、前記弁接触部よりも前記プランジャから遠い位置に設けられる
燃料ポンプ。
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EP22863843.3A EP4286718A1 (en) | 2021-09-03 | 2022-02-02 | Fuel pump |
US18/281,030 US20240151198A1 (en) | 2021-09-03 | 2022-02-02 | Fuel Pump |
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- 2022-02-02 WO PCT/JP2022/004023 patent/WO2023032253A1/ja active Application Filing
- 2022-02-02 EP EP22863843.3A patent/EP4286718A1/en active Pending
- 2022-02-02 CN CN202280019544.5A patent/CN116964317A/zh active Pending
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EP4286718A1 (en) | 2023-12-06 |
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