WO2017175539A1 - 高圧燃料供給ポンプ - Google Patents
高圧燃料供給ポンプ Download PDFInfo
- Publication number
- WO2017175539A1 WO2017175539A1 PCT/JP2017/009646 JP2017009646W WO2017175539A1 WO 2017175539 A1 WO2017175539 A1 WO 2017175539A1 JP 2017009646 W JP2017009646 W JP 2017009646W WO 2017175539 A1 WO2017175539 A1 WO 2017175539A1
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- WIPO (PCT)
- Prior art keywords
- pump body
- pressure fuel
- fuel supply
- supply pump
- pump
- Prior art date
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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
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/445—Selection of particular materials
-
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/30—Controlling fuel injection
- F02D41/38—Controlling fuel injection of the high pressure type
- F02D41/3809—Common rail control systems
- F02D41/3836—Controlling the fuel pressure
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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
- F02M57/00—Fuel-injectors combined or associated with other devices
- F02M57/02—Injectors structurally combined with fuel-injection pumps
- F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
- F02M57/027—Injectors structurally combined with fuel-injection pumps characterised by the pump drive electric
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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
- 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
- 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
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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
- 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
- F02M59/48—Assembling; Disassembling; Replacing
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- C—CHEMISTRY; METALLURGY
- C21—METALLURGY OF IRON
- C21D—MODIFYING THE PHYSICAL STRUCTURE OF FERROUS METALS; GENERAL DEVICES FOR HEAT TREATMENT OF FERROUS OR NON-FERROUS METALS OR ALLOYS; MAKING METAL MALLEABLE, e.g. BY DECARBURISATION OR TEMPERING
- C21D9/00—Heat treatment, e.g. annealing, hardening, quenching or tempering, adapted for particular articles; Furnaces therefor
- C21D9/0068—Heat treatment, e.g. annealing, hardening, quenching or tempering, adapted for particular articles; Furnaces therefor for particular articles not mentioned below
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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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
- F02M2200/8046—Fuel injection apparatus manufacture, repair or assembly the manufacture involving injection moulding, e.g. of plastic or metal
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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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
- F02M2200/8084—Fuel injection apparatus manufacture, repair or assembly involving welding or soldering
-
- 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
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
Definitions
- the present invention relates to a high-pressure fuel supply pump that pumps fuel to a fuel injection valve of an internal combustion engine, and particularly includes a pump body in which a pressurizing chamber that pressurizes fuel is formed, and functional parts such as an electromagnetic suction valve mechanism are provided in the pump body. It relates to the structure to be attached.
- Patent Document 1 describes that “the pump housing is integrally formed by casting an iron material such as low carbon steel, austenitic stainless steel, or ferritic stainless steel” (see paragraph 0049).
- Pulp housing 4.0 is cylinder 4 2, tappet guide 4 4, flange 46, solenoid valve support 48, suction part 50, and discharge part 70.
- an iron material such as stainless steel
- it is hardened by quenching.
- surface treatment such as plating on the outer peripheral side of the body, which may increase production cost.
- other functional parts such as an electromagnetic suction valve mechanism are welded and joined to the pump body, the material hardened by quenching has low weldability, and cracks may occur during welding.
- the pump body is cast to integrally form the flange and the pump body, and the material is low carbon steel not subjected to quenching, particularly austenitic stainless steel or ferritic stainless steel. It is possible. However, when these low carbon steels and ferritic stainless steels are used as countermeasures for weldability, they are also inferior in corrosion resistance, so it is necessary to apply plating to the outer peripheral side of the pump body, resulting in an increase in production costs as a result. is there. In the case of austenitic stainless steel, it is not necessary to apply plating, but in the pump body where high pressure acts, the strength is insufficient and the difference in thermal expansion is different from the hard parts used inside the pump. When the temperature is high or low, there is a possibility that a gap is generated in the fitting part or the fastening part between the high hardness component and the pump body, and the necessary performance as a pump may not be exhibited.
- an object of the present invention is to provide a high-pressure fuel supply pump having a pump body that can be manufactured by forging, improving corrosion resistance and weldability.
- the present invention provides: “In a high-pressure fuel supply pump having a metal pump body forming a pressurizing chamber, the pump body has 12% to 18% Cr and 3% to 7% Ni. And the pump body has a forged surface at a part of the outer peripheral surface thereof ”.
- 1 is a longitudinal sectional view of a high-pressure fuel supply pump according to a first embodiment of the present invention. It is the horizontal direction sectional view seen from the upper direction of the high-pressure fuel supply pump by the first example of the present invention. It is the longitudinal cross-sectional view seen from FIG. 1 of the high-pressure fuel supply pump by 1st Example of this invention from another direction.
- 1 is a longitudinal sectional view of a high-pressure fuel supply pump in which a suction joint according to a first embodiment of the present invention is attached to a side surface of a pump body. 1 shows a welding structure of a discharge joint of a high-pressure fuel supply pump according to a first embodiment of the present invention.
- 1 is an enlarged longitudinal sectional view of an electromagnetic intake valve mechanism of a high-pressure fuel supply pump according to a first embodiment of the present invention, showing a state where the electromagnetic intake valve is in an open state.
- 1 is a configuration diagram of an engine system to which a high-pressure fuel supply pump according to a first embodiment of the present invention is applied.
- 1 is a horizontal sectional view of a high-pressure fuel supply pump in which a suction joint according to a first embodiment of the present invention is attached to a side surface of a pump body, as viewed from above. It is the horizontal direction sectional view which looked at the high pressure fuel supply pump with which the suction joint by the 1st example of the present invention was attached to the side of the pump body from the upper part, and the discharge joint is a figure integral with the pump body.
- Example 1 of the present invention will be described in detail with reference to the drawings.
- a portion surrounded by a broken line indicates a main body of a high-pressure fuel supply pump (hereinafter referred to as a high-pressure pump), and indicates that the mechanism / part shown in the broken line is integrated in the pump body 1. .
- a high-pressure pump a high-pressure fuel supply pump
- Fuel in the fuel tank 20 is pumped up by a feed pump 21 based on a signal from an engine control unit 27 (hereinafter referred to as ECU).
- ECU engine control unit 27
- the fuel is pressurized to an appropriate feed pressure and sent to the low-pressure fuel inlet 10a of the high-pressure pump through the suction pipe 28.
- the fuel that has passed through the suction joint 51 from the low-pressure fuel suction port 10a is a pressure pulsation propagation preventing mechanism 100 having a valve 102, a pressure pulsation reducing mechanism 9, and a suction port 31b of an electromagnetic suction valve 300 that constitutes a variable capacity mechanism via a suction passage.
- the fuel that has flowed into the electromagnetic suction valve 300 passes through the fuel introduction passage 30p and the valve body 30, and flows into the pressurizing chamber 11.
- the reciprocating power is applied to the plunger 2 by the cam mechanism 93 of the engine.
- the reciprocating motion of the plunger 2 sucks fuel from the valve body 30 during the downward stroke of the plunger 2 and pressurizes the fuel during the upward stroke.
- the fuel is pumped to the common rail 23 to which the pressure sensor 26 is attached.
- the injector 24 injects fuel into the engine based on a signal from the ECU 27.
- This embodiment is a high pressure pump applied to a so-called direct injection engine system in which an injector 24 blows fuel directly into a cylinder cylinder of an engine.
- the high-pressure pump discharges the fuel flow rate so as to obtain a desired supply fuel by a signal from the ECU 27 to the electromagnetic suction valve 300.
- FIG. 1 is a longitudinal sectional view of the high-pressure pump of this embodiment
- FIG. 2 is a horizontal sectional view of the high-pressure pump as viewed from above
- FIG. 3 is a longitudinal sectional view of the high-pressure pump as seen from a different direction from FIG.
- the suction joint 51 is provided at the upper portion of the damper cover
- FIG. 4 is a longitudinal sectional view of the high-pressure pump in which the suction joint 51 is provided on the side surface of the pump body 1.
- the high-pressure pump of the present embodiment uses a mounting flange 1e provided on the pump body 1 to be in close contact with the plane of the cylinder head 90 of the internal combustion engine and is fixed with a plurality of bolts (not shown).
- ⁇ O-ring 61 is fitted into the pump body 1 for sealing between the cylinder head 90 and the pump body 1 to prevent engine oil from leaking outside.
- the pump body 1 is provided with a cylinder for guiding the reciprocating motion of the plunger 2.
- An electromagnetic suction valve 300 for supplying fuel to the pressurizing chamber 11 and a discharge valve mechanism 8 for discharging the fuel from the pressurizing chamber 11 to the discharge passage and preventing backflow are provided.
- the fuel that has passed through the discharge valve mechanism 8 is connected to engine-side components by a discharge joint 12c.
- the cylinder 6 is fixed to the pump body 1 by press-fitting on the outer peripheral side thereof.
- the surface of the cylindrical press-fitting portion is sealed so that fuel pressurized from the gap with the pump body 1 does not leak to the low pressure side.
- a tappet 92 that converts the rotational movement of the cam 93 attached to the camshaft of the internal combustion engine into a vertical movement and transmits it to the plunger 2.
- the plunger 2 is pressure-bonded to the tappet 92 by the spring 4 through the retainer 15. Thereby, the plunger 2 can be reciprocated up and down with the rotational movement of the cam 93.
- the plunger seal 13 held at the lower end of the inner periphery of the seal holder 7 is installed in a slidable contact with the outer periphery of the plunger 2 at the lower part of the cylinder 6 in the figure.
- lubricating oil including engine oil
- the suction joint 51 is attached to the pump body 1 or the damper cover 14.
- the suction joint 51 is connected to a low-pressure pipe that supplies fuel from the fuel tank 20 of the vehicle, and the fuel is supplied from here to the inside of the high-pressure pump.
- the suction filter 52 in the suction joint 51 serves to prevent foreign matter existing between the fuel tank 20 and the low-pressure fuel inlet 10a from being absorbed into the high-pressure fuel supply pump by the flow of fuel.
- the fuel that has passed through the low pressure fuel suction port 10a reaches the suction port 31b of the electromagnetic suction valve 300 via the pressure pulsation reducing mechanism 9 and the low pressure fuel flow path 10d.
- the discharge valve mechanism 8 provided at the outlet of the pressurizing chamber 11 includes a discharge valve sheet 8a, a discharge valve 8b that contacts and separates from the discharge valve sheet 8a, and a discharge valve spring that urges the discharge valve 8b toward the discharge valve sheet 8a. 8c, and a stopper 8d that determines the stroke (movement distance) of the discharge valve 8b.
- the discharge valve stopper 8d and the pump body 1 are joined by welding at the contact portion 8e to block the fuel and the outside.
- the discharge valve 8b When there is no fuel differential pressure in the pressurizing chamber 11 and the discharge valve chamber 12a, the discharge valve 8b is pressed against the discharge valve seat 8a by the urging force of the discharge valve spring 8c and is in a closed state. Only when the fuel pressure in the pressurizing chamber 11 becomes higher than the fuel pressure in the discharge valve chamber 12a, the discharge valve 8b opens against the discharge valve spring 8c. The high-pressure fuel in the pressurizing chamber 11 is discharged to the common rail 23 through the discharge valve chamber 12a covered with the discharge valve cover 12d, the fuel discharge passage 12b, and the fuel discharge port 12. When the discharge valve 8b is opened, the discharge valve 8b comes into contact with the discharge valve stopper 8d, and the stroke is limited.
- the stroke of the discharge valve 8b is appropriately determined by the discharge valve stopper 8d.
- the discharge valve 8b repeats opening and closing movements, the discharge valve 8b is guided by the outer peripheral surface of the discharge valve stopper 8d so that the discharge valve 8b moves only in the stroke direction. By doing so, the discharge valve mechanism 8 becomes a check valve that restricts the flow direction of fuel.
- the pressurizing chamber 11 includes the pump body 1, the electromagnetic suction valve 300, the plunger 2, the cylinder 6, and the discharge valve mechanism 8.
- the rod biasing spring 40 is set to have a biasing force necessary and sufficient to keep the valve element 30 open in a non-energized state.
- a so-called normally open high pressure pump is shown, but the present invention is not limited to this, and can be applied to a normally closed high pressure pump.
- the volume of the pressurizing chamber 11 decreases with the compression motion of the plunger 2. In this state, the fuel once sucked into the pressurizing chamber 11 once again passes through the opening of the valve body 30 in the valve-opened state. Since the pressure is returned to 10d, the pressure in the pressurizing chamber does not increase. This process is called a return process.
- the electromagnetic suction valve 300 sucks fuel into the pressurizing chamber 11 by moving the magnetic core 39, the movable core 36, the rod 35 and the valve body 30 arranged following them by energizing the electromagnetic coil 43. Refers to the sending mechanism. These functions are described in detail below.
- the valve element 30 operates in the valve opening direction by the strong rod urging spring 40, so that it is normally open, but from the engine control unit 27 (hereinafter referred to as ECU). Is applied to the electromagnetic suction valve 300, a current flows through the electromagnetic coil 43 via the terminal 46. When the current flows, the magnetic core 39 generates a magnetic attractive force.
- the movable core 36 is attracted in the valve closing direction by the magnetic attractive force of the magnetic core 39 on the magnetic attractive surface S shown in FIG.
- a rod 35 having a flange portion 35a for locking the movable core 36 is disposed between the movable cores 36.
- the rod biasing spring 40 is covered with a lid holding member 39 and a lid member 44. Since the rod 35 has the flange portion 35 a, the movable core 36 can be locked, so that the rod 35 can move together with the movable core 36. Therefore, the rod 35 disposed between the movable cores 36 can move in the valve closing direction when a magnetic attractive force is applied. Further, the rod 35 is disposed between the valve closing biasing spring 41 and the rod guide portion 37 b provided with the fuel passage 37 at the lower part of the movable core.
- the rod 35 is an inner peripheral portion of the flange portion 35a, and a recessed portion 35b that is recessed toward the inner peripheral side is formed at a position where the rod 35 contacts the movable core 36.
- a recessed portion 35b that is recessed toward the inner peripheral side is formed at a position where the rod 35 contacts the movable core 36.
- the rod 35 is formed with an inclined portion 35c whose diameter decreases toward the tip at the tip on the valve body 30 side.
- the rod 35 is formed by a lathe process, a concave portion that is recessed on the opposite side of the valve body 30 is formed at the distal end portion on the valve body 30 side.
- the lower part (intake valve side) of the rod 35 includes a valve body 30, an intake valve biasing spring 33, and a stopper 32.
- the valve body 30 protrudes toward the pressurizing chamber, and a guide portion 30 b is formed that is guided by the suction valve biasing spring 33.
- the valve body 30 is moved by the gap of the valve body stroke 30e as the rod 35 moves, so that the fuel supplied from the supply passage 10d in the valve open state is supplied to the pressurizing chamber.
- the guide portion 30b is press-fitted into the housing of the suction valve mechanism, and stops moving when it collides with the fixed stopper 32.
- the rod 35 and the valve body 30 are separate and independent structures.
- the valve body 30 closes the flow path to the pressurizing chamber 11 by contacting the valve seat of the valve seat member 31 disposed on the suction side, and the flow path to the pressurizing chamber 11 by moving away from the valve seat. Configured to open.
- the discharged fuel becomes 30 MPa or more. Therefore, the pressure chamber 11 becomes high pressure, and the valve body 30 collides with the valve seat member 31.
- the impact when the valve body 30 collides with the stopper 32 is very large, and it is necessary to increase the strength thereof.
- the valve body 30 is arranged in a flat plate shape and includes a flat plate portion and a guide portion 30b that protrudes toward the pressurizing chamber.
- the thickness of the flat plate portion is focused on as an element that affects the strength. That is, the strength is improved by increasing the thickness of the flat plate portion of the valve body 30 in the moving direction of the suction valve biasing spring 33 as shown in FIG. Specifically, the thickness of the flat plate portion is made thicker than the thickness of the guide portion 30b protruding from the flat plate portion.
- FIG. 6 shows a cross-sectional view of the position where the suction port 31b (flow path) formed in the valve seat member 31 is the largest.
- the magnetic urging force overcomes the urging force of the rod urging spring 40 and the rod 35 moves away from the intake valve 30. Therefore, the suction valve 30 is closed by the biasing force by the suction valve biasing spring 33 and the fluid force caused by the fuel flowing into the suction passage 10d. After the valve is closed, the fuel pressure in the pressurizing chamber 11 rises with the upward movement of the plunger 2, and when the pressure exceeds the pressure at the fuel discharge port 12, high-pressure fuel is discharged via the discharge valve mechanism 8 to the common rail 23. Supplied. This stroke is called a discharge stroke.
- the compression stroke of the plunger 2 (the ascending stroke from the lower starting point to the upper starting point) consists of a return stroke and a discharge stroke.
- the quantity of the high-pressure fuel discharged can be controlled by controlling the energization timing to the coil 43 of the electromagnetic suction valve 300. If the timing of energizing the electromagnetic coil 43 is advanced, the ratio of the return stroke during the compression stroke is small and the ratio of the discharge stroke is large. That is, the amount of fuel returned to the suction passage 10d is small and the amount of fuel discharged at high pressure is large. On the other hand, if the energization timing 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 passage 10d is large, and the amount of fuel discharged at high pressure is small.
- the energization timing to the electromagnetic coil 43 is controlled by a command from the ECU 27.
- the relief valve 200 includes a relief valve cover 201, a ball valve 202, a relief valve presser 203, a spring 204, and a spring holder 205.
- the relief valve 200 is a valve that is configured to operate only when a problem occurs in the common rail 23 or the member ahead and the pressure becomes abnormally high, and the pressure in the common rail 23 or the member ahead is increased. The valve is opened only in the event of a failure and returns the fuel to the pressurized chamber. Therefore, it has a very strong spring 204.
- the low pressure fuel chamber 10 is provided with a pressure pulsation reducing mechanism 9 that reduces and reduces the pressure pulsation generated in the high pressure pump from spreading to the fuel pipe 28.
- a damper upper portion 10b and a damper lower portion 10c are provided above and below the pressure pulsation reducing mechanism 9 with a gap therebetween.
- the pressure pulsation reducing mechanism 9 provided in the low-pressure fuel chamber 10 is formed of a metal diaphragm damper in which two corrugated disk-shaped metal plates are bonded together on the outer periphery and an inert gas such as argon is injected inside. The pressure pulsation is absorbed and reduced by expansion and contraction of the metal damper.
- Reference numeral 9b denotes a mounting bracket for fixing the metal damper to the inner peripheral portion of the pump body 1, and since it is installed on the fuel passage, the support portion with the damper is not part of the entire circumference but part of the mounting bracket 9b. It allows fluid to flow back and forth freely.
- the plunger 2 has a large-diameter portion 2a and a small-diameter portion 2b, and the volume of the sub chamber 7a increases or decreases as the plunger reciprocates.
- the sub chamber 7a communicates with the low pressure fuel chamber 10 through a fuel passage 10e. When the plunger 2 descends, fuel flows from the sub chamber 7a to the low pressure fuel chamber 10, and when it rises, fuel flows from the low pressure fuel chamber 10 to the sub chamber 7a.
- the discharge joint 12c is inserted or press-fitted into a hole 1k provided in the pump body 1, and the joint surface 12e is welded.
- the stress at the time of pump operation generated in the welded portion is generated by the space 400 provided by the recessed portion 1f formed in the pump body 1 and the recessed portion 12f formed in the discharge joint 12c. Reduced.
- the pump body 1 has a forged surface at a part of the outer peripheral surface. That is, the manufacturing cost can be suppressed by forming the pump body 1 by forging.
- the pump body 1 since the pump body 1 may be machined as necessary after it is formed by forging, it is only necessary to have a forged surface at least at a part of the outer peripheral surface. The forged surface is rougher than the machined surface by cutting.
- the high-pressure pump is used in the engine room, it is necessary to have a corrosion resistance sufficient to withstand this.
- a steel material containing 12% to 18% Cr (chromium) and 3% to 7% Ni (nickel) is used as the material of the pump body 1.
- the material of the pump body 1 is made of a steel material containing about 16% Cr and about 5% Ni.
- the high-pressure pump needs to improve pitting corrosion resistance. Therefore, in this embodiment, a steel material containing 0.5% to 3% of Mo (molybdenum) as the material of the pump body 1 is employed. More specifically, it is desirable to contain about 1% Mo. Mo is also a component that can increase strength and hardness at high temperatures by mixing with Cr. It is desirable to contain 0.01% to 0.1% N (nitrogen). By including N, the tensile strength and the yield strength can be increased, and in particular, corrosion resistance such as pitting corrosion resistance and crevice corrosion resistance can be improved.
- Mo mobdenum
- N nitrogen
- the pump body 1 is required to have a strength capable of withstanding a load due to the high pressure because a high pressure fuel of a 20 MPa level and a maximum of 60 MPa level acts inside.
- a steel material containing Cr, Ni, and Mo with the above distribution, a material having high strength with a tensile strength of 900 MPa level can be obtained by heat treatment.
- N (nitrogen) and 0.08% or less C (carbon) a high strength steel material can be obtained.
- the discharge joint 12c, the flow control solenoid 300, the damper cover 14, the suction joint 51 and the like are fixed to the pump body 1 as functional parts by welding.
- these functional parts are joined to the pump body 1 by welding, a space for screw threads to be engaged is unnecessary as compared with screw fastening or the like.
- the discharge joint 12c is welded to the pump body 1 at the connecting portion 12e.
- This connecting portion functions as a seal portion for shutting off fuel inside the pump from the outside of the pump, so that space saving can be achieved. Can do.
- the pump can be miniaturized and materials can be saved.
- the seal part is required separately from the fastening part, resulting in an increase in production cost.
- weldability as a material of the pump body 1 is required.
- the material of the pump body 1 is weldable so that the deteriorated part caused by welding to the pump body 1 does not break, or the loss of stickiness and loss of resistance to impact and bending. It is necessary to have
- the pump body 1 is required to have strength, it is conceivable to use a high-strength martensitic material such as SUS420J2 or SUS431.
- a high-strength martensitic material such as SUS420J2 or SUS431.
- the present inventors such as martensitic SUS420J2 and SUS431 have sufficient strength, but have a very large amount of carbon, so that the required weldability cannot be obtained. It has been found that the weld cracks that have occurred. Accordingly, when these materials are used for the pump body 1 and the functional parts are fixed by welding, it is impossible to provide a reliable high-pressure pump due to this weld crack.
- Cr is 12% to 18%
- Ni is 3% to 7%
- Mo is 0.5% to 3%. It is what you have.
- This Mo contributes not only to pitting corrosion resistance but also to improvement of weldability.
- it can be set as material sufficient with respect to weldability by restraining the carbon content which the pump body 1 contains to 0.08% or less.
- N nitrogen
- the above-described N contributes to pitting corrosion resistance, but if it is too much, the weldability deteriorates. Therefore, in this embodiment, it is suppressed to 0.1% or less.
- the pump body 1 of this embodiment is formed by forging. It is possible to improve the material yield by providing the convex recesses for the required shape by forming the pump body 1 by forging for the process of manufacturing ordinary rod-like material only by machining. is there. In short, molding can be performed with less material for machining, and as a result, manufacturing cost can be reduced.
- the functional parts described above can be forged integrally with the pump body 1.
- the flange 1e for fixing the pump body 1 and the high-pressure pump to the engine is integrally formed by forging.
- the material is required to have forgeability.
- the above-described chemical components as the material, it is possible to obtain good forgeability, particularly by suppressing the carbon content to 0.08% or less.
- a material that suppresses P and S, which are impurities, to 0.05% or less is used.
- the space 1g for escaping the tool for fastening the bolt for mounting the pump can be stealed by forging.
- materials such as Cr, Ni, and Mo employed in this embodiment are effective materials compared to Fe (iron), it is desirable to form the pump body 1 with a small amount of steel material. Therefore, in this embodiment, the material described above is used for the pump body 1 and the pump body 1 and the flange 1e are integrally formed by forging.
- the flange portion 1 e is formed at two symmetrical positions on the outer peripheral portion of the pump body 1.
- the pump body 1 is formed so that the outer peripheral portion 1i is substantially cylindrical.
- FIG. 8 shows a drawing in which the discharge joint 12c and the pump body 1 are separate and the discharge joint 12c is fixed to the pump body 1 by welding.
- FIG. 9 shows a drawing in which the material of this embodiment is used for the pump body 1, and the discharge joint 12c and the pump body 1 are integrally formed by forging with the same member.
- the pump body 1 is formed by integrally forming an engine fitting portion 1h into which the high-pressure pump is inserted into the engine with the same member.
- the shape becomes complicated and forging becomes difficult.
- the integration of the discharge joint 12c and the pump body 1 and the stealing of the meat are given priority, and the fitting portion 1h with the engine is separated from the pump body 1, depending on the complexity and ease of forging. It is also possible to manufacture by selecting a part and a separate part flexibly.
- the surplus from the split surface of the mold is not used for the forging to protrude from the normal split surface of the mold. It is possible to use methods such as closed forging and closed forging that do not protrude, and the production cost can be further reduced.
- the pump body 1 is formed by a forging process, and then a necessary part is machined. Specifically, for example, when the discharge joint 12c is fixed to the pump body 1 by welding, the welding connection surface 12e needs to be smooth. Therefore, the pump body 1 needs machinability (ease of machining).
- machinability ease of machining
- the present inventors can obtain good machinability by suppressing the amount of C (carbon) to 0.08% or less as the material of the pump body 1 and further using the metal having the above distribution. I found.
- Mn manganese
- S sulfur
- the pump body 1 is formed with a hole 1k into which the discharge joint 12c for discharging the fuel pressurized in the pressurizing chamber 11 is inserted. Is done.
- a portion where the hole 1k is formed is formed by a recessed portion 1b that is recessed inward with respect to the outermost peripheral end 1k of the outer peripheral portion 1i.
- the welding surface between the discharge joint 12c and the pump body 1, that is, the recess 1b to which the laser is irradiated is formed on the outer peripheral side of the hole 1k as a flat portion in a direction perpendicular to the insertion direction of the discharge joint 12c.
- the recess 1b is formed in a plane substantially parallel to the outer periphery 1i.
- the recess 1b is formed by forging, the material of the pump body 1 can be reduced, so that the cost can be reduced and the weight can be reduced.
- the dent 1b is a part where the discharge joint 1c is welded, it is desirable to make the surface smooth by machining.
- the machining process can be reduced. By doing or omitting, it is possible to reduce the manufacturing cost. Further, the machining process for the recess 1b can be performed only on a necessary portion of the welded portion and the forged surface is left for the rest, so that the manufacturing cost can be reduced.
- the pump body 1 has a machined surface formed more smoothly than the forged surface on the entire outer periphery at a position corresponding to the hole 1k in the vertical direction, and the forged surface below the hole 1k.
- the machining surface can be reduced to the minimum necessary, and the rest can be left as the forged surface, so that the manufacturing speed can be improved and the manufacturing cost can be reduced.
- it demonstrated that it has a forge surface below the hole 1k here it is the same also about the place where the hole 1k is not formed in the position corresponding to the hole 1k in an up-down direction (height direction). It is preferable to have a forged surface.
- the hole 1k is formed at the center in the vertical direction (height direction)
- the manufacturing cost can be reduced as described above. That is, it is desirable to have a forged surface around the hole 1k other than where the hole 1k is formed.
- the pump body 1 is formed with a hole 1l into which a suction joint 51 for sucking fuel is inserted.
- a portion of the outer peripheral portion 1i of the pump body 1 where the hole 11 is formed is formed with a recessed portion 1c that is recessed inward with respect to the outermost peripheral end 1j of the outer peripheral portion 1i.
- the recessed portion 1c is formed as a flat portion in a direction orthogonal to the insertion direction of the suction joint 51 on the outer peripheral side of the hole 1l.
- the pump body 1 is formed with a hole 1m into which the electromagnetic suction valve 300 is inserted. And the site
- the recessed portion 1d is formed as a flat portion in a direction orthogonal to the insertion direction of the electromagnetic suction valve 300 on the outer peripheral side of the hole portion 1m.
- the pump body 1 is formed with a hole portion into which a stopper 8d for determining the stroke (movement distance) of the discharge valve 8b of the discharge valve mechanism 8 is inserted.
- a portion where the hole is formed is formed with a recessed portion 1n that is recessed inwardly with respect to the outermost peripheral end portion 1j of the outer peripheral portion 1i.
- the recess 1n is formed by a flat portion in a direction orthogonal to the insertion direction of the stopper 8d of the discharge valve mechanism 8 on the outer peripheral side of the hole.
- the pump body 1 Since the material of the pump body 1 can be reduced by forming these recesses 1c, 1d, and 1m, it is possible to reduce the cost and reduce the weight.
- the pump body 1 has a machined surface formed more smoothly than the forged surface on the entire outer periphery at a position corresponding to the hole in the vertical direction, and has the forged surface below the hole. It is the same as what I did.
- any of the above-described holes (1k, 1l, 1m) is surrounded by a flat surface (concave part) that is substantially the same as the opening surface of the hole (1k, 1l, 1m) in the outer peripheral part 1i of the pump body 1.
- 1b, 1c, 1d, 1n) are formed.
- the flat portions (recessed portions 1b, 1c, 1d, 1n) are formed by machined surfaces that are formed more smoothly than the forged surfaces. It is desirable for the pump body 1 to be formed with an inclined surface so as to spread from the flat portion (the recessed portions 1b, 1c, 1d, and 1n) toward the outer peripheral side.
- the pump body 1 has a forged surface formed below the flat portion (recessed portions 1b, 1c, 1d, 1n), and the inclined surface is formed so as to be connected to the forged surface. It is desirable.
- the pump body 1 of this embodiment can improve the corrosion resistance, it is not necessary to provide plating for improving the corrosion resistance.
- a so-called plating-less pump body 1 can be obtained.
- the damper cover 14 that covers the pump body 1 from above is fixed directly to the pump body 1 by a welded portion.
- the welded portion of the damper cover 14 has a lattice pattern that loses plating, which may be inferior in corrosion resistance.
- a process such as applying a coating material to the welded portion after the welding and joining is necessary.
- such a process is unnecessary, and the productivity can be greatly improved.
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Abstract
Description
破線で囲まれた部分が高圧燃料供給ポンプ(以下、高圧ポンプと呼ぶ)の本体を示し、この破線の中に示されている機構・部品はポンプボディ1に一体に組み込まれていることを示す。
本実施例においてポンプボディ1は外周面の一部に鍛造面を有する。つまり、ポンプボディ1が鍛造により成形されることで製造コストを抑えることができる。なお、ポンプボディ1を鍛造で成形した後に必要に応じて切削加工をすることがあるので、少なくとも外周面の一部に鍛造面を有していれば良い。切削による機械加工を行った面に対し、鍛造面は表面粗さが荒くなる。
ここで、高圧ポンプはエンジンルーム内で使用するものであるため、これに耐えるだけの耐食性を有するように構成することが必要である。この場合にポンプボディ1の外周面にめっき等の表面処理を行うことで耐久性を向上させることも考えられるが、これにより生産コストの増大を招く虞がある。そこで本実施例では、ポンプボディ1の素材としてCr(クロム)を12%~18%、Ni(ニッケル)を3%~7%を含む鉄鋼材料を採用したものである。これにより、ポンプボディ1の外周面にめっき等の表面処理を行うことなく、必要な耐久性をポンプボディ1に持たせることが可能である。より具体的には、ポンプボディ1の材料を、Crを16%程度、またNi量を5%程度、含む鉄鋼材料で構成することが望ましい。このようにCrとNiとを組み合わせることにより必要な耐食性が得られ、また耐熱性を得ることができる。
2 プランジャ
6 シリンダ
7 シールホルダ
8 吐出弁機構
9 圧力脈動低減機構
10a 低圧燃料吸入口
11 加圧室
12 燃料吐出口
12c 吐出ジョイント
13 プランジャシール
30 吸入弁
36 アンカー
40 ロッド付勢ばね
43 電磁コイル
100 圧力脈動伝播防止機構
101 弁シート
102 弁
103 ばね
104 ばねストッパ
200 リリーフバルブ
300 電磁吸入弁
400 溶接部空間
500 レーザビーム
Claims (19)
- 加圧室を形成する金属製のポンプボディを備えた高圧燃料供給ポンプにおいて、
前記ポンプボディはCrを12%~18%、Niを3%~7%を含む鉄鋼材料であり、前記ポンプボディは外周面の一部に鍛造面を有する高圧燃料供給ポンプ。 - 請求項1に記載の高圧燃料供給ポンプであって、
前記ポンプボディはMoを0.5%~3%を含む鉄鋼材料である高圧燃料供給ポンプ。 - 請求項1又は2に記載の高圧燃料供給ポンプであって、
前記ポンプボディは2%以下のMnを含む鉄鋼材料である高圧燃料供給ポンプ。 - 請求項1又は2に記載の高圧燃料供給ポンプであって、
前記ポンプボディは0.08%以下のCを含む鉄鋼材料である高圧燃料供給ポンプ。 - 請求項1又は2に記載の高圧燃料供給ポンプであって、
前記ポンプボディは0.01%~0.1%のNを含む鉄鋼材料である高圧燃料供給ポンプ。 - 請求項1または請求項2に記載の高圧燃料供給ポンプであって、前記ポンプボディは、エンジンに取付けられるフランジを同一部材で一体に成形していることを特徴とする高圧燃料供給ポンプ
- 請求項1または請求項2に記載の高圧燃料供給ポンプであって、前記ポンプボディは、前記高圧燃料供給ポンプがエンジンに挿入されるエンジン勘合部位を同一部材で一体に成形していることを特徴とする高圧燃料供給ポンプ
- 請求項1または請求項2に記載の高圧燃料供給ポンプであって、前記ポンプボディは、吐出ジョイントを同一部材で一体に成形していることを特徴とする高圧燃料供給ポンプ
- 請求項1または請求項2に記載の高圧燃料供給ポンプであって、前記ポンプボディは、吸入ジョイントを同一部材で一体に成形していることを特徴とする高圧燃料供給ポンプ
- 請求項1または請求項2に記載の高圧燃料供給ポンプであって、
前記ポンプボディの素材はEN1.4418、又はEN1.4313である高圧燃料供給ポンプ。 - 請求項1に記載の高圧燃料供給ポンプにおいて、前記ポンプボディを上部から覆うカバーと、前記カバーを前記ポンプボディに対し直接固定する溶接部と、を備えた高圧燃料供給ポンプ。
- 請求項1に記載の高圧燃料供給ポンプにおいて、
前記ポンプボディは外周部がほぼ円筒形状になるように形成され、前記フランジ部の上部は前記外周部の最外周側端部に対して内側に凹んだ凹み部で形成された高圧燃料供給ポンプ。 - 請求項1に記載の高圧燃料供給ポンプにおいて、
前記フランジ部は前記ポンプボディの外周部において対称となる2箇所に形成され、
前記ポンプボディは外周部がほぼ円筒形状になるように形成され、2箇所の前記フランジ部の上部は前記外周部の最外周側端部に対して内側に凹んだ凹み部で形成された高圧燃料供給ポンプ。 - 請求項1に記載の高圧燃料供給ポンプにおいて、
前記ポンプボディは外周部がほぼ円筒形状になるように形成され、
前記ポンプボディには前記加圧室で加圧された燃料を吐出する吐出ジョイントが挿入される孔部が形成され、
前記ポンプボディの外周部のうち、前記孔部が形成される部位は前記外周部の最外周側端部に対して内側に凹んだ凹み部で形成された高圧燃料供給ポンプ。 - 請求項1に記載の高圧燃料供給ポンプにおいて、
前記ポンプボディは外周部がほぼ円筒形状になるように形成され、
前記ポンプボディには燃料を吸入する吸入ジョイントが挿入される孔部が形成され、前記ポンプボディの外周部のうち、前記孔部が形成される部位は前記外周部の最外周側端部に対して内側に凹んだ凹み部で形成された高圧燃料供給ポンプ。 - 請求項1に記載の高圧燃料供給ポンプにおいて、
前記ポンプボディの上部には前記加圧室で加圧された燃料を吐出する吐出ジョイントが挿入される孔部が形成され、
前記ポンプボディは前記孔部に対応する位置に前記鍛造面よりも滑らかに形成される機械加工面を有し、前記孔部よりも下側において前記鍛造面を有する高圧燃料供給ポンプ。 - 請求項1に記載の高圧燃料供給ポンプにおいて、
前記ポンプボディの上部には前記加圧室で加圧された燃料を吐出する吐出ジョイントが挿入される孔部が形成され、
前記ポンプボディは前記孔部に対応する位置の全外周において前記鍛造面よりも滑らかに形成される機械加工面を有し、前記孔部よりも下側において前記鍛造面を有する高圧燃料供給ポンプ。 - 請求項1に記載の高圧燃料供給ポンプにおいて、
前記ポンプボディには前記加圧室で加圧された燃料を吐出する吐出ジョイントが挿入される孔部が形成され、
前記ポンプボディの外周部のうち、前記孔部の周りは前記孔部の開口面とほぼ同一面の平面部が形成され、前記平面部は前記鍛造面よりも滑らかに形成される機械加工面で形成され、
前記ポンプボディには前記平面部から下側に向かって外周側に広がるように傾斜面が形成された高圧燃料供給ポンプ。 - 請求項1に記載の高圧燃料供給ポンプにおいて、
前記ポンプボディには前記加圧室で加圧された燃料を吐出する吐出ジョイントが挿入される孔部が形成され、
前記ポンプボディの外周部のうち、前記孔部の周りは前記孔部の開口面とほぼ同一面の平面部が形成され、前記平面部は前記鍛造面よりも滑らかに形成される機械加工面で形成され、前記ポンプボディには前記平面部から下側に向かって外周側に広がり、かつ前記平面部よりも下側の鍛造面まで繋がる傾斜面が形成された高圧燃料供給ポンプ。
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US16/091,160 US10788003B2 (en) | 2016-04-06 | 2017-03-10 | High-pressure fuel supply pump |
EP17778918.7A EP3441606B1 (en) | 2016-04-06 | 2017-03-10 | High-pressure fuel supply pump |
CN201780021181.8A CN109072845B (zh) | 2016-04-06 | 2017-03-10 | 高压燃料供给泵 |
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JP2007120492A (ja) | 2005-09-29 | 2007-05-17 | Denso Corp | 高圧燃料ポンプ |
JP2008111396A (ja) * | 2006-10-31 | 2008-05-15 | Denso Corp | 高圧燃料ポンプの製造方法 |
JP2012251467A (ja) * | 2011-06-02 | 2012-12-20 | Hitachi Automotive Systems Ltd | 燃料の圧力脈動低減機構、及びそれを備えた内燃機関の高圧燃料供給ポンプ |
WO2014083979A1 (ja) * | 2012-11-29 | 2014-06-05 | 日立オートモティブシステムズ株式会社 | 高圧燃料供給ポンプ |
WO2015163245A1 (ja) * | 2014-04-25 | 2015-10-29 | 日立オートモティブシステムズ株式会社 | 高圧燃料供給ポンプ |
Also Published As
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US10788003B2 (en) | 2020-09-29 |
US20190128229A1 (en) | 2019-05-02 |
EP3441606A1 (en) | 2019-02-13 |
CN109072845A (zh) | 2018-12-21 |
JP6843837B2 (ja) | 2021-03-17 |
EP3441606B1 (en) | 2021-12-01 |
JPWO2017175539A1 (ja) | 2018-11-08 |
CN109072845B (zh) | 2021-07-30 |
EP3441606A4 (en) | 2020-03-18 |
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