WO2013080253A1 - 高圧燃料供給ポンプ - Google Patents
高圧燃料供給ポンプ Download PDFInfo
- Publication number
- WO2013080253A1 WO2013080253A1 PCT/JP2011/006673 JP2011006673W WO2013080253A1 WO 2013080253 A1 WO2013080253 A1 WO 2013080253A1 JP 2011006673 W JP2011006673 W JP 2011006673W WO 2013080253 A1 WO2013080253 A1 WO 2013080253A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- cylinder
- pump housing
- pressurizing chamber
- plunger
- fuel supply
- Prior art date
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Classifications
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- 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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
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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
- F02M59/20—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
- F02M59/366—Valves being actuated electrically
- F02M59/367—Pump inlet valves of the check valve type being open when actuated
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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
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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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0014—Valves characterised by the valve actuating means
- F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
- F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
- F02M63/0019—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means characterised by the arrangement of electromagnets or fixed armatures
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- 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
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- 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
- F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
Definitions
- the present invention relates to a high-pressure fuel supply pump, and more particularly to a cylinder configured in a cup shape.
- a cup (referred to as a plug in Japanese Patent Publication No. 2007-231959) and an inner cylindrical surface (inner peripheral surface) provided in a recess of the pump housing, and A structure in which a pressurizing chamber is formed by fitting a cylindrical cylinder is disclosed, and the cylinder including this cup is configured to be pressed and fixed to the inner peripheral surface of the pump housing by the screw thrust of the cylinder holder. Yes. Further, it is described that the cup and the cylinder may be integrated.
- the cup and the cylinder fitted to the inner cylindrical surface (inner peripheral surface) portion of the pump housing cannot be fixed unless they are pressed and held by a separate member such as a cylinder holder.
- the cylinder used as a part of the pressurizing chamber is pressurized in the direction to escape from the pump housing when pressurizing the fuel. Therefore, it is necessary to increase the fixing force by the cylinder holder as the fuel discharge pressure increases. There is a concern about the increase in size and complexity of the cylinder holder.
- An object of the present invention is to provide a high-pressure fuel supply pump that is low-cost, small, light, high-pressure, and highly reliable in order to solve the above problems.
- a mechanism that can simplify the cylinder holder is provided.
- the cylinder is cup-shaped and fitted to the inner cylindrical surface (inner peripheral surface) portion of the recess of the pump housing, and the inner cylindrical surface (inner peripheral surface) portion of the cylinder and the ceiling portion.
- the cylinder is pressed in the direction of the pump housing by the pressure in the pressurizing chamber even when the fuel discharge pressure (pressure in the pressurizing chamber) is increased. Therefore, the cylinder holder can be simplified, and a high pressure can be realized with a small size and light weight.
- 1 is an example of a fuel supply system using a high-pressure fuel supply pump according to a first embodiment in which the present invention is implemented.
- 1 is a longitudinal sectional view of a high-pressure fuel supply pump according to a first embodiment in which the present invention is implemented. It is a longitudinal cross-sectional view of the high pressure fuel supply pump by 1st Example with which this invention was implemented, and represents a cross section perpendicular
- FIG. 3 shows a state before the electromagnetic suction valve mechanism 30 of the high-pressure fuel supply pump according to the first embodiment in which the present invention is implemented is assembled in the pump housing 1.
- the external view of the flange 41 of the high-pressure fuel supply pump by the 1st Example by which this invention was implemented, and the bush 43 is shown. In this figure, only the flange 41 and the bush 43 are shown, and other components are not shown.
- the enlarged view of the welding part 41a part vicinity of the high-pressure fuel supply pump by the 1st Example by which this invention was implemented is shown.
- the enlarged view of the welding part 41a vicinity vicinity of the high-pressure fuel supply pump by 1st Example by which this invention was implemented is shown, and it expands rather than FIG. It is a longitudinal cross-sectional view of the high pressure fuel supply pump by 2nd Example by which this invention was implemented.
- FIG. 16 is a cross-sectional view of a high-pressure fuel supply pump according to a fifth embodiment in which the present invention is implemented, and shows a view in which a cylinder fixing position is different from FIG. 15.
- 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 low-pressure fuel chamber 10c. It reaches the suction port 30a of the valve mechanism 30.
- 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.
- FIG. 4 is an enlarged view of the electromagnetic intake valve mechanism 30 and shows a state where the electromagnetic coil 53 is not energized and is not energized.
- FIG. 5 is an enlarged view of the electromagnetic intake valve mechanism 30 and shows a state where the electromagnetic coil 53 is energized.
- the pump housing 1 is formed with a recess 1A for accommodating the cylinder 6 including the pressurizing chamber 11 in the center, and a hole 30A for mounting the electromagnetic suction valve mechanism 30 is formed so as to communicate with the pressurizing chamber 11. Has been.
- the plunger rod 31 includes three parts, that is, a suction valve portion 31a, a rod portion 31b, and an anchor fixing portion 31c.
- An anchor 35 is welded and fixed to the anchor fixing portion 31c by a welding portion 37b.
- the spring 34 is fitted into the anchor inner periphery 35a and the first core portion inner periphery 33a as shown in the figure, and a spring force is generated by the spring 34 in a direction in which the anchor 35 and the first core portion 33 are separated.
- the valve seat 32 includes a suction valve seat portion 32a, a suction passage portion 32b, a press-fit portion 32c, and a sliding portion 32d.
- the press-fit portion 32 c is press-fitted and fixed to the first core portion 33.
- the suction valve seat portion 32a is press-fitted and fixed to the pump housing 1, and the pressurization chamber 11 and the suction port 30a are completely blocked by this press-fit portion.
- the first core portion 33 is welded and fixed to the pump housing 1 by a welded portion 37c, and shuts off the suction port 30a and the outside of the high-pressure fuel supply pump.
- the second core portion 36 is fixed to the first core portion 33 by a welded portion 37a, and completely blocks the internal space and the external space of the second core portion 36.
- the second core portion 36 is provided with a magnetic orifice portion 36a.
- the plunger rod 31 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 31 is As shown in FIG. 4, it moves to the right in the figure. In this state, the intake valve portion 31a and the intake valve seat portion 32a come into contact with each other and the intake port 38 is closed.
- the intake valve portion 31a is set to open by overcoming the urging force of the spring 34 and open the intake port 38 by the valve opening force due to the fluid differential pressure.
- the suction valve portion 31 a is completely opened and the anchor 31 is in contact with the first core portion 33.
- the suction valve portion 31 a does not open completely, and the anchor 31 does not contact the first core portion 33.
- the intake valve portion 31a When the intake valve portion 31a is fully open, the valve open state is maintained. On the other hand, when the intake valve portion 31a is not fully opened, the intake valve portion 31a is fully opened by encouraging the valve opening motion of the intake valve portion 31a, so that the anchor 31 is in contact with the first core portion 33, Then maintain that state.
- the compression process of the plunger 2 (the ascending process from the lower start point to the upper start point) includes a return process and a discharge process.
- the amount of high-pressure fuel to be discharged can be controlled by controlling the timing at which the electromagnetic coil 53 of the electromagnetic intake valve mechanism 30 is de-energized.
- the ratio of the return process is small and the ratio of the discharge process is large during the compression process.
- the timing of releasing the input voltage is delayed, the ratio of the return process during the compression process is large and the ratio of the discharge process is small. That is, the amount of fuel returned to the suction passage 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.
- 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 suction port 10 a is pressurized to a high pressure by the reciprocating motion of the plunger 2 in the pressurizing chamber 11 of the pump housing 1, and is pumped from the fuel discharge port 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 in accordance with the number of cylinders of the internal combustion engine, open and close according to a control signal from an engine control unit (ECU) 27, and inject fuel into the cylinders.
- ECU engine control unit
- the suction valve portion 31a repeats the opening / closing motion of the suction port 38 as the plunger 2 moves downward and upward, and the plunger rod 31 repeats the lateral movement in the drawing.
- the movement of the plunger rod 31 is limited to the movement in the horizontal direction in the drawing by the sliding portion 32d of the valve seat 32, and the sliding portion 32d and the rod portion 31b repeat the sliding motion. Therefore, the sliding portion needs to have a sufficiently low surface roughness so as not to be a resistance to the sliding movement of the plunger rod 31.
- the selection of the sliding clearance is as follows.
- the plunger rod 31 touches like a pendulum around the sliding portion, and the anchor 35 and the second core portion 36 come into contact with each other. If the plunger rod 31 slides, the anchor 35 and the second core portion 36 will also slide, so the resistance of the plunger rod 31 will increase, and the responsiveness of the opening / closing motion of the suction port 38 will be poor. Become. Further, since the anchor 35 and the second core portion 36 are made of ferritic magnetic stainless steel, there is a possibility that abrasion powder or the like is generated when they are slid. Furthermore, as will be described later, the smaller the gap between the anchor 35 and the second core portion 36, the greater the magnetic biasing force. If the gap is too large, the magnetic biasing force is insufficient, and the amount of fuel discharged at high pressure cannot be properly controlled. For these reasons, the gap between the anchor 35 and the second core portion 36 needs to be as small as possible and not in contact.
- the sliding part is provided at one place, and the sliding length L of the sliding part 32d is sufficiently long as shown in the figure.
- the sliding portion is formed by the inner diameter of the sliding portion 32d and the outer shape of the rod portion 31b. Both of them require a tolerance, and the clearance of the sliding portion also requires a tolerance.
- the clearance between the anchor 35 and the second core portion 36 has an upper limit value based on the magnetic biasing force as described above. In order to absorb this clearance tolerance and prevent the anchor 35 and the second core portion 36 from coming into contact with each other, the sliding length L may be increased to reduce the pendulum motion.
- the suction valve portion 31a and the suction valve seat portion 32a are not completely in surface contact when the suction port 38 is closed. This is because the verticality of the suction valve portion 31a and the rod portion 31b of the plunger rod 31 and the verticality of the suction valve seat portion 32a and the sliding portion 32d of the valve seat 32 cannot be absorbed by the clearance of the sliding portion. . If the suction valve portion 31a and the suction valve seat portion 32a are not completely in surface contact, the plunger rod 31 may be damaged due to excessive torque applied to the plunger rod 31 by the high pressure fuel in the pressurizing chamber 11 that has become high pressure during the discharge process. There is. In addition, an excessive load is applied to the sliding portion, and the sliding portion may be damaged or worn.
- the suction valve portion 31a and the suction valve seat portion 32a need to be in full surface contact.
- the pendulum motion of the plunger rod 31 is suppressed by increasing the sliding length L as described above, the verticality of the intake valve portion 31a and the rod portion 31b of the plunger rod 31 and the intake of the valve seat 32 The accuracy required for the verticality of the valve seat portion 32a and the sliding portion 32d is increased.
- the valve seat 32 is provided with a suction valve seat portion 32a and a sliding portion 32d.
- the suction valve seat portion 32a and the sliding portion 32d are made the same member so that the perpendicularity between the suction valve seat portion 32a and the sliding portion 32d can be made with high accuracy. If the suction valve seat portion 32a and the sliding portion 32d are separate members, a factor that deteriorates the perpendicularity is inevitably generated in the parts to be processed and joined. However, the suction valve seat portion 32a and the sliding portion 32d should be a single member. This solves this problem.
- the magnetic circuit constructed around the magnetic coil 53 must generate a sufficient magnetic biasing force.
- the members constituting the magnetic circuit are an anchor 35, a first core portion 33, a yoke 51, and a second core portion 36 as shown in FIG. 5, and these are all magnetic materials.
- the magnetic flux does not pass directly between the first core portion 33 and the second core portion 36, and the anchor 35 is interposed. Need to pass through. This is to generate a magnetic urging force between the first core portion 33 and the anchor 35, and the magnetic flux directly passes between the first core portion 33 and the second core portion 36, and the magnetic flux passes through the anchor. If this decreases, the magnetic biasing force will decrease.
- an intermediate member is provided between the first core portion 33 and the second core portion 36. Since this intermediate member is a non-magnetic material, the magnetic flux does not pass directly between the first core portion 33 and the second core portion 36, and all the magnetic flux passes through the anchor 35.
- the first core portion 33 and the second core portion 36 are directly joined by the welded portion 37, and the magnetic orifice portion 36a is provided in the second core portion.
- the thickness is made as thin as the strength allows, while the other portions of the second core portion 36 have a sufficient thickness.
- the magnetic orifice portion 36a is provided in the vicinity of the portion where the first core portion and the anchor 35 are in contact.
- the magnetic flux that passes directly through the first core portion 33 and the second core portion is very small, thereby being generated between the first core portion 33 and the anchor 35.
- the reduction of the magnetic urging force is within an allowable range.
- the first core portion 33 and the anchor 35 are in contact with each other, it is between the second core portion 36 and the anchor 35 that there is the largest gap in the magnetic circuit. Since the gap is not a magnetic material but is filled with fuel, the larger the gap, the greater the magnetic resistance of the magnetic circuit. Therefore, the smaller the gap, the better.
- the gap between the second core portion 36 and the anchor 35 is reduced by increasing the sliding length L of the sliding portion.
- the magnetic coil 53 is formed by winding a lead wire 54 around the axis of the plunger rod 31. Both ends of the lead wire 54 are welded to the terminal 56 at lead wire welds 55.
- the terminal is a conductive substance and is open to the connector portion 58. When a mating connector from the ECU is connected to the connector portion 58, the terminal contacts the mating terminal and transmits current to the coil.
- Fig. 6 shows the conventional structure.
- the lead wire welding part 55 is arrange
- the lead wire welded portion 55 is disposed outside the yoke 51. Since the lead wire welded portion 55 is disposed outside the magnetic circuit, and the space required for the lead wire welded portion 55 is not provided, the entire length of the magnetic circuit can be shortened, and the first core portion 33 and the anchor 35 can be shortened. A sufficient magnetic biasing force can be generated.
- FIG. 7 shows a state before the electromagnetic intake valve mechanism 30 is assembled into the pump housing 1.
- the suction valve unit 37 and the connector unit 38 are created for the suction valve unit 37 and the connector unit 38, respectively.
- the suction valve seat portion 32a of the suction valve unit 37 is press-fitted and fixed to the pump housing 1, and then the welded portion 37c is welded over the entire circumference.
- the welding is laser welding.
- the connector 38 is press-fitted and fixed to the first core portion 33. Thereby, the direction of the connector 58 can be freely selected.
- the pump housing 1 is formed with a recess 1A for accommodating a cylinder 6 including a pressurizing chamber 11 at the center.
- a hole 11A for mounting the discharge valve mechanism 8 is provided in the cylinder so as to open to the pressurizing chamber 11. 6 is formed in a direction intersecting with the recess 1 ⁇ / b> A for housing 6.
- 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 cylinder 6 is formed in a bottomed cup shape having a ceiling portion 6A.
- a concave portion as the pressurizing chamber 11 is formed in the inner peripheral portion of the cylindrical member forming the cylinder.
- a plurality of through holes 6 a communicating with the pressurizing chamber 11 and the suction port 38 and a plurality of through holes 6 b communicating with the pressurizing chamber 11 and the fuel discharge port 12 are formed around the cylinder 6.
- the outer cylindrical surface (outer peripheral surface) of the cylinder 6 is fitted into the inner cylindrical surface (inner peripheral surface) of the recess 1A of the pump housing 1, and is fitted and held by the press-fit portion 6c.
- the cylinder 6 is fixed at two points: a fitting portion 6c on the inner cylindrical surface (inner peripheral surface) of the pump housing 1 and a fitting portion 6d on the inner cylindrical surface (inner peripheral surface).
- the coaxiality with the center axis of 6 is improved.
- a hole 10d communicating with the low-pressure fuel chamber 10c is provided in the ceiling portion 10A of the inner cylindrical surface (inner peripheral surface) of the pump housing 1, and serves as an air vent hole when the cylinder 6 is press-fitted.
- the air vent hole 10d By providing the air vent hole 10d, the press-fitting load of the cylinder 6 can be lowered, and deformation due to buckling can be prevented.
- the communication hole 10d maintains the hole diameter D at a diameter satisfying “area AD> ADc ⁇ Ad”, so that even when high pressure fuel passes through the fitting portion between the cylinder 6 and the pump housing 1, the high pressure fuel can be stored in the low pressure fuel chamber. Therefore, the cylinder 6 can be fixed without being removed from the pump housing 1 due to the pressure difference.
- the upper end portion of the ceiling portion 6A of the cylinder 6 is brought into pressure contact with the ceiling portion 10A of the pump housing 1 by the pressure in the pressurizing chamber 11, and metal sealing is performed.
- the plunger seal 13 is held at the lower end of the spring holder 7 by the seal holder 15 and the spring holder 7 that are press-fitted and fixed to the inner peripheral cylindrical surface 7 c of the spring holder 7.
- the central axis of the plunger seal 13 is held coaxially with the central axis of the inner peripheral cylindrical surface 7c of the spring holder 7, and at the same time is held coaxially with the central axis of the cylindrical fitting portion 7e.
- the plunger 2 and the plunger seal 13 are slidably installed at the lower end portion of the cylinder 6.
- the plunger seal 13 prevents the fuel in the seal chamber 10f from flowing into the engine on the tappet 3 side. At the same time, lubricating oil (including engine oil) for lubricating the sliding portion in the engine room is prevented from flowing into the pump body 1.
- the spring holder 7 is fitted by an inner cylindrical surface (inner peripheral surface) portion provided at the lower part of the pump housing 1 and an outer cylindrical surface (outer peripheral surface) portion 7e of the spring holder 7, and in this embodiment, laser welding is used. It is fixed.
- a groove 7d for fitting the O-ring 61 is provided in the outer peripheral cylindrical surface 7b of the pump housing 1.
- the O-ring 61 blocks the engine cam side and the outside by the inner wall of the fitting hole 70 on the engine side and the groove 7d of the pump housing 1, and prevents the engine oil from leaking to the outside.
- the cylinder 6 can hold the plunger 2 moving forward and backward in the pressurizing chamber 11 so as to be slidable along the forward and backward movement direction.
- the lower end of the plunger 2 is provided with a tappet 3 that converts the rotational motion of the cam 5 attached to the camshaft of the engine into a vertical motion and transmits it to the plunger 2.
- the plunger 2 is pressure-bonded to the tappet 3 by a spring 4 via a retainer 15.
- the retainer 15 is fixed to the plunger 2 by press-fitting. As a result, the plunger 2 can be moved back and forth (reciprocated) up and down as the cam 5 rotates.
- the low-pressure fuel chamber 10c is connected to the seal chamber 10f via the suction channel 10d and the suction channel 10e provided in the cylinder holder 7, and the seal chamber 10f is always connected to the pressure of the intake fuel. ing.
- the fuel in the pressurizing chamber 11 is pressurized to a high pressure, a minute amount of high-pressure fuel flows into the seal chamber 10f through the sliding clearance between the cylinder 6 and the 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 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 fuel in the seal chamber 10f is always replaced with the sliding movement of the plunger 2, so that this fuel has an effect of removing generated heat.
- deformation of the large-diameter portion 2a due to frictional heat and the seizure and adhesion of the plunger 2 and the cylinder 6 generated thereby can be prevented.
- the friction area becomes smaller as the diameter of the sliding portion with the plunger seal 13 is smaller, the frictional heat generated by the sliding motion is also reduced.
- the amount of heat generated by friction with the plunger seal 13 can be kept small, and seizure sticking can be prevented.
- 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.
- FIG. 8 shows an external view of the flange 41 and the bush 43. In this figure, only the flange 41 and the bush 43 are shown, and other components are not shown.
- the two bushes 43 are attached to the flange 41 and attached to the opposite side of the engine.
- the two set screws 42 are screwed into respective screws formed on the engine side, and the two bushes 43 and the flange 41 are pressed against the engine to fix the high pressure fuel supply pump to the engine.
- FIG. 9 shows an enlarged view of the flange 41, the set screw 42, and the bush 43 part.
- the bush 43 has a collar portion 43a and a caulking portion 43b.
- the caulking portion 43 b is caulked and coupled to the mounting hole of the flange 41.
- the pump housing 1 and the welded portion 41a are welded together by laser welding.
- the resin fastener 44 is inserted into the bush 43, and the set screw 42 is inserted into the fastener 44.
- the fastener 44 serves to temporarily fix the set screw 42 to the bush 43. That is, the set screw 42 is fixed so as not to fall off the bush 43 until the high-pressure fuel supply pump is attached to the engine.
- the set screw 42 is screwed and fixed to a screw portion provided on the engine side. At that time, the set screw 42 is rotated in the bush 43 by the tightening torque of the set screw 42. it can.
- the pressure in the pressurizing chamber 11 repeats high pressure and low pressure as described above.
- a force acts so that the pump housing 1 is lifted upward in the figure due to this pressure. This force does not work when the pressure chamber 11 is at a low pressure. For this reason, the pump housing repeatedly receives a load upward in the drawing.
- the flange 41 fixes the pump housing 1 to the engine by two set screws 42. Therefore, when the pump housing 1 is lifted upward as described above, the flange 42 is in a state where the two set screws 42 and the bush 43 are fixed and a bending load is repeatedly applied to the central portion. Due to this repeated load, the flange 41 and the pump housing 1 are deformed, so that there is a problem in that repeated stress is generated and fatigue failure occurs. Furthermore, the sliding portion of the cylinder 6 is also deformed, and the above-described seizure and sticking between the plunger 2 and the cylinder 6 occurs.
- the flange 41 In order to weld through the flange 41 by laser welding, it is sufficient to increase the output of the laser. However, since heat is always generated during welding, the flange 41 is thermally deformed by the heat. Further, a large amount of spatter generated during welding is generated and fixed to the pump housing 1 and other components. From the above viewpoint, the welding length for through welding by laser welding is better.
- the flange 41a can be through-welded by laser welding, and the occurrence of spatter can be minimized.
- the upper end surface and the lower end surface of the welded part 41a are always raised more than the base material.
- the pump housing 1 when a repeated load is applied to the pump housing 1, it bends in the direction of the repeated load with the two set screws 42 and the bush 43 being fixed.
- the welded portion 41 a is welded through the entire circumference by laser welding, and the curvature of the flange 41 spreads to the pump housing 1.
- the cylinder holder 7 and the pump housing 1 are in contact only with the screws 7g and 1b.
- the screw 1b and the welded portion 41a of the pump housing 1 are present at a position where they want to be separated by a distance m.
- the minimum wall thickness at the distance m is n. Even if the pump housing 1 is deformed by the bending of the flange 41, the deformation is absorbed by the portion of the distance m and the wall thickness n, and the values of m and n are selected so as not to reach the screw 1b.
- FIG. 9 shows an enlarged view near the welded portion 41a.
- the maximum stress generated when the pump housing 1 is pulled upward in the figure by repeated load and the flange 41 is bent is the arrow on the surface of the pump housing 1 as shown as the maximum stress in FIG. Occurs in the direction.
- the generated stress may be dispersed by the shape effect as much as possible so that the stress concentration does not occur.
- the R portion 1c and the R portion 1e are connected by the straight portion 1d, and the optimum value is selected.
- the straight part 1d exists between the two R parts 1c and 1e, and the stress generated on the straight part 1d is evenly distributed. As a result, the maximum value of the generated stress could be reduced without causing stress concentration.
- the bending effective distance: O indicates the shortest distance between the end portions of the two bushes 43, and this portion is substantially bent by a repeated load. If the effective bending distance O can be reduced, the rigidity of the flange 41 is improved as a result.
- the bush 43 is provided with a flange portion 43a to reduce the bending effective distance: O.
- a height for inserting the fastener 44 is required.
- the outer shape of the bush 43 is increased at that height, there are problems such as interference with the pump housing 1 and an increase in the material of the bush 43.
- the spring holder 7A and the plunger seal holder 7B are separated and the outer shape of the pump housing 1 is reduced, thereby reducing the cost.
- a groove 7d for fitting the O-ring 61 is provided in the outer cylindrical portion 7b of the spring holder 7A.
- the O-ring 61 blocks the engine cam side and the outside by the inner wall of the engine-side fitting hole 70 and the groove 7d of the spring holder 7A, thereby preventing the engine oil from leaking to the outside.
- the plunger seal holder 7B and the cylinder holder 7A are fixed in advance before being fixed to the pump housing 1. In this embodiment, it is fixed by laser welding 7j, and the fuel is sealed.
- the outer peripheral cylindrical surface portion 7k of the spring holder 7A is press-fitted and fixed to the inner peripheral cylindrical surface portion of the pump housing 1, and further, the fuel is sealed by being fixed by laser welding 7h.
- the plunger seal 13 is held at the lower end of the spring holder 7A by a seal holder 15 and a spring holder 7A that are press-fitted and fixed to the inner peripheral cylindrical surface of the plunger seal holder 7B.
- the plunger seal 13 is held by the inner peripheral cylindrical surface 7c of the spring holder 7A so that its axis is coaxial with the axis of the cylindrical fitting portion 7e.
- the plunger 2 and the plunger seal 13 are slidably installed at the lower end of the cylinder 6 in the figure.
- the cylinder 6 is provided with two or more stepped portions 6f formed of a large diameter portion and a small diameter portion on the outer peripheral surface portion, and the stepped portion 6f is a cylinder machined coaxially with the inner cylindrical side surface (inner peripheral surface) of the cylinder 6.
- a groove 6g is provided.
- the sliding part 6m smaller than the large diameter part 2a of the plunger 2 is provided on the ceiling part 6A of the cylinder 6.
- the sliding portion 6m is processed coaxially with the sliding portion 6h of the large diameter portion 2a of the plunger 2.
- a small-diameter portion 2c is provided on the upper surface of the plunger 2 coaxially with the axis, and is fitted to a sliding portion 6m provided on the ceiling portion 6A of the cylinder 6, thereby increasing the sliding area between the plunger 2 and the cylinder 6.
- a plurality of lateral holes 6p serving as fuel passages (6a, 6b) penetrating the inside and outside are provided in the side surface of the cylinder 6, and the cylinder 6 is disposed in the lateral hole 6p as the fuel passages (6a, 6b). Two or more locations are provided at positions where fuel can be passed from the suction passage to the discharge passage regardless of the angle in the circumferential direction.
- This hole functions as an air vent hole when the cylinder cup is press-fitted. If there is no air vent hole, the press-fit load is in units of several tons. In that case, the body housing and the cylinder are deformed. In the embodiment, press-fitting is performed at a rating of 1 ton, usually 8000 N or less.
- the outer cylindrical portion (outer peripheral surface) of the cup-shaped cylinder member is press-fitted and fixed to the inner cylindrical portion (inner peripheral surface) of the pump housing.
- the cylinder is press-fitted with a force that prevents the cylinder from coming out of the pump housing due to the pressure difference between the outside and inside of the cylinder.
- the hole diameter D is set to a diameter satisfying “the area D of the hole D> the outer diameter area ADc of the cylinder ⁇ the outer diameter area Ad of the plunger”, it is possible to reliably eliminate the generation of a force that causes downward pressure due to the in-cylinder pressure. Can do.
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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)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
1A 凹所
2 プランジャ
6 シリンダ
6A 天井部(シリンダの)
10A 天井部(ポンプハウジングの)
11 加圧室
30 電磁吸入弁機構
Claims (10)
- 凹所が形成されたポンプハウジング、
当該ポンプハウジングの前記凹所に組み合わされ、ポンプの加圧室を画成するシリンダ、
前記シリンダに滑合し前記加圧室内の流体を加圧するプランジャを備え、
当該プランジャの往復動によって前記加圧室内に吸入される燃料を加圧して前記加圧室から吐出するものにおいて、
前記シリンダは天井部を有する円筒部材で形成されており、当該円筒部材の内側に前記加圧室が区画形成されており、
前記ポンプハウジングに形成される燃料吸入通路が前記シリンダを貫いて前記加圧室に達しており、前記ポンプハウジングに形成される燃料吐出通路が前記シリンダを貫いて前記加圧室に接続されている
高圧燃料供給ポンプ。 - 請求項1に記載のものにおいて、
前記シリンダの外周面部を前記ポンプハウジングの前記凹所の内周面部に嵌合することにより、前記シリンダを前記ポンプハウジングに固定するよう構成されている
高圧燃料供給ポンプ。 - 請求項1若しくは2のいずれかに記載したものにおいて、
前記ポンプハウジングの前記凹所の天井部に穴が開けられており、
前記当該穴が前記ポンプハウジングの前記凹所に嵌合される前記シリンダの前記天井部の外面で塞がれている
高圧燃料供給ポンプ。 - 請求項3に記載したものにおいて、
前記穴の径が前記シリンダの外径よりも小さく形成されている
高圧燃料供給ポンプ。 - 請求項1乃至4のいずれかに記載したものにおいて、
前記プランジャの圧縮動作によって前記シリンダの前記加圧室内に発生する圧力の反力が前記シリンダを前記ポンプハウジングの前記天井部の内壁面方向に押すように構成されている
高圧燃料供給ポンプ。 - 請求項1乃至5のいずれかに記載したものにおいて、
前記シリンダの外周面部と前記ポンプハウジングの内周面部との間にシール部が形成されている
高圧燃料供給ポンプ。 - 請求項6に記載したものにおいて、
前記シール部が前記シリンダの外周面部と前記ポンプハウジングの内周面部との間の金属接触によるメタルシール部として形成されている
高圧燃料供給ポンプ。 - 請求項1乃至7のいずれかに記載したものにおいて、
前記シリンダの外周面部に径の大きい部分と小さい部分で形成される二段以上の段差部を設け、当該段差部の径の大きいところで前記ポンプハウジングの内周面に嵌合するよう構成し、当該径の大きいところの内側部に環状の溝を設けた
高圧燃料供給ポンプ。 - 請求項1乃至8に記載したものにおいて、
前記シリンダの前記天井部に開口部を設け、前記プランジャの上端面に当該プランジャの最外径よりも径の小さい軸部を設け、前記開口部と前記軸部とが摺動するよう構成されている
高圧燃料供給ポンプ。 - 請求項1乃至9のいずれかに記載したものにおいて、
前記シリンダの側面部に内外を貫通する燃料通路としての横穴を二箇所以上を開口した
高圧燃料供給ポンプ。
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2013546837A JP5909502B2 (ja) | 2011-11-30 | 2011-11-30 | 高圧燃料供給ポンプ |
CN201180075234.7A CN103958880B (zh) | 2011-11-30 | 2011-11-30 | 高压燃料供给泵 |
DE112011105898.5T DE112011105898T5 (de) | 2011-11-30 | 2011-11-30 | Hochdruckkraftstoffpumpe |
US14/360,778 US10422330B2 (en) | 2011-11-30 | 2011-11-30 | High pressure fuel pump |
PCT/JP2011/006673 WO2013080253A1 (ja) | 2011-11-30 | 2011-11-30 | 高圧燃料供給ポンプ |
US16/576,000 US20200011314A1 (en) | 2011-11-30 | 2019-09-19 | High pressure fuel pump |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2011/006673 WO2013080253A1 (ja) | 2011-11-30 | 2011-11-30 | 高圧燃料供給ポンプ |
Related Child Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/360,778 A-371-Of-International US10422330B2 (en) | 2011-11-30 | 2011-11-30 | High pressure fuel pump |
US16/576,000 Continuation US20200011314A1 (en) | 2011-11-30 | 2019-09-19 | High pressure fuel pump |
Publications (1)
Publication Number | Publication Date |
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WO2013080253A1 true WO2013080253A1 (ja) | 2013-06-06 |
Family
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PCT/JP2011/006673 WO2013080253A1 (ja) | 2011-11-30 | 2011-11-30 | 高圧燃料供給ポンプ |
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US (2) | US10422330B2 (ja) |
JP (1) | JP5909502B2 (ja) |
CN (1) | CN103958880B (ja) |
DE (1) | DE112011105898T5 (ja) |
WO (1) | WO2013080253A1 (ja) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2015163243A1 (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 |
JP2016156287A (ja) * | 2015-02-23 | 2016-09-01 | 株式会社デンソー | ポンプ |
WO2018186219A1 (ja) * | 2017-04-07 | 2018-10-11 | 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 |
CN113302393A (zh) * | 2019-01-24 | 2021-08-24 | 卡特彼勒公司 | 燃料轨 |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10584668B2 (en) * | 2015-08-28 | 2020-03-10 | Hitachi Automotive Systems, Ltd. | High-pressure fuel pump and method for producing same |
DE102015220870A1 (de) * | 2015-10-26 | 2017-04-27 | Robert Bosch Gmbh | Hochdruckpumpe |
JP7295337B2 (ja) * | 2020-04-14 | 2023-06-20 | 日立Astemo株式会社 | 高圧燃料供給ポンプ及び製造方法 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH08296528A (ja) * | 1995-04-25 | 1996-11-12 | Yanmar Diesel Engine Co Ltd | 燃料噴射装置の調圧機構 |
JPH09250427A (ja) * | 1996-03-15 | 1997-09-22 | Zexel Corp | 燃料噴射ポンプ |
JP2010249006A (ja) * | 2009-04-15 | 2010-11-04 | Nico Precision Co Inc | ディーゼルエンジン用燃料噴射ポンプ |
Family Cites Families (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2940606C2 (de) * | 1979-10-06 | 1985-12-19 | Woma-Apparatebau Wolfgang Maasberg & Co Gmbh, 4100 Duisburg | Pumpenventilkopf für Hochdruckpumpen |
JP3467859B2 (ja) | 1994-09-20 | 2003-11-17 | 株式会社デンソー | 燃料噴射ポンプの油圧タイマ装置 |
DE19721227A1 (de) * | 1997-05-21 | 1998-11-26 | Bosch Gmbh Robert | Kolbenpumpe |
EP1471248B1 (en) * | 1999-02-09 | 2006-10-11 | Hitachi, Ltd. | High pressure fuel supply pump for internal combustion engine |
JP2001207852A (ja) | 2000-01-25 | 2001-08-03 | Kubota Corp | エンジンの副室式燃焼室 |
DE60139517D1 (de) * | 2001-01-05 | 2009-09-17 | Hitachi Ltd | Flüssigkeitspumpe und Hochdruckbrennstoffpumpe |
EP1348864A4 (en) | 2001-01-05 | 2005-03-16 | Hitachi Ltd | HIGH PRESSURE FUEL PUMP |
US6474127B1 (en) * | 2001-05-30 | 2002-11-05 | Edmonton Consultadoria E Servicios Lda | Pressing method, in particular for obtaining hydraulic cylinders and high-pressure filters |
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 |
CN1776215A (zh) * | 2004-11-16 | 2006-05-24 | 株式会社电装 | 高压燃料泵 |
JP4648254B2 (ja) * | 2006-06-22 | 2011-03-09 | 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 |
JP4625789B2 (ja) * | 2006-07-20 | 2011-02-02 | 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 |
JP2007231959A (ja) | 2007-06-15 | 2007-09-13 | Hitachi Ltd | 高圧燃料供給ポンプ |
JP5478051B2 (ja) * | 2008-10-30 | 2014-04-23 | 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 |
JP5124612B2 (ja) * | 2010-03-25 | 2013-01-23 | 日立オートモティブシステムズ株式会社 | 内燃機関の高圧燃料ポンプ制御装置 |
-
2011
- 2011-11-30 DE DE112011105898.5T patent/DE112011105898T5/de active Pending
- 2011-11-30 WO PCT/JP2011/006673 patent/WO2013080253A1/ja active Application Filing
- 2011-11-30 JP JP2013546837A patent/JP5909502B2/ja active Active
- 2011-11-30 CN CN201180075234.7A patent/CN103958880B/zh active Active
- 2011-11-30 US US14/360,778 patent/US10422330B2/en active Active
-
2019
- 2019-09-19 US US16/576,000 patent/US20200011314A1/en not_active Abandoned
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH08296528A (ja) * | 1995-04-25 | 1996-11-12 | Yanmar Diesel Engine Co Ltd | 燃料噴射装置の調圧機構 |
JPH09250427A (ja) * | 1996-03-15 | 1997-09-22 | Zexel Corp | 燃料噴射ポンプ |
JP2010249006A (ja) * | 2009-04-15 | 2010-11-04 | Nico Precision Co Inc | ディーゼルエンジン用燃料噴射ポンプ |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2015163243A1 (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 |
CN106255822A (zh) * | 2014-04-25 | 2016-12-21 | 日立汽车系统株式会社 | 高压燃料供给泵 |
JPWO2015163243A1 (ja) * | 2014-04-25 | 2017-04-13 | 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 |
CN106255822B (zh) * | 2014-04-25 | 2018-12-07 | 日立汽车系统株式会社 | 高压燃料供给泵 |
JP2016156287A (ja) * | 2015-02-23 | 2016-09-01 | 株式会社デンソー | ポンプ |
WO2018186219A1 (ja) * | 2017-04-07 | 2018-10-11 | 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 |
US10890151B2 (en) | 2017-04-07 | 2021-01-12 | Hitachi Automotive Systems, Ltd. | High-pressure fuel pump |
CN113302393A (zh) * | 2019-01-24 | 2021-08-24 | 卡特彼勒公司 | 燃料轨 |
Also Published As
Publication number | Publication date |
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CN103958880B (zh) | 2016-08-24 |
US20140314601A1 (en) | 2014-10-23 |
JPWO2013080253A1 (ja) | 2015-04-27 |
CN103958880A (zh) | 2014-07-30 |
DE112011105898T5 (de) | 2014-08-28 |
US10422330B2 (en) | 2019-09-24 |
JP5909502B2 (ja) | 2016-04-26 |
US20200011314A1 (en) | 2020-01-09 |
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