WO2013128958A1 - 電磁駆動型の吸入弁を備えた高圧燃料供給ポンプ - Google Patents
電磁駆動型の吸入弁を備えた高圧燃料供給ポンプ Download PDFInfo
- Publication number
- WO2013128958A1 WO2013128958A1 PCT/JP2013/050504 JP2013050504W WO2013128958A1 WO 2013128958 A1 WO2013128958 A1 WO 2013128958A1 JP 2013050504 W JP2013050504 W JP 2013050504W WO 2013128958 A1 WO2013128958 A1 WO 2013128958A1
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- WO
- WIPO (PCT)
- Prior art keywords
- valve
- fuel supply
- supply pump
- pressure fuel
- valve member
- Prior art date
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- 239000000446 fuel Substances 0.000 title claims abstract description 110
- 230000007246 mechanism Effects 0.000 claims abstract description 42
- 230000001012 protector Effects 0.000 claims abstract description 38
- 230000006835 compression Effects 0.000 claims description 8
- 238000007906 compression Methods 0.000 claims description 8
- 239000012530 fluid Substances 0.000 abstract description 31
- 238000000034 method Methods 0.000 description 12
- 238000003466 welding Methods 0.000 description 9
- 230000001105 regulatory effect Effects 0.000 description 8
- 239000002184 metal Substances 0.000 description 6
- 230000002093 peripheral effect Effects 0.000 description 6
- 238000002788 crimping Methods 0.000 description 5
- 230000004907 flux Effects 0.000 description 5
- 238000006073 displacement reaction Methods 0.000 description 4
- 238000002485 combustion reaction Methods 0.000 description 3
- 230000007423 decrease Effects 0.000 description 3
- 230000001276 controlling effect Effects 0.000 description 2
- 239000002828 fuel tank Substances 0.000 description 2
- 239000000696 magnetic material Substances 0.000 description 2
- 239000010705 motor oil Substances 0.000 description 2
- 230000010349 pulsation Effects 0.000 description 2
- 230000001174 ascending effect Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 230000003111 delayed effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 230000005389 magnetism Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Images
Classifications
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- 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
- F02M51/00—Fuel-injection apparatus characterised by being operated electrically
- F02M51/04—Pumps peculiar thereto
-
- 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
-
- 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
- F02M51/00—Fuel-injection apparatus characterised by being operated electrically
-
- 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
- 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
- F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
-
- 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
-
- 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
- F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
-
- 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
- F04B1/0439—Supporting or guiding means for the 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
- 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
- F04B1/0452—Distribution members, e.g. valves
- F04B1/0456—Cylindrical
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
- F04B53/108—Valves characterised by the material
- F04B53/1082—Valves characterised by the material magnetic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B7/00—Piston machines or pumps characterised by having positively-driven valving
- F04B7/0076—Piston machines or pumps characterised by having positively-driven valving the members being actuated by electro-magnetic means
Definitions
- the present invention relates to a high-pressure fuel supply pump for use in an in-cylinder injection internal combustion engine, and relates to a high-pressure fuel supply pump having an electromagnetically driven intake valve mechanism, and in particular, the electromagnetically driven intake valve mechanism is a valve member.
- the present invention relates to a high-pressure fuel supply pump having an electromagnetically driven intake valve mechanism that is a so-called normally closed type in which a plunger rod is integrated and a spring that biases the plunger rod biases a valve member in a valve closing direction.
- a movable plunger which is operated by an electromagnetic force, has a valve member at the tip of the electromagnetically driven intake valve mechanism.
- a regulating member that regulates the displacement of this plunger at a specific position
- a spring member that biases the movable plunger to the opposite side of the regulating member
- the fluid differential pressure above and below the valve seat is due to electromagnetic force
- It is configured to assist the movement of the movable plunger by acting in the same direction as the movement of the movable plunger, and after the movable plunger makes a specific displacement in the direction of the regulating member due to the fluid differential pressure, an electromagnetic force is applied to the plunger. It is configured.
- the electromagnetically driven suction valve mechanism configured in this way is changed from a suction process in which the piston plunger of the pump is directed from the top dead center position to the bottom dead center position, and conversely, a discharge process from the bottom dead center position to the top dead center position. Then, the fuel once sucked into the pressurizing chamber during the suction process is discharged from the inlet opening of the pressurizing chamber to the valve member side, and passes through the fuel passage around the valve member and between the valve seat and the valve member. Then, the fuel outlet of the electromagnetic drive mechanism flows backward to spill into the low pressure fuel chamber of the electromagnetic drive mechanism.
- valve member of the suction valve is spring-loaded via the plunger of the electromagnetic drive mechanism while the electromagnetic drive mechanism is not energized. It is urged in the valve opening direction by force to leave the valve seat and is held in the valve opening position.
- the suction valve and the fluid passage so that the fluid force (dynamic pressure) of the fuel flow overflowing through the fluid passage does not act on the back surface of the suction valve arranged in the fluid passage between the suction port and the pressurizing chamber.
- An isolation member is provided for isolating the gap between the two.
- a pressurizing chamber for pressurizing a fluid is provided, and the suction port is located on the pressurizing chamber side of the suction port so as to open and close the suction port formed at the inlet of the pressurization chamber, and the suction port is closed by a spring.
- a high-pressure fuel pump provided with a separating member in a fluid passage between a pressurizing chamber and a suction port and separating a rear portion of the suction valve from the fluid passage.
- the fluid force of the fuel flow flowing backward from the pressurizing chamber acts on the surface of the valve member on the pressurizing chamber side, and the valve member that is being opened is closed. Energize in the direction.
- the electromagnetic drive mechanism becomes larger and the electromagnetic drive mechanism becomes larger in order to maintain the valve opening state without being affected by this fluid force. It was. In other words, if the fluid force in the valve closing direction acting on the valve member becomes stronger than the magnetic attractive force at an unexpected timing, the valve member comes into contact with the intake valve seat, and the valve is closed. This is the same as the problem that the flow rate cannot be controlled smoothly and the problem that the holding current following the starting current of the electromagnetic drive mechanism cannot be reduced.
- An object of the present invention is an electromagnetic drive in which an electromagnetically driven suction valve mechanism is a so-called normally closed type in which a valve member and a plunger rod are integrated, and a spring that biases the plunger rod biases the valve member in the valve closing direction.
- the present invention comprises a valve member having a seat surface that comes into contact with the suction valve seat, and a plunger rod that is positioned on the seat surface side of the valve member and operates the valve member with a magnetic attraction force,
- the plunger rod makes a full stroke in the valve opening direction and the plunger rod drive anchor contacts the stopper, the valve is formed with a minimum gap between the valve member and the surface opposite to the seat surface.
- the protector which suppresses that fluid pressure acts on the surface on the opposite side to the seat surface of a valve member from the fluid pressure which acts on the surface on the opposite side to the seat surface of a member was provided.
- the fluid force in the valve closing direction generated in the valve member by the fluid flowing through the valve member can be reduced, that is, the magnetism generated in the direction in which the valve member maintains the valve open state away from the intake valve seat.
- the fluid force can be kept smaller than the suction force. Further, since the protector and the suction valve member do not come into contact with each other, the generation of sound does not increase. Therefore, it is possible to obtain a high-pressure fuel supply pump that can accurately control the flow rate even when the capacity is increased and that generates less noise.
- 1 is a longitudinal sectional view of a high-pressure fuel supply pump having an electromagnetically driven intake valve according to a first embodiment in which the present invention is implemented. It is an enlarged view of the high pressure fuel supply pump provided with the electromagnetically driven suction valve according to the first embodiment in which the present invention is implemented, and shows a state where the electromagnetic coil is not energized. It is an enlarged view of the high pressure fuel supply pump provided with the electromagnetically driven suction valve according to the first embodiment in which the present invention is implemented, and shows a state where the electromagnetic coil is energized.
- 1 is a perspective view of a high-pressure fuel supply pump provided with an electromagnetically driven intake valve according to a first embodiment in which the present invention is implemented, and shows a state in which an electromagnetic coil is not energized.
- 1 is a perspective view of a high-pressure fuel supply pump including an electromagnetically driven intake valve according to a first embodiment in which the present invention is implemented, and shows a state where an electromagnetic coil is energized.
- 1 shows a state before a high-pressure fuel supply pump having an electromagnetically driven suction valve according to a first embodiment in which the present invention is implemented is assembled into a pump housing 1. It is a time chart for demonstrating a motion of the high pressure fuel supply pump provided with the electromagnetically driven suction valve by the 1st Example by which this invention was implemented.
- the electromagnetically driven suction valve mechanism of the high-pressure fuel supply pump of the present embodiment is configured as follows.
- valve member 31a and the plunger rod 31b are integrated, and a spring 34 that biases the plunger rod 31b is a so-called normal close type that biases the valve member 31a in the valve closing direction.
- This electromagnetically driven suction valve mechanism has a plunger rod 31 b that is operated by electromagnetic force generated by the electromagnetic coil 53.
- the anchor 35 fixed to the anchor fixing portion 31 c of the plunger rod 31 b is attracted to the fixed core 33 by electromagnetic force and collides with the end surface of the fixed core 33.
- the fixed core 33 functions as a regulating member that regulates the displacement of the plunger rod 31b at a specific position.
- the spring 34 is held between a spring stopper 34a fixed to the plunger rod 31b and the suction valve seat housing 32, and biases the plunger rod 31b to the side away from the regulating member (fixed core 33).
- the fluid pressure difference between the upstream and downstream of the valve member 31a acts to bias the valve member 31a in the valve opening direction, and counteracts the biasing force of the spring 34.
- the electromagnetic force opposes the acting force of the spring 34 that urges the valve plunger rod 31b toward the side away from the regulating member (fixed core 33), and synchronizes with the acting force due to the fluid differential pressure that urges the valve member 31a in the valve opening direction. Then, the valve member 31a is urged in the valve opening direction, or the valve member 31a is maintained in the valve open state.
- valve member 31a and the plunger rod 31b press and contract the spring 34 by the fluid differential pressure, and a specific displacement (full opening in the embodiment) in the direction of the regulating member (fixed core 33), that is, the valve opening direction of the valve member 31a.
- the electromagnetic coil 53 is energized to apply an electromagnetic force to the anchor 35 of the plunger rod 31b, and the anchor 35 is maintained in contact with the fixed core 33. ing.
- the electromagnetically driven suction valve mechanism configured in this way is from the suction process in which the piston plunger 2 of the high pressure fuel supply pump is directed from the top dead center position to the bottom dead center position, and conversely from the bottom dead center position to the top dead center position.
- the discharge process is started, the fuel once sucked into the pressurizing chamber 11 during the suction process is discharged from the inlet opening (also spill opening) 11A of the pressurizing chamber 11 to the valve member 31a side.
- the fuel flows back through the fuel outlet passage of the electromagnetically driven intake valve mechanism 30 that is formed around the valve member 31a and between the intake valve seat portion 32a and the valve member 31a. Spills into the suction port 30a of the mechanism 30.
- the plunger driving anchor 35 fixed to the magnet contacts the magnetic attraction portion 33a of the fixed core 33 as a stopper and as a regulating member, and the plunger rod 31b makes a full stroke in the opening direction of the valve member 31a, the valve member 31a Of the valve member 31a and a surface 31B of the valve member 31a opposite to the seat surface 31A.
- the protector 39 includes a protector 39 as a wall member having a flat plate portion 39b facing the surface opposite to the seat surface 31A. It is provided between the entrance opening (also spill opening) 11A of the pressurizing chamber 11.
- the gap GA between the valve member 31a and the protector 39 is always larger than the gap GB between the anchor 35 as a mover and the magnetic attraction portion 33a of the fixed core 33 as a stopper and as a restricting member.
- the valve member 31a At the maximum compression position of the spring 34 that biases the plunger rod 31b in the valve closing direction of the valve member 31a, the valve member 31a reaches the fully open position, and at that time, the distance GA between the valve member 31a and the protector 39 is not zero. become. That is, in the state where a wall surface member having a flat disk-shaped portion facing the end surface portion opposite to the valve seat 32a side of the valve member 31a is provided and the valve member is fully stroked in the valve opening direction, A thin layer of fuel is interposed between the end surface portion and the protector 39 as a wall surface portion having a flat disk-shaped portion so as not to contact each other.
- the anchor 35 serving as a mover and the magnetic attraction portion 33a of the fixed core 33 serving as a stopper and as a restricting member are collided. To alleviate the impact. Thereby, a collision sound can be reduced.
- the protector 39 is fixed by press-fitting to a distal end outer peripheral press-fitting portion 32b of a suction valve seat housing 32 as a member in which the suction valve seat portion 32a is formed.
- the outer peripheral surface 39d of the protector 39 and the outer peripheral surface of the suction valve seat housing 32 as a member on which the suction valve seat portion 32a is formed are separately fixed to the pump housing 1 by press fitting.
- FIG. 1 a portion surrounded by a broken line indicates a pump housing 1 of the high-pressure pump, and mechanisms and components shown in the broken line indicate that they are integrated into the pump housing 1 of the high-pressure pump. .
- the fuel in the fuel tank 20 is pumped up by the feed pump 21 based on a signal from an engine control unit 27 (hereinafter referred to as ECU), pressurized to an appropriate feed pressure, and passed through the suction pipe 28 to the suction port 10a of the high-pressure fuel supply pump. Sent to.
- ECU engine control unit 27
- the fuel that has passed through the suction port 10a passes through a filter 102 fixed in the suction joint 101, and further, an electromagnetically driven type that constitutes a variable capacity mechanism via the suction flow path 10b, the metal diaphragm damper 9, and the suction flow path 10c.
- an electromagnetically driven type that constitutes a variable capacity mechanism via the suction flow path 10b, the metal diaphragm damper 9, and the suction flow path 10c.
- the suction filter 102 in the suction joint 101 serves to prevent foreign matter existing between the fuel tank 20 and the suction port 10a from being absorbed into the high-pressure fuel supply pump by the flow of fuel.
- the pump housing 1 is formed with a recess 1A as a pressurizing chamber 11 in the center, and a hole 11B for mounting the discharge valve mechanism 8 is formed so as to open to the pressurizing chamber 11.
- a discharge valve mechanism 8 is provided at the outlet of the pressurizing chamber 11.
- the discharge valve mechanism 8 includes a sheet member (sheet member) 8a, a discharge valve 8b, a discharge valve spring 8c, and a holding member 8d as a discharge valve stopper.
- the discharge valve mechanism 8 is formed by welding a welded portion 8e outside the pump housing 1. Assemble mechanism 8. Thereafter, the discharge valve mechanism 8 assembled from the left side in the figure is press-fitted and fixed to the pump housing 1.
- the press-fitting unit also has a function of blocking the pressurizing chamber 11 and the discharge port 12.
- the discharge valve 8b In a state where there is no differential pressure of fuel between the pressurizing chamber 11 and the discharge port 12, the discharge valve 8b is pressed against the seat member 8a by the urging force of the discharge valve spring 8c and is closed. Only when the fuel pressure in the pressurizing chamber 11 becomes larger than the fuel pressure in the discharge port 12 by a predetermined value, the discharge valve 8b is opened against the discharge valve spring 8c, and the pressure in the pressurizing chamber 11 is increased. The fuel is discharged to the common rail 23 through the discharge port 12.
- the discharge valve 8b When the discharge valve 8b is opened, it comes into contact with the holding member 8d and its operation is restricted. Therefore, the stroke of the discharge valve 8b is appropriately determined by the holding member 8d. If the stroke is too large, the fuel discharged to the fuel discharge port 12 will flow back into the pressurizing chamber 11 again due to the delay in closing the discharge valve 8b, and the efficiency of the high-pressure pump will decrease. . Further, when the discharge valve 8b repeats opening and closing movements, the holding member 8d guides the discharge valve 8b to move only in the stroke direction. By configuring as described above, the discharge valve mechanism 8 becomes a check valve that restricts the flow direction of fuel.
- the outer periphery of the cylinder 6 is held by a cylindrical fitting portion 7 a of the cylinder holder 7.
- the cylinder 6 is fixed to the pump housing 1 by screwing a screw 7 g threaded on the outer periphery of the cylinder holder 7 into a screw 1 b threaded on the pump housing 1.
- the plunger seal 13 is held at the lower end of the cylinder holder 7 by the seal holder 13A and the cylinder holder 7 that are press-fitted and fixed to the inner peripheral cylindrical surface 7c of the cylinder holder 7. At this time, the plunger seal 13 is held by the inner peripheral cylindrical surface 7c of the cylinder holder 7 so that its axis is coaxial with the axis of the cylindrical fitting portion 7a.
- the piston plunger 2 and the plunger seal 13 are installed in a slidable contact state at the lower end of the cylinder 6 in the figure.
- the cylinder holder 7 is provided with an outer peripheral cylindrical surface 7b, in which a groove 7d for fitting the O-ring 61 is provided.
- the O-ring 61 shuts off the engine cam side and the outside by the inner wall of the engine-side fitting hole 70 and the groove 7d of the cylinder holder 7 to prevent the engine oil from leaking to the outside.
- the cylinder 6 has a crimping part 6 a that intersects the reciprocating direction of the piston plunger 2, and the crimping part 6 a is crimped to the crimping surface 1 a of the pump housing 1. Crimping is performed by thrust generated by screw tightening.
- the pressurizing chamber 11 is formed by this pressure bonding, so that even if the fuel in the pressure chamber 11 is pressurized and becomes high pressure, the screw is not leaked from the pressure chamber 11 through the pressure bonding portion. Tightening torque must be managed.
- a clearance 1 ⁇ / b> B is provided between the outer periphery of the cylinder 6 and the inner periphery of the pump housing 1 on the pressure chamber 11 side from the crimping portion 6 a of the cylinder 6. Since the outer periphery of the cylinder 6 is held by the cylindrical fitting portion 7a of the cylinder holder 7, the clearance 1B is provided so that the outer periphery of the cylinder 6 and the inner periphery of the pump housing 1 do not come into contact with each other. it can.
- the cylinder 6 holds the piston plunger 2 that moves forward and backward in the pressurizing chamber 11 so as to be slidable along the forward and backward movement direction.
- a tappet 3 that converts the rotational movement of the cam 5 attached to the camshaft of the engine into a vertical movement and transmits it to the piston plunger 2.
- the piston plunger 2 is pressed against the tappet 3 by a spring 4 via a retainer 15.
- the retainer 15 is fixed to the piston plunger 2 by press-fitting. Thereby, the piston plunger 2 can be moved up and down (reciprocating) in accordance with the rotational movement of the cam 5.
- the suction flow path 10c is connected to the seal chamber 10f via a passage (not shown), and the seal chamber 10f is always connected to the pressure of the intake fuel.
- the fuel in the pressurizing chamber 11 is pressurized to a high pressure, a small amount of high-pressure fuel flows into the seal chamber 10f through the sliding clearance between the cylinder 6 and the piston plunger 2, but the inflowed high-pressure fuel is released to the suction pressure. Therefore, the plunger seal 13 is not damaged by the high pressure.
- the piston plunger 2 includes a large-diameter portion 2 a that slides with the cylinder 6 and a small-diameter portion 2 b that slides with the plunger seal 13.
- the diameter of the large diameter portion 2a is set larger than the diameter of the small diameter portion 2b, and is set coaxially with each other.
- the sliding part with the cylinder 6 is the large diameter part 2a
- the sliding part with the plunger seal 13 is the small diameter part 2b.
- the metal diaphragm damper 9 is composed of two metal diaphragms, and the outer periphery is fixed to each other by welding at the welded portion in a state where gas is sealed in the space between both diaphragms.
- the metal diaphragm damper 9 changes its volume, thereby reducing the low pressure pulsation.
- the high pressure fuel supply pump is fixed to the engine by the flange 41, the set screw 42, and the bush 43.
- the flange 41 is welded to the pump housing 1 by welding at a welded portion 41a. In this embodiment, laser welding is used.
- the pump housing 1 is formed with a recess 1A as a pressurizing chamber 11 in the center, and a hole 30A for mounting an electromagnetically driven suction valve mechanism 30 is formed so as to open the pressurizing chamber 11. Yes.
- the intake valve seat housing 32 includes an intake valve seat portion 32a, a press-fit portion 32b, a suction passage portion 32c, a fuel communication passage 32d, a press-fit portion 32e, and a sliding portion 32f.
- the press-fit portion 32 e is press-fitted and fixed to the fixed core 33.
- the intake valve seat portion 32a is press-fitted into the protector 39 at the press-fit portion 32b.
- the protector 39 includes an opening 39a, a protector 39b, a fixed arm 39c, and a press-fit portion 39d.
- the press-fitting part 39d is press-fitted and fixed to the pump housing 1, and the pressurization chamber 11 and the suction port 30a are completely blocked by the press-fitting part 32b and the press-fitting part 39d.
- the fixed core 33 is welded and fixed to the pump housing 1 by a welding portion 33c, and shuts off the suction port 30a and the outside of the high-pressure fuel supply pump.
- the inner yoke 36 is fixed to the fixed core 33 via a seal ring 37.
- the fixed core 33 and the seal ring 37 are welded and fixed by a welded portion 37a, and the inner yoke 36 and the seal ring 37 are welded and fixed by a welded portion 37b. Thereby, the inside and the outside of the fixed core 33 and the inner yoke 36 are completely cut off.
- the guide 38 includes an opening 38a, a sliding portion 38b, and a press-fit portion 38c, and is press-fitted and fixed inside the inner yoke 36 by the press-fit portion 38c.
- the valve-plunger unit 31 is composed of three parts: a valve member 31a, a plunger rod 31b, and an anchor fixing part 31c, and constitutes a suction valve part.
- An anchor 35 is welded and fixed to the anchor fixing portion 31c by a welding portion 35b.
- the spring stopper 34a is press-fitted and fixed to the plunger rod 31b of the valve-plunger unit 31, and the spring 34 is held between the spring stopper 34a and the end face of the intake valve seat housing 32 as shown in the figure.
- valve-plunger unit 31 the anchor 35, and the spring stopper 34a are integrated.
- the plunger rod 31b of the valve-plunger unit 31 is inserted into the inner periphery of the sliding portion 32f of the intake valve seat housing 32 and the sliding portion 38b of the guide 38, and there is a sliding clearance (clearance) between them. . Therefore, the valve-plunger unit 31, the anchor 35, and the spring stopper 34a are integrally movable in the left-right direction in FIG. 2, FIG. 3, and FIG. There is a gap (clearance) between the anchor 35 and the inner yoke 36, and the two members do not contact each other.
- the urging force generated by the spring 34 is generated in a direction in which the anchor 35 and the fixed core 33 are pulled apart via the spring stopper 34a.
- the outer yoke 51 is press-fitted and fixed to the fixed core 33 by a press-fit portion 51a.
- a small gap (clearance) exists between the outer yoke 51 and the inner yoke 36.
- the welded portions 37a and 37b have no lateral load.
- an electromagnetic coil 53 is provided in the space surrounded by the fixed core 33, the seal ring 37, the inner yoke 36, and the outer yoke 51.
- the coil is connected to a terminal 56 at a connecting portion 55 by a wire 54, and the terminal 56 is connected to an engine control unit (hereinafter referred to as ECU) 27. Accordingly, the electromagnetic coil 53 is loaded with a signal (voltage) from the ECU 27.
- the plunger rod 31b When the electromagnetic coil 53 is not energized and is not energized, and when there is no fluid differential pressure between the suction channel 10c (suction port 30a) and the pressurizing chamber 11, the plunger rod 31b is It will be in the state which moved to right direction in a figure like 3. In this state, the valve member 31a and the suction valve seat portion 32a are in a closed state, and the pressurizing chamber 11 and the suction port 30a are shut off.
- valve member 31a When the piston plunger 2 is in a suction stroke state that is displaced downward in FIG. 2 due to rotation of the cam, the volume of the pressurizing chamber 11 increases and the fuel pressure in the pressurizing chamber 11 decreases. In this process, when the fuel pressure in the pressurizing chamber 11 becomes lower than the pressure in the suction passage 10c (suction port 30a), the valve member 31a has a valve opening force (valve member 31a shown in FIG. Force to displace to the left).
- the valve member 31a is moved by the valve opening force due to the fluid differential pressure so as to overcome the biasing force of the spring 34 and separate from the suction valve seat portion 32a, so that the pressurizing chamber 11 and the suction port 30a communicate with each other.
- the fluid differential pressure is large, the magnetic attraction portion 35a of the anchor 35 comes into contact with the magnetic attraction portion 33a of the fixed core 33, and the valve member 31a stops moving and is completely opened. That is, the magnetic attraction portion 33a of the fixed core 33 functions as a stopper for valve opening movement of the plunger rod 31b, the anchor 35, and the spring stopper 34a that move together.
- valve open state When the valve member 31a is fully open, the valve open state is maintained. On the other hand, when the valve member 31a is not fully opened, the valve member 31a is encouraged to open, the magnetic suction part 35a of the anchor 35 contacts the magnetic suction part 33a of the fixed core 33, and the valve member 31a moves. Is stopped and the valve is completely opened. That is, also in this case, the magnetic attraction portion 33a of the fixed core 33 functions as a stopper for the valve opening movement of the plunger rod 31b, the anchor 35, and the spring stopper 34a that move together.
- the state in which the valve member 31a is separated from the intake valve seat portion 32a that is, the state in which the valve member 31a opens the intake port 32A, is maintained, and fuel is supplied from the intake port 30a to the intake passage portion 32c of the intake valve seat housing 32 and It passes through the suction port 32A and flows into the pressurizing chamber 11 through the gap SG between the valve member 31a and the suction valve seat portion 32a.
- the volume of the pressurizing chamber 11 decreases with the compression movement of the piston plunger 2, but in this state, the fuel once sucked into the pressurizing chamber 11 becomes the gap SG between the valve member 31a and the suction valve seat portion 32a and Since the pressure is returned to the suction flow path 10c (suction port 30a) through the suction port 32A, the pressure in the pressurizing chamber does not increase. This process is called a return process.
- the compression stroke of the piston plunger 2 (the upward stroke from the lower start point to the upper start point) includes a return stroke and a discharge stroke.
- the amount of high-pressure fuel discharged can be controlled by controlling the timing of releasing the energization of the electromagnetic coil 53.
- the ratio of the return stroke is small during the compression stroke, and the ratio of the discharge stroke is large. That is, the amount of fuel returned to the suction channel 10c (suction port 30a) is small, and the amount of fuel discharged at high pressure is large.
- the timing for releasing the input voltage is delayed, the ratio of the return stroke during the compression stroke is large and the ratio of the discharge stroke is small. That is, the amount of fuel returned to the suction channel 10c is large, and the amount of fuel discharged at high pressure is small.
- the timing for releasing the energization of the electromagnetic coil 53 is controlled by a command from the ECU 27.
- the amount of fuel discharged at high pressure can be controlled to an amount required by the internal combustion engine by controlling the timing of releasing the energization of the electromagnetic coil 53.
- the fuel guided to the fuel inlet 10a is pressurized to a high pressure by the reciprocating motion of the piston plunger 2 in the pressurizing chamber 11 of the pump housing 1, and is pumped from the fuel outlet 12 to the common rail 23. .
- the common rail 23 is provided with an injector 24 and a pressure sensor 26.
- the injectors 24 are mounted according to the number of cylinders of the internal combustion engine, and open and close according to the control signal of the ECU 27 to inject fuel into the cylinders.
- the diameter ⁇ d of the flat plate portion 39b of the protector 39 shown in FIG. 5 is set larger than the diameter of the valve member 31a.
- the valve member 31a can be slightly displaced in the diameter direction by the clearance of the sliding portion, etc., but is set so that the valve member 31a does not protrude from the diameter of the flat plate portion 39b of the protector 39 under any conditions. Has been.
- the pressurizing chamber 11 and the suction port 30a communicate with each other through the opening 39a, and the fuel flows through the opening 39a.
- the intake valve seat housing 32 is press-fitted by a press-fit portion 32b, and the protector 39 is press-fitted and fixed to the pump housing 1 by a press-fit portion 39d.
- a disc-shaped flat plate portion 39b at the center of the protector 39 is integrated with an annular press-fit portion 39d by a fixed arm portion 39c.
- the clearance (gap) GA between the disc-shaped flat plate portion 39b at the center of the protector 39 and the valve member 31a is always larger than the clearance (timing gap) GA between the magnetic attraction portion 33a and the magnetic attraction portion 35a. That is, even when the magnetic attraction part 33a and the magnetic attraction part 35a are in contact with each other and the valve member 31a is completely opened, the disk-shaped flat plate part 39b at the center of the protector 39 and the end surface part of the valve member 31a are not in contact with each other. A clear clearance (gap) GA exists.
- the fuel in the pressurizing chamber 11 flows to the suction port 30a through the opening 39a at the inlet of the pressurizing chamber.
- a fluid force is generated in the valve member 31 a in the direction of closing the valve member 31 a, but a part or most of the fluid force is received by the flat plate portion 39 b of the protector 39.
- the sum of the fluid force acting on the valve member 31a and the urging force by the spring 34 becomes smaller than the magnetic attractive force.
- the valve member 31a does not protrude from the diameter of the flat plate portion 39b of the protector 39, this effect is remarkable.
- the magnetic attraction force is strongest when the magnetic attraction part 33a and the magnetic attraction part 35a are in contact. Even when the valve member 31a is completely opened, the magnetic attraction part 33a and the magnetic attraction part 35a are in contact with each other, so that a magnetic attraction force greater than the fluid force can be secured.
- valve closing time the time until the valve member 31a comes into contact with the intake valve seat portion 32a and closes. If the valve closing time is too long, the plunger ascending motion ends before the valve member 31a is completely closed, and the lowering motion is shifted to cause a problem that high-pressure discharge cannot be performed.
- FIG. 7 shows a state before the electromagnetically driven suction valve mechanism 30 is assembled into the pump housing 1.
- the suction valve unit 300 first, units are created for the suction valve unit 300 and the connector unit 500, respectively.
- the press-fit portion 32 b on the outer periphery of the suction valve seat portion 32 a of the suction valve unit 300 is press-fitted and fixed to the inner periphery of the ring-shaped press-fit portion 39 d of the protector 39.
- the protector 9 is press-fitted and fixed to the pump housing 1.
- the welded portion 37c is welded over the entire circumference.
- the welding is laser welding.
- the connector unit 500 is press-fitted and fixed to the fixed core 33. Thereby, the direction of the connector 58 can be freely selected.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Magnetically Actuated Valves (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
図1中で、破線で囲まれた部分が高圧ポンプのポンプハウジング1を示し、この破線の中に示されている機構、部品は高圧ポンプのポンプハウジング1に一体に組み込まれていることを示す。
(2)プロテクタ39の平板部39bと弁部材31aの間のクリアランスがゼロとはならず、弁部材31aの閉弁時間を短くできる。
1a 圧着面
1A 凹所
1B クリアランス
2 ピストンプランジャ
2a 大径部
2b 小径部
3 タペット
4 ばね
5 カム
6 シリンダ
6a 圧着部
7 シリンダホルダ
7a 円筒嵌合部
7c 内周円筒面
7g ねじ
8 吐出弁機構
8a シート部材
8b 吐出弁
8c 吐出弁ばね
8d 保持部材
8e、33c、35b、37a、37b 溶接部
9 金属ダイアフラムダンパ
10a 吸入口
10b、10c 吸入流路
10f シール室
11 加圧室
11A 入り口開口
11B 孔
12 吐出口
13 プランジャシール
15 リテーナ
21 フィードポンプ
30 電磁駆動型の吸入弁機構
30a 吸入ポート
30A 孔
31 弁-プランジャユニット
31a (吸入弁としての)弁部材
31b プランジャロッド
31c アンカー固定部
32 吸入弁シートハウジング
32a 吸入弁シート部
32b、32e、38c、39d、51a 圧入部
32c 吸入通路部
32d 燃料連通路
32f、38b 摺動部
32A 吸込口
33 固定コア
33a、35a 磁気吸引部
34 ばね
34a ばねストッパ
35 アンカー
36 インナーヨーク
37 シールリング
38 ガイド
38a、39a 開口部
39 プロテクタ
39b 平板部
39c 固定腕部
51 アウターヨーク
53 電磁コイル
101 吸入ジョイント
300 吸入弁ユニット
500 コネクタユニット
Claims (12)
- ポンプハウジングに形成された加圧室の入り口開口部に取付けられて、加圧室へ流入し加圧室からスピルする燃料を調整する電磁駆動型の吸入弁を備えた高圧燃料供給ポンプであって、
弁シートに当接するシート面を有する弁部材と、前記弁部材のシート面側に位置し電磁力で前記弁部材を操作するプランジャロッドとを備え、
前記プランジャロッド駆動用のアンカーがストッパに接触し、
前記プランジャロッドが開方向にフルストロークしたとき、前記弁部材の前記シート面とは反対側の面と隙間を隔てて対面するプロテクタを備え、
前記プロテクタは前記弁部材の前記シート面とは反対側の面と前記加圧室の入り口開口との間に設けた
電磁駆動型の吸入弁を備えた高圧燃料供給ポンプ。 - 請求項1の高圧燃料供給ポンプにおいて、
前記弁部材と前記プロテクタとの間の隙間は前記アンカーと前記ストッパとの間の隙間より常に大きい
電磁駆動型の吸入弁を備えた高圧燃料供給ポンプ。 - 請求項1もしくは2に記載の高圧燃料供給ポンプにおいて、
前記プランジャロッドを前記弁部材の閉弁方向に付勢する閉弁用ばねを有し、前記閉弁用ばねの最大圧縮位置において、前記吸入弁が全開位置に到達し、そのとき前記弁部材と前記プロテクタとの間隔がゼロではない最小間隔になる
電磁駆動型の吸入弁を備えた高圧燃料供給ポンプ。 - 請求項1ないし3に記載の高圧燃料供給ポンプにおいて、
前記弁部材と前記プランジャロッドとが一体となっている
電磁駆動型の吸入弁を備えた高圧燃料供給ポンプ。 - 請求項1ないし4に記載の高圧燃料供給ポンプにおいて、
前記プランジャロッドと前記アンカーとが一体となっている
電磁駆動型の吸入弁を備えた高圧燃料供給ポンプ。 - 請求項1ないし5に記載の高圧燃料供給ポンプにおいて、
前記電磁力は、前記弁部材を前記弁シートから離脱する方向(前記弁部材の開弁方向)に発生する
電磁駆動型の吸入弁を備えた高圧燃料供給ポンプ。 - 請求項1ないし6に記載の高圧燃料供給ポンプにおいて、
前記電磁力は前記アンカーと前記ストッパとの間に発生する
電磁駆動型の吸入弁を備えた高圧燃料供給ポンプ。 - 請求項1ないし7に記載の高圧燃料供給ポンプにおいて、
前記プロテクタが、前記弁シートが形成された部材に固定されている
電磁駆動型の吸入弁を備えた高圧燃料供給ポンプ。 - 請求項1ないし7に記載の高圧燃料供給ポンプにおいて、
前記プロテクタと前記弁シートが形成された部材とは別々に前記高圧燃料供給ポンプのポンプハウジング部へ圧入されている
電磁駆動型の吸入弁を備えた高圧燃料供給ポンプ。 - ポンプハウジングに形成された加圧室の入り口開口部に取付けられて、加圧室へ流入し加圧室からスピルする燃料を調整する電磁駆動型の吸入弁を備えた高圧燃料供給ポンプであって、
弁シートに当接するシート面を有する弁部材と、前記弁部材のシート面側に位置し電磁力で前記弁部材を操作するプランジャロッドとを備え、
前記プランジャロッド駆動用のアンカーがストッパに接触し、
前記プランジャロッドに取付けられた前記弁部材の前記弁シート側とは反対側の端面部と対面する平らな円板状部を有する壁面部材を有し、
前記壁面部材は前記弁部材の前記シート面とは反対側の面と前記加圧室の入り口開口との間に設けられており、
前記弁部材が開弁方向にフルストロークした状態において、前記弁部材の端面部と前記壁面部材の前記平らな円板状部とが非接触となるように両者の間に燃料の薄い層が介在するよう構成した
電磁吸入弁を有する高圧燃料供給ポンプ。 - 請求項10に記載の高圧燃料供給ポンプにおいて、
前記プランジャロッドを前記弁部材の閉弁方向に付勢する閉弁用ばねを有し、前記閉弁用ばねの最大圧縮位置において、バルブが全開位置に到達し、そのとき弁部材とプロテクタとの間隔がゼロではない最小間隔になる
電磁吸入弁を有する高圧燃料供給ポンプ。 - 請求項10に記載の高圧燃料供給ポンプにおいて、
電磁力で前記プランジャロッドを電磁力で操作する電磁駆動機構を備え、
前記プランジャロッドに固定された前記電磁駆動機構用のアンカー有し、
前記プランジャロッドがフルストロークしたとき前記アンカーがストッパに接触するよう構成されており、
前記弁部材とプロテクタとの隙間は前記アンカーと前記ストッパとの隙間より常に大きい
電磁吸入弁を有する高圧燃料供給ポンプ。
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CN201380008008.6A CN104093969B (zh) | 2012-02-27 | 2013-01-15 | 具备电磁驱动型的吸入阀的高压燃料供给泵 |
DE112013001157.3T DE112013001157T5 (de) | 2012-02-27 | 2013-01-15 | Hochdruck-Kraftstoffförderpumpe mit einem elektromagnetisch angetriebenen Einlassventil |
US14/374,840 US20150017039A1 (en) | 2012-02-27 | 2013-01-15 | High-pressure fuel supply pump having an electromagnetically-driven inlet valve |
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JP2012039517A JP5975672B2 (ja) | 2012-02-27 | 2012-02-27 | 電磁駆動型の吸入弁を備えた高圧燃料供給ポンプ |
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JP (1) | JP5975672B2 (ja) |
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Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR101581304B1 (ko) * | 2013-12-04 | 2015-12-31 | 주식회사 현대케피코 | 유로 제어 밸브 |
KR101556627B1 (ko) * | 2014-05-21 | 2015-10-02 | 주식회사 현대케피코 | 이중 완충구조를 가지는 내연기관용 고압 펌프 |
KR101556637B1 (ko) | 2014-05-21 | 2015-10-02 | 주식회사 현대케피코 | 댐핑 구조를 가지는 내연기관용 고압 펌프 |
CN104806406B (zh) * | 2015-04-30 | 2018-01-19 | 哈尔滨工程大学 | 常闭型机电复合式高压油泵 |
CN109154264B (zh) * | 2016-05-27 | 2020-12-22 | 日立汽车系统株式会社 | 高压燃料供给泵 |
US11002236B2 (en) | 2016-11-18 | 2021-05-11 | Hitachi Automotive Systems, Ltd. | High-pressure fuel supply pump |
WO2018123323A1 (ja) * | 2016-12-28 | 2018-07-05 | 日立オートモティブシステムズ株式会社 | 電磁吸入弁を備えた高圧燃料供給ポンプ |
JP6692303B2 (ja) * | 2017-01-26 | 2020-05-13 | 日立オートモティブシステムズ株式会社 | 高圧燃料ポンプ |
JP6855893B2 (ja) * | 2017-04-13 | 2021-04-07 | 株式会社デンソー | 電磁弁 |
DE102018211291B4 (de) * | 2018-07-09 | 2021-02-18 | Vitesco Technologies GmbH | Kraftstoffhochdruckpumpe |
WO2020117311A1 (en) * | 2018-12-07 | 2020-06-11 | Stanadyne Llc | Inlet control valve for high pressure fuel pump |
EP3889482B1 (en) * | 2019-02-25 | 2024-04-24 | Hitachi Astemo, Ltd. | Fuel pump |
JP2021005653A (ja) * | 2019-06-26 | 2021-01-14 | パナソニックIpマネジメント株式会社 | 電磁石装置、ショックアブソーバ及び移動体 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2006291838A (ja) * | 2005-04-11 | 2006-10-26 | Hitachi Ltd | 高圧燃料ポンプ |
JP2010174968A (ja) * | 2009-01-29 | 2010-08-12 | Denso Corp | 電磁弁 |
JP2011157918A (ja) * | 2010-02-03 | 2011-08-18 | Denso Corp | 高圧ポンプ |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS635140A (ja) * | 1986-06-24 | 1988-01-11 | Diesel Kiki Co Ltd | 燃料噴射ポンプの噴射制御方法 |
JP4432610B2 (ja) * | 2004-05-17 | 2010-03-17 | トヨタ自動車株式会社 | 内燃機関の燃料供給装置 |
EP1763631A2 (en) * | 2004-07-02 | 2007-03-21 | Toyota Jidosha Kabushiki Kaisha | Fuel supply system for internal combustion engine |
JP2006132517A (ja) * | 2004-10-07 | 2006-05-25 | Toyota Motor Corp | 内燃機関の燃料噴射装置および内燃機関の高圧燃料系統の制御装置 |
JP4415884B2 (ja) * | 2005-03-11 | 2010-02-17 | 株式会社日立製作所 | 電磁駆動機構,電磁弁機構及び電磁駆動機構によって操作される吸入弁を備えた高圧燃料供給ポンプ,電磁弁機構を備えた高圧燃料供給ポンプ |
JP4455470B2 (ja) * | 2005-10-19 | 2010-04-21 | 日立オートモティブシステムズ株式会社 | 高圧燃料ポンプ、及び高圧燃料ポンプのノーマルクローズ型の電磁弁のコントローラ |
US20090090331A1 (en) * | 2007-10-04 | 2009-04-09 | Ford Global Technologies, Llc | Volumetric Efficiency Based Lift Pump Control |
EP2317105B1 (en) * | 2009-10-28 | 2012-07-11 | Hitachi Ltd. | High-pressure fuel supply pump and fuel supply system |
JP5331731B2 (ja) * | 2010-03-03 | 2013-10-30 | 日立オートモティブシステムズ株式会社 | 電磁式の流量制御弁及びそれを用いた高圧燃料供給ポンプ |
US9399976B2 (en) * | 2013-07-18 | 2016-07-26 | Denso International America, Inc. | Fuel delivery system containing high pressure pump with isolation valves |
-
2012
- 2012-02-27 JP JP2012039517A patent/JP5975672B2/ja not_active Expired - Fee Related
-
2013
- 2013-01-15 WO PCT/JP2013/050504 patent/WO2013128958A1/ja active Application Filing
- 2013-01-15 US US14/374,840 patent/US20150017039A1/en not_active Abandoned
- 2013-01-15 CN CN201380008008.6A patent/CN104093969B/zh active Active
- 2013-01-15 DE DE112013001157.3T patent/DE112013001157T5/de not_active Withdrawn
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2006291838A (ja) * | 2005-04-11 | 2006-10-26 | Hitachi Ltd | 高圧燃料ポンプ |
JP2010174968A (ja) * | 2009-01-29 | 2010-08-12 | Denso Corp | 電磁弁 |
JP2011157918A (ja) * | 2010-02-03 | 2011-08-18 | Denso Corp | 高圧ポンプ |
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US20150017039A1 (en) | 2015-01-15 |
CN104093969B (zh) | 2016-11-09 |
DE112013001157T5 (de) | 2014-11-06 |
JP2013174191A (ja) | 2013-09-05 |
JP5975672B2 (ja) | 2016-08-23 |
CN104093969A (zh) | 2014-10-08 |
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