EP1557558B1 - Pompe d'alimentation en carburant et corps à structure poussoir - Google Patents

Pompe d'alimentation en carburant et corps à structure poussoir Download PDF

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Publication number
EP1557558B1
EP1557558B1 EP03758923.1A EP03758923A EP1557558B1 EP 1557558 B1 EP1557558 B1 EP 1557558B1 EP 03758923 A EP03758923 A EP 03758923A EP 1557558 B1 EP1557558 B1 EP 1557558B1
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EP
European Patent Office
Prior art keywords
fuel
plunger
pass
supply pump
fuel supply
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP03758923.1A
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German (de)
English (en)
Other versions
EP1557558A1 (fr
EP1557558A4 (fr
Inventor
Nobuo c/o Bosch Automotive Systems Corporation AOKI
Kazuya c/o Bosch Automotive Systems Corporation KUBOTA
Takeshi c/o Bosch Automotive Systems Corporation TERADA
Noriyuki c/o Bosch Automative Systems Corporation KOBAYASHI
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Bosch Corp
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Bosch Automotive Systems Corp
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Filing date
Publication date
Priority claimed from JP2002313763A external-priority patent/JP2004150290A/ja
Priority claimed from JP2003004013A external-priority patent/JP2004218459A/ja
Priority claimed from JP2003120627A external-priority patent/JP2004324536A/ja
Application filed by Bosch Automotive Systems Corp filed Critical Bosch Automotive Systems Corp
Publication of EP1557558A1 publication Critical patent/EP1557558A1/fr
Publication of EP1557558A4 publication Critical patent/EP1557558A4/fr
Application granted granted Critical
Publication of EP1557558B1 publication Critical patent/EP1557558B1/fr
Anticipated expiration legal-status Critical
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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
    • F02M63/02—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
    • F02M63/023—Means for varying pressure in common rails
    • F02M63/0235—Means for varying pressure in common rails by bleeding fuel pressure
    • F02M63/025—Means for varying pressure in common rails by bleeding fuel pressure from the common rail
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
    • 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
    • F02M59/462—Delivery valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0439—Supporting or guiding means for the pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift

Definitions

  • the present invention relates to a fuel supply pump and a tappet structure body. More specifically, the present invention relates to a fuel supply pump, for example, which is suitable for an accumulator fuel injection device that mechanically amplifies the pressure of a large flow rate of fuel through the use of a pressure amplifying piston, and to a tappet structure body.
  • JP 2885076 B has proposed an accumulator fuel injection device having a pressure-amplifying piston for amplifying the pressure of a fuel and a cylinder chamber, located between a pressure accumulator and a fuel injection valve.
  • an accumulator fuel injection device 380 that comprises: a pressure accumulator 395; an oil supply channel 360 for a fuel; an oil control channel 361; a switching valve 362 for fuel injection control; a pressure amplifying piston 378 for elevating the fuel pressure to 70 to 120 MPa (approximately 700 to 1, 200 kgf/cm 2 ); a cylinder chamber 383 for housing the pressure amplifying piston 378; a hydraulic circuit 363; a piston-work switching valve (three-way solid valve for amplifier) 364; and a controller (not shown).
  • the accumulator fuel injection device disclosed in JP 06-93936 A needs to be provided with two kinds of the pressure accumulator, their switching device, and so on. Therefore, there is a problem in that the accumulator fuel injection device is complicated and grown in size.
  • the lubricant prevents the movement of a plunger and fuel having a large flow rate cannot be pressurized sufficiently because of lubricant cannot travel forward and backward freely between a spring-holding member and a cam chamber when the cam and plunger of the fuel supply pump are driven at high speed. As the flow rate of fuel is restricted, a large amount of fuel cannot be pressurized sufficiently.
  • a pressure amplifying piston is placed between the pressure accumulator and the fuel injection valve to intend to provide a multi-stage pressure injection.
  • a pressure pump for supplying high-pressure fuel to the pressure accumulator is one of the conventional pressure pumps used for the conventional accumulator fuel injection devices. Any pressure pump, which intends to supply a large amount of high-pressure fuel, is not designed.
  • the present inventors has found out that, by providing a penetration portion between a spring-holding chamber and a cam chamber, a large amount of a fuel oil can be sufficiently pressurized even when the cam and the plunger are driven at high speed because of allowing a lubricant or a fuel for lubrication to move forward and backward without restraint.
  • an object of the present invention is to provide a fuel supply pump enough to pressurize fuel by driving a cam and a plunger at high speed without allowing a lubricant or a fuel for lubrication to inhibit the movement of a plunger even in the case of enlarging the amount of fuel discharged, and to provide a tappet structural body suitable for such a pump.
  • the lubricant or the fuel for lubrication in the spring-holding chamber can be transferred quickly and smoothly through the pass-through hole which cannot be closed by the roller.
  • the plunger moves down to inhale fuel, the lubricant or the fuel for lubrication in the cam chamber can be transferred quickly and smoothly to the spring-holding chamber through the pass-through hole formed in the roller body.
  • such a tappet structure body allows the cam and the plunger to be driven at high speed when the tappet structure body is used in the fuel supply pump. For instance, when the cam is driven quickly at a rotational frequency of 1,500 rpm or more, the lubricant or the fuel for lubrication inhibits the high-speed movement of the cam and the plunger less frequently than before. As a result, the lubricant or the fuel for lubrication inhibits the high-speed movements of the cam and the plunger less frequently than before, resulting in less exposure to heat generated by friction with a cam shaft.
  • a fuel supply pump 50 is equipped with a specific spring sheet 10 and a tappet structure body 6.
  • the spring sheet 10 comprises : a spring holding portion 12 for retaining a spring 68 used for pulling a plunger 54 of a fuel supply pump 50; and a plunger mounting portion 14 for mounting the tip portion 55 of the plunger 54 thereon.
  • a plurality of pass-through holes 16 is formed around the plunger mounting portion 14.
  • the tappet structure body 6 comprises a roller 29 and a roller body 28.
  • a plurality of pass-through holes 30b is formed in the roller body 28.
  • the configuration of the fuel supply pump is, but not specifically limited to, preferably one having a fuel supply pump 50 shown in Figs. 1 and 2 . That is, the fuel supply pump 50 is preferably constructed of a pump housing 52, a barrel (cylinder) 53, a plunger 54, a spring sheet 10, a tappet structure body 6, and a cam 60.
  • the plunger 54 slides reciprocally along the inside of the barrel 53 in the pump housing 52 in response to the rotary movement of the cam 60 to form a fuel compression chamber 74 for pressurizing fuel introduced therein.
  • two sets of the barrel (cylinder) 53 and the plunger 54 are installed in the pump housing 52.
  • two or more sets are preferably used.
  • the pump housing 52 is, as exemplified in Fig. 1 and Fig. 2 , an enclosure for housing the barrel (cylinder) 53, the plunger 54, the tappet structure body 6, and the cam 60.
  • the pump housing 52 has a shaft-inserting hole 92a opened from side to side in the horizontal direction and a cylindrical spaces 92b, 92c opened from end to end in the vertical direction.
  • the pump housing 52 is preferably provided with through-holes 97, 98 opened in the lateral directions of the cylindrical spaces 92b, 92c, respectively.
  • each of the through-holes 97, 98 is provided as an assembly of three hole portions (large, middle, and small holes) 97a-97c, 98a-98d with different pore sizes, concentrically arranged in a stepwise pattern.
  • the tip portions of guide pins 99 are press-inserted into the hole portion 97a, 98a to ensure high-precision positioning of the guide pins 99.
  • the hole portions 97b, 98b have their own functions of introducing the tip portions of the guide pins 99 into the hole portions 97c, 98c to press-insert the tip portions of the guide pin 99 into the hole portions 97c or 98c, respectively.
  • the hole portions 97a, 98a are preferably formed of threaded portions such that the guide pins 99 can be threadably fit into the hole portions 97a, 98a to press-insert the dip portions of the guide pins 99 into the hole portions 97a, 98a, respectively.
  • a plunger barrel 53 is, as exemplified in Fig. 1 and Fig. 2 , an enclosure for supporting the plunger 54 and constitutes a part of a fuel compression chamber (pump chamber) 74 for pressurizing a large amount of fuel at high pressures by the plunger 54. Therefore, the plunger barrel 53 is preferably attached to the upper opening portion of each of the cylindrical spaces 92b, 92c in the pump housing 52.
  • the conformation of the plunger barrel can be suitably changed so as to correspond to the respective types.
  • the plunger 54 is a principle structural component for pressurizing fuel at high pressures in the fuel compression chamber 74 formed in the plunger barrel 53. Therefore, the plunger 54 is preferably arranged so as to be capable of lifting and lowering movements in the plunger barrel 53 attached in each of the cylindrical spaces 92b, 92c formed in the pump housing 52 lifting and lower movement.
  • the plunger 54 is preferably provided with a pressure portion 54a for allowing the plunger 54 to be introduced into or pulled out of the inside of the fuel compression chamber 74.
  • the pressure portion 54a is designed such that the pressure portion 54a has a diameter smaller than the diameter of the plunger barrel 53.
  • a gap is preferably formed between the pressure portion 54a and a discharge valve 79 when the pressure portion 54a moves to the top dead center. This is because that the plunger 54 is driven at high speed to smoothly feed fuel to a common rail under pressure without allowing the pressure portion 54a to occlude the inlet of the discharge valve 79 even after pressurizing a large amount of fuel.
  • the plunger 54 is preferably formed in the shape of a round bar as a whole and provided with a collar portion 55 on its opposite end with respect to the pressure portion 54a to allow the plunger 54 to be smoothly driven at high speed in the plunger barrel 53. That is, it is preferable that the collar part 55 for locking is integrally formed on the external peripheral surface of the tip portion (lower end portion) of the cylindrical plunger 54. This is because that such a configuration of the plunger 54 can be easily and positively fixed in the opening portion 15 formed in the plunger mounting portion 14.
  • the plunger 54 is preferably constructed such that the plunger 54 is always forced to move toward the cam by a spring 68 for returning the plunger and moves upward in response to the rotary movement of the cam 60 to pressurize fuel in the fuel compression chamber 74.
  • the rotation frequencies of the cam and the plunger are preferably in the range of 1,500 to 4,000 rpm.
  • the rotation frequencies of the cam and the plunger are preferably in the range of 1 to 5 times higher than the rotation frequency of an engine.
  • the fuel compression chamber 74 is a small chamber in the plunger barrel 53, which is formed by a combination of the plunger barrel 53 and the plunger 54.
  • the fuel quantitatively introduced into the fuel compression chamber 74 through a fuel supply valve 73 can be pressurized efficiently and massively by driving the plunger 54 at high speed.
  • a spring sheet and a roller body described latter are provided with their respective pass-through holes and the corresponding pass-through holes are communicated with each other.
  • the pressurized fuel is supplied to a common rail 106 shown in Fig. 11 through the fuel discharge valve 79.
  • the spring sheet 10 comprises a spring holding portion 12 for retaining a spring to be used at the time of pulling down the plunger of the fuel supply pump and a plunger mounting portion 14 for catching the plunger.
  • a spring holding portion 12 for retaining a spring to be used at the time of pulling down the plunger of the fuel supply pump
  • a plunger mounting portion 14 for catching the plunger.
  • pass-through holes 16 for allowing passage of a lubricant or a fuel for lubrication are formed around the plunger mounting portion 14.
  • a spring holding protion12 is not specifically limited to as far as a spring used for pulling down the plunger of the fuel supply pump can be easily arranged. As shown in Figs. 6 and 7 , however, it may be of a disk shape or a planner body with portions partially protruded in the circumferential direction.
  • a groove or a hook may be preferably formed in or provided on part of the spring holding portion to embed or catch part of the spring.
  • the spring can be easily fixed and precisely disposed in place by means of bringing a coil spring (not shown) used for pulling down the plunger into contact with the surface 13 of the spring holding portion 12.
  • a plunger mounting portion is not limited to particular one as far as it is configured to easily catch the plunger and pull it down.
  • the plunger mounting portion is preferably a combination of a comparatively large insert hole 15b in which the tip portion of the plunger can be laterally inserted by sliding; a comparatively small central hole 15a for catching the tip portion of the plunger. That is, it is preferable that the width of the insert hole 15b of the opening 15 is larger than the diameter of the central hole 15a of the opening 15.
  • the opening 15 allows the spring sheet and the plunger to easily catch one another while easily centering them together without using any specific additional fixing device. Therefore, in the fuel supply pump, even at the time of drying the plunger at high speed, the displacement between the tappet structure body and the plunger can be lowered.
  • the plunger mounting portion 14 is constructed as above, as shown in Figs. 8(a) to (c) , a collar portion formed on the tip portion of the plunger 54 is allowed to pass through the insert hole 15b of the opening 15. Then, the collar portion is allowed to catch the rear surface of the plunger mounting portion 14 in the central hole 15a of the opening 15 to prevent them from pulling out.
  • plunger mounting portion may be preferably configured as modified examples shown in Figs. 8(a) to 8(c)
  • a plunger mounting portion 14 is shaped like a dish to form a fuel reserving portion 16b in the inner area of the spring holding portion 12.
  • a step 17 can be easily formed between the spring holding portion 12 and the side surface of the plunger mounting portion 14.
  • a fuel reserving portion is formed between them.
  • a lubricant or a fuel for lubrication can be freely fed therethrough. Therefore, the high speed driving of the plunger becomes less inhibited and exerts predetermined lubrication effects on the respective points.
  • a plunger mounting portion 14 is configured enough to easily mount the plunger thereon and formed in the inner region of the spring holding portion 12 without forming any fuel reserving portion 16b therein.
  • the spring sheet can be thinned. Therefore, the spring sheet can be handled and processed without difficulty.
  • Fig. 8 (c) shows another example in which a plunger mounting portion 14 is formed such that it extends directly to the inner area of the spring holding portion 12.
  • a plunger mounting portion 14 is formed such that it extends directly to the inner area of the spring holding portion 12.
  • the pass-through hole 16 of the spring sheet 10 and the pass-through hole 30b of the roller body 28 are aligned with each other to make a communication between them.
  • a lubricant or a fuel for lubrication can be freely fed therethrough. Therefore, the high speed driving of the plunger becomes less inhibited and exerts predetermined lubrication effects on the respective points.
  • the spring holding portion 12 is allowed, for example, to retain a cylindrical spring.
  • the plunger can be caught in the inner area of the spring and easily centered to allow the plunger to drive at high speed.
  • the height of the plunger mounting portion 14 is adjusted to make a step 17 between the spring holding portion 12 and the side surface of the plunger mounting portion 14.
  • the height of the step 17 is represented by the symbol t1.
  • the step has a height (t1) of 1 mm or more.
  • pass-through holes 16 formed around the plunger mounting portion 14 are not specifically limited.
  • circular pass-through holes are formed with a limited number of 1 to 20.
  • the number of the pass-through holes is preferably in the range of 2 to 15, more preferably in the range of 3 to 10.
  • the pass-through hole is substantially shaped in a circle, or it may be preferably shaped in another form such as an oval, square, irregular, or groove form.
  • the pass-through holes 16 are preferably arranged around the plunger mounting portion 14 in a radial pattern or in a semi-radial pattern.
  • the example shown in Fig. 6 and Fig. 7(a) there are five pass-through holes 16 arranged in a semi-radial pattern with respect to the central point P of the plunger mounting portion 14.
  • the pass-through holes 16 are preferably arranged in a semi-radial pattern while staying out of the opening 15.
  • each of the pass-through holes 16 exemplified in Fig. 6 and Fig. 7(a) is substantially in the shape of a circle, it is preferable that each of the pass-through holes has a diameter of 0.5 to 12 mm.
  • the diameter of the pass-through hole is more preferably in the range of 1 to 10 mm, still more preferably in the range of 1.5 to 6 mm.
  • plural pass-through holes may have their respective diameters different from each other.
  • the pass-through holes can be provided as a mixture of those having comparatively large diameters and those having comparatively small diameters.
  • the larger holes allow a lubricant or a fuel for lubrication to quickly pass therethrough and the smaller holes allow detailed controls on the amount or rate of a lubricant or a fuel for lubrication passed while reducing restraints on the formation or arrangement of these holes.
  • the pass-through holes are preferably provided as a mixture of those having comparatively large diameters of 2.5 mm or more and those having comparatively small diameters of less than 2.5 mm.
  • the pass-through holes having comparatively large diameters of 2.5 mm or more are formed in the plunger mounting portion and those having comparatively small diameters of less than 2.5 mm are formed in the spring holding portion.
  • a tappet structure body is not limited to a specific one as far as it cooperates with the spring sheet to form a penetration portion.
  • it may be constructed of the same constituents as those of the second embodiment described latter. Therefore, detained description thereof will be omitted.
  • a cam 60 is a main element for converting the rotary movement of a motor into the vertical motion of the plunger 54 through the tappet structure body 6. Therefore, preferably, the cam 60 is inserted and held rotatably in a shaft-inserting hole 92a via a bearing body. Then, it is constructed so as to be revolved by driving a diesel engine (cam shaft 3).
  • the outer peripheral surface of the cam 60 is preferably integrally provided with two cam portions 3a, 3b in parallel with each other with a predetermined distance in the axial direction and located below the cylindrical spaces 92b, 92c of the pump housing 52.
  • cam portions 3a, 3b are preferably arranged in parallel with each other with a predetermined distance oppositely in the circumferential direction.
  • a fuel inlet valve and a fuel outlet valve are arranged as exemplified in Fig. 5 and constituted as exemplified in Figs. 9 to 10 .
  • the fuel inlet valve 73 is preferably constructed of a valve main body 19 and a valve body 20 having a collar portion 20b on its tip portion.
  • the valve main body 19 is preferably provided with a cylindrical fuel inlet chamber 19a opened downward and a fuel inlet hole 19b for feeding fuel into the fuel inlet chamber 19a.
  • the fuel outlet valve 79 comprises a valve body and is housed in part of the pump housing. Then, preferably, the valve body is always energized by a spring in the valve-closing direction to supply a pressurized fuel to a common rail by opening and closing the valve.
  • each of the fuel inlet valve 73 and the fuel outlet valve 79 comprises the valve main body 19, the valve body 20 movably attached in the inside of the valve main body 19, the fuel inlet chamber 19a provided in the inside of the valve main body 19, the fuel inlet hole 19b, the sheet portion 23 mutually contacted with the valve body 20 and part of the valve main body 19.
  • two or more fuel inlet holes 19b are formed and arranged in a non-radial pattern with respect to the fuel inlet chamber 19a.
  • the fuel outlet valve as constructed above also supplies the common rail with fuel, for example, even at a flow rate of approximately 500 to 1,500 liters per hours quickly and quantitatively.
  • a lubrication system of the fuel supply pump preferably employs, but not specifically limited to, a fuel lubrication system that utilizes part of a fuel oil as a lubrication component (fuel for lubrication).
  • the lubrication component existed in the spring-holding chamber may tend to be mixed with part of the fuel leaked from a fuel-pressurizing chamber even the sealing property of the chamber is enhanced.
  • employing the fuel lubrication system prevents the lubrication component from becoming wax while keeping the ability of emission gas purification because they have the same composition.
  • the fuel supply pump of the first embodiment is preferably a part of an amplified mechanical common rail system 100 using a mechanical pressure amplifying system such as piston.
  • the fuel supply pump 103 is preferably constructed of a fuel tank 102, a feed pump (low pressure pump) 104 for supplying the fuel from the fuel tank 102, a fuel supply pump (high pressure pump) 103, a common rail 106 provided as a pressure accumulator for pressure-accumulation of the fuel fed under pressure from the fuel supply pump 103, a piston amplifier 108 (amplifying piston), and a fuel injection system 110.
  • the capacity and form of a fuel tank 102 exemplified in Fig. 11 are preferably defined in consideration of, for example, the circulation of fuel at a flow rate of approximately 500 to 1,500 liters per hour.
  • the feed pump 104 is, as shown in Fig. 11 , provided for feeding fuel (diesel oil) in the fuel tank 102 to the fuel supply pump 103 under pressure. It is preferable that a filter 105 is placed between the feed pump 104 and the fuel supply pump 103.
  • the feed pump 104 has a gear pump structure mounted on the end of the cam such that the feed pump 104 can be driven by directly connecting with the axis of the cam or through an appropriate gear ratio.
  • the fuel fed under pressure from the feed pump 104 through the filter 105 is preferably supplied to the fuel supply pump 103 through a proportional control valve (FMU) 120 for adjusting the amount of fuel injected as shown in Fig. 12 .
  • FMU proportional control valve
  • the proportional control valve 120 controls the amount of current passing through a coil 124 under the control of an electronic control unit (ECU) described later to proportionally adjust the position of an anchor 125.
  • ECU electronice control unit
  • the position of a piston 127 at the tip portion of the anchor 125 is adjusted in response to the position of the anchor 125, so that the fuel-passing area between a slit 122 formed in the piston 127 and the fuel supply portion 129 can be varied to control the fuel supplied to an inlet valve (not shown) in the fuel supply pump 103.
  • the fuel in addition to feed the fuel supplied from the feed pump 104 to the proportional control valve 120 and the fuel supply pump 103 under pressure, it is preferable to construct that the fuel is returned to the fuel tank 102 through a overflow valve (OFV) 134 installed in parallel with the proportional control valve 120. Moreover, it is preferable that part of the fuel is fed under pressure to a bearing (not shown) of the fuel supply pump 103 through an orifice 136 installed with the overflow valve 134 and then used as a fuel lubricating oil of the bearing.
  • OFV overflow valve
  • the fuel supply pump 103 is a device for pressurizing the fuel supplied from the feed pump 104 at high pressure as described above.
  • the fuel supply pump 103 is preferably constructed such that, after pressurizing the fuel, the fuel is fed to the common rail 106 under pressure through the high pressure channel 107.
  • a one way valve (not shown) on the outlet of the fuel supply pump 103, or both of the common rail 106 described below and the fuel supply pump 103.
  • the common rail 106 is connected to a plurality of injectors (injection valves) 110.
  • the accumulated pressure fuel at high pressure by the common rail 106 is injected into an internal combustion engine (not shown) from each of the injectors 110.
  • the amount of discharge from each of these injectors 110 is preferably controlled through an injector driving unit (IDU) .
  • the IDU is connected to an electrical controlling unit (ECU) provided as a controller described letter.
  • the IDU is driven by drive signals from the ECU.
  • a pressure detector 117 is connected to the side end of the common rail 106 and a pressure-detection signal obtained by the pressure detector 117 is preferably sent to the ECU. That is, it is preferable to control an electromagnetic control valve (not shown) and also control the drive of IDU in response to the pressure detected when the ECU receives the pressure-detection signal from the pressure detector 117.
  • a piston amplifier pressure amplifying piston
  • a piston amplifier is constructed of a cylinder 155, a mechanical piston 154, a compression chamber 158, an electromagnetic valve 170, and a circulation pathway 157.
  • the mechanical piston 154 is equipped with a pressure-receiving portion 152 having a comparatively large area and a pressure portion 156 having a comparatively small area.
  • the common rail pressure of the compression chamber 158 is preferably adjusted to one that allows fuel having a pressure of approximately 30 MPa to be pressurized by the pressure portion 156 having a comparatively small area to make the pressure of the fuel in the range of 150 to 300 MPa.
  • a large amount of fuel having the common rail pressure is used for pressurizing the mechanical piston 154.
  • the fuel pressurized by the pressure portion 156 is fed to a fuel injection system (fuel injection nozzle) 163, effectively injected, and combusted.
  • a fuel injection system fuel injection nozzle
  • the mechanical piston can be effectively pushed by the fuel having a common rail pressure without excessively increasing the size of the common rail.
  • a mechanical piston is equipped with a pressure-receiving portion having a comparatively large area and a pressure portion having a comparatively small area. While considering the stroke of the mechanical piston, it is possible to effectively pressurize the fuel having the common rail pressure to a desired level with a small pressure. More concretely, the fuel from the common rail (pressure: p1, volume: V1, workload: W1) can be received by a pressure-receiving portion having a comparatively large area and then changed to higher-pressure fuel (pressure: p2, volume: V2, work load: W2) by a mechanical piston equipped with a pressure portion having a comparatively small area.
  • the configuration of the fuel injection system (fuel injection nozzle) 110 is, but not specifically limited to, preferably constructed as follows: As shown in Fig. 13 , for example, the fuel injection system 110 comprises a nozzle body 163.
  • the nozzle body 163 includes: a seat surface 164 on which a needle valve body 162 can be placed; and an injection hole 165 formed on the downstream side from the valve body abutting portion of the seat surface 164.
  • it is constructed that the fuel supplied from the upstream side of the seat surface 164 at the time of lifting a needle valve body 162 is introduced into the injection hole 165.
  • such a fuel injection nozzle system 166 is preferably of an electromagnetic valve type, in which the needle valve body 162 is always energized toward the seat surface 164 by the spring 161 and opens and shuts the needle valve body 162 by switching energization / no energization of solenoid 180.
  • timing chart of high-pressure fuel injection it is preferable to indicate a fuel injection chart having two-staged injection conditions as indicated by the solid line as indicated by the solid line A in Fig. 15 .
  • a fuel injection chart as indicated by the dashed line B in Fig. 15 , a combination of the common rail pressure and amplification with a piston amplifier.
  • the conventional injection timing chart becomes a single-stage injection timing chart with a low injection amount as indicated by the dashed line C in Fig. 15 .
  • the fuel supply pump 103 the actions of the piston amplifier 108, and the fuel injection valve 110 in the first embodiment will be described. That is, as shown in Fig. 11 , at the time of operating the fuel injection system (fuel injection nozzle system) 166, the fuel in the fuel tank 102 is supplied from the feed pump 104 to the fuel supply pump 103. Furthermore, the high-pressure fuel is preferably supplied from the fuel supply pump 103 to the high pressure channel 107 under pressure.
  • the fuel is subjected to pressure accumulation at approximately 50 MPa in the common rail 106 and then the fuel is preferably pressurized under ultra-high pressure conditions of 150 MPa or more as the piston amplifier 108 is provided between the common rail 106 and the fuel injection valve 110.
  • a tappet structure body 6 having a roller 29 and a roller body 28 wherein the roller body 28 is provided with a pass-through hole 30b for allowing the passage of a lubricant or a fuel for lubrication such that the pass-through hole 30b penetrates from the upper surface portion to a non-roller portion of the roller body 28.
  • the basic configuration of the tappet structure body 6 and the roller body 28 having the pass-through hole 30b will be more concretely described with reference to the drawings as necessary.
  • the tappet structure body 6 is essentially constructed of a shell 27, the roller body 28, and the roller 29. It is preferably constructed to move up and down by the rotary movement of a cam shaft 3 and a cam 60 connected thereto shown in Fig 1 . Still, Fig. 17 and Fig. 18 show the modified example of a tappet structure body 6 containing a shell 27 and a spring sheet 10, and Fig. 19 and Fig. 20 show the modified example of a tappet structure body 6 containing a shell 27, each of which are preferably used.
  • the shell 27 opens from side to side in the vertical direction and forms a cylindrical body having the outer peripheral surface fitted to the peripheral surface of cylindrical spaces 92b and 92c of a pump housing 52 shown in Fig. 3 .
  • an opening (slit) 27a into which a guide pin inserts, is provided and formed as a through-hole extending in the axis direction of the shell 27. This is because the guide pin and the opening 27a cooperate to move up and down along the axis of the cylindrical spaces 92b and 92c for maintaining the movement of the tappet structure body 6 in the required direction, when the tappet structure body 6 moves up and down.
  • a first protruded portion 27b is preferably provided for restricting the upward movement of the roller body 28.
  • a second protruded portion 27c is provided integrally therewith for guiding the outer peripheral surface of a spring 68. This is because the roller body 28 is not required to have any function for restricting the movement of the spring sheet 26 in the radial direction and is thus allowed to have a simple shape.
  • the roller 29 is rotationally supported by a roller support 30a, the whole surface of which is applied with carbon treatment, for example a carbon coating. Additionally, the roller 29 is constructed to receive the rotation force of the cam 60 communicating into the cam shaft 3. This is because the sliding between the roller 29 and the roller support 30a can be controlled by the carbon treatment applied to the roller support 30a, and thereby, through the roller 29, the rotation force of the cam 60 can be transferred to the roller support 30 which is a part of the roller body 28, to be efficiently exchanged into the reciprocal movement of a plunger.
  • carbon treatment for example a carbon coating
  • the tappet structure body 6 as constructed above can reciprocally move at high speed repeatedly for the long term in response to the rotation of the cam 60 communicating into the cam shaft 3.
  • the roller body 28 preferably has a main body 30 and is held within the shell 27.
  • its whole body is formed by a plane round-shaped block body composed of a bearing steel.
  • Fig. 21 to Fig. 24 shows the modified example of a roller body 28, each of which can be preferably used.
  • the roller support 30a having the inner peripheral surface fitted to the outerperipheral surface of the roller 29. Furthermore, on the central portion of the upper surface of the main body 30, a contact portion 30c is provided integrally with the plunger 54 and protrudes toward the plunger 54. Preferably, on the peripheral portion of the main body 30, a sheet receiver 30d for receiving the spring sheet 26 is provided integrally therewith to protrude.
  • the number and the shape of the pass-through hole provided on the roller body is not especially limited.
  • the number of the pass-through hole provided in the round shape is preferably in the range of one to ten.
  • the lubricant or the fuel for lubrication at the side of the spring can be efficiently transferred into the cam side, taking the size and the arrangement thereof into consideration, even if the number of the pass-through hole is one.
  • the pass-through holes more than 10 in number may have a difficulty with the arrangement in the roller body and the formation thereof.
  • the number of the pass-through hole is in the range of two to eight, more preferably in the range of two to six.
  • the number of the pass-through hole of the roller body is preferably equal to or less than that of the pass-through hole of the spring sheet.
  • the pass-through hole is preferred to be in the round shape substantially or otherwise in the shape of an ellipse, rectangle, deformation, or groove.
  • the pass-through hole 30b provided on the roller body 28 is arranged around the roller body in a radial pattern. Still, in an example shown in Fig. 16(b) , two pass-through holes 30b are arranged at the symmetric position with respect to the central protruded portion 30c.
  • the formation of the respective pass-through holes can be facilitated and further the decline in the mechanical strength of the roller body can be declined.
  • the pass-through holes 30b are preferably provided to diagonally penetrate from the upper surface portion to a non-roller portion of the roller body 28, for example to a side surface portion.
  • the diameter of the pass-through hole 30b shown in Fig. 16 (b) and Fig. 21 is preferably defined in consideration of a fuel-passing amount per unit time and so on. If the pass-through hole 30b is substantially in the round shape, its diameter is preferably in the range of 0.5 to 12 mm.
  • the lubricant or the fuel for lubrication may have a difficulty to move forward and backward freely if the pass-through hole has a diameter less than 0.5 mm.
  • the pass-through hole has a diameter more than 12 mm, the mechanical strength and the durability of the roller body may be reduced.
  • the pass-through hole preferably has a diameter in the range of 1 to 10 mm, more preferably in the range of 2 to 6 mm.
  • the above pass-through hole 30b is preferably provided to penetrate from the upper surface portion to non-roller portion of the roller body 28.
  • the above pass-through hole 30b is preferably provided to penetrate from the upper surface portion to a non-roller portion of the roller body 28.
  • a channel 35 is preferably provided on the area including the lower-side opening of the pass-through hole 30b to pass the lubricant or the fuel for lubrication through the channel 35.
  • forming the cannels on the upper and lower portion of the roller body respectively allows fuel to be sufficiently pressurized without inhibiting the movement of the plunger by the lubricant or the fuel for lubrication even in the case of driving the cam and the plunger in the fuel supply pump at high speed and enlarging the amount of fuel discharged.
  • both of (or either of) the contact surfaces of the roller body and the plunger are preferred to be a curved surface structure.
  • the both of (or either of) the contact surfaces of the roller body 28 and the plunger 54 is preferred to be the curved surface structure having the radius of curvature in the range of, for example 30 mm to 2,000 mm.
  • the predetermined penetration portion is provided.
  • the lubricant or the fuel for lubrication is allowed to pass through between the spring-holding chamber and the cam chamber quickly and smoothly.
  • the spring sheet having a certain pass-through hole and the tappet structure body is cooperated. Thereby even a large amount of the lubricant or the fuel for lubrication is allowed to pass through quickly and smoothly.
  • the fuel supply pump of the present invention along with the common rail can be suitably used as a fuel supply pump applied to an accumulator fuel injection device (APCRS: Amplified Piston Common Rail System) which mechanically pressurizes fuel through a piston and so on utilizing for example a large flow rate of fuel.
  • APCRS Amplified Piston Common Rail System
  • the predetermined pass-through hole is provided. Therefore, pressure pulsation due to the plunger driven at high speed can be decreased and even a large amount of the lubricant or the fuel for lubrication is allowed to pass through quickly and smoothly.
  • the tappet structure body of the present invention is used for the fuel injection system having a pressure-amplifying fuel supply pump which mechanically pressurizes a large flow rate of fuel, a large amount of the lubricant or the fuel for lubrication can move forward and backward freely between the spring side and the cam side through the predetermined pass-through hole. Therefore, the plunger can be easily driven at high speed without inhibiting the movement of the plunger by the lubricant or the fuel for lubrication.

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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)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (8)

  1. Pompe d'alimentation en carburant comprenant un corps à structure poussoir (6) et une tôle bleue (10),
    une partie de pénétration pour permettre le passage d'un lubrifiant ou d'un carburant pour lubrification à travers celle-ci étant prévue entre une chambre de maintien de ressort pour maintenir un ressort devant être utilisé pour remonter un piston (54) et une chambre de came pour loger une came devant être utilisée pour déplacer le piston (54) vers le haut et vers le bas, caractérisée par le fait que
    le corps à structure poussoir (6) comprend un galet (29) qui coulisse et un corps de galet (28), ledit galet (29) est supporté de manière rotative par un support de galet (30a) dans le corps de galet (28),
    un trou traversant (30b) pour permettre le passage du lubrifiant ou du carburant pour lubrification à travers celui-ci, est formé dans le corps de galet (28) et prévu comme appartenant à la partie de pénétration, et
    le trou traversant (30b) pénètre depuis un côté de la chambre de maintien de ressort d'une surface supérieure du corps de galet (28) jusqu'à une position qui est ouverte sur un côté de la chambre de came et jusqu'à une position de non-coulissement de galet.
  2. Pompe d'alimentation en carburant selon la revendication 1, dans laquelle
    la tôle bleue (10) comprend :
    une partie de maintien de ressort (12) pour maintenir un ressort (68) devant être utilisé pour tirer vers le bas le piston (54) de la pompe d'alimentation en carburant ; et
    une partie de montage de piston (14) pour attraper le piston (54),
    un trou traversant (30b) étant formé autour de la partie de montage de piston (14) et prévu comme appartenant à la partie de pénétration.
  3. Pompe d'alimentation en carburant selon la revendication 2, dans laquelle une pluralité des trous traversants (30b) sont formés et disposés autour de la partie de montage de piston (14) en un motif radial ou un motif semi-radial.
  4. Pompe d'alimentation en carburant selon l'une quelconque des revendications 1 à 3, dans laquelle une pluralité des trous traversants (30b) sont formés dans le corps de galet (28) et disposés dans une direction périphérique du corps de galet (28).
  5. Pompe d'alimentation en carburant selon l'une quelconque des revendications 1 à 4, dans laquelle un canal (33) pour permettre le passage d'un lubrifiant ou d'un carburant pour lubrification à travers celui-ci est formé dans une zone comprenant une ouverture du trou traversant (30b) sur une surface supérieure du corps de galet (28).
  6. ompe d'alimentation en carburant selon l'une quelconque des revendications 1 à 5, dans laquelle un canal (35) pour permettre le passage d'un lubrifiant ou d'un carburant pour lubrification à travers celui-ci est formé dans une zone comprenant une ouverture du trou traversant (30b) sur le côté inférieur de celui-ci.
  7. Pompe d'alimentation en carburant selon l'une quelconque des revendications 1 à 6, dans laquelle un système de lubrification par carburant utilisant une partie d'un fioul comme carburant pour lubrification est utilisé et la partie de pénétration permet le passage du carburant pour lubrification à travers celui-ci.
  8. Pompe d'alimentation en carburant selon l'une quelconque des revendications 1 à 7, dans laquelle la pompe d'alimentation en carburant est utilisée dans un dispositif d'injection de carburant à accumulation pour mettre sous pression du carburant à un débit de 500 à 1500 litres par heure à une valeur de 50 MPa ou plus.
EP03758923.1A 2002-10-29 2003-10-27 Pompe d'alimentation en carburant et corps à structure poussoir Expired - Lifetime EP1557558B1 (fr)

Applications Claiming Priority (7)

Application Number Priority Date Filing Date Title
JP2002313763 2002-10-29
JP2002313763A JP2004150290A (ja) 2002-10-29 2002-10-29 燃料供給用ポンプおよびタペット構造体
JP2003004013A JP2004218459A (ja) 2003-01-10 2003-01-10 燃料供給用ポンプおよびタペット構造体
JP2003004013 2003-01-10
JP2003120627A JP2004324536A (ja) 2003-04-24 2003-04-24 燃料供給用ポンプおよびタペット構造体
JP2003120627 2003-04-24
PCT/JP2003/013688 WO2004040121A1 (fr) 2002-10-29 2003-10-27 Pompe d'alimentation en carburant et corps a structure poussoir

Publications (3)

Publication Number Publication Date
EP1557558A1 EP1557558A1 (fr) 2005-07-27
EP1557558A4 EP1557558A4 (fr) 2006-12-06
EP1557558B1 true EP1557558B1 (fr) 2018-01-31

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EP (1) EP1557558B1 (fr)
KR (1) KR100674772B1 (fr)
AU (1) AU2003275677A1 (fr)
WO (1) WO2004040121A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100738770B1 (ko) * 2004-01-14 2007-07-12 봇슈 가부시키가이샤 연료 공급용 펌프
EP2050956B1 (fr) 2007-10-18 2012-12-12 Delphi Technologies Holding S.à.r.l. Ensemble de pompe
DE102008001871A1 (de) * 2008-05-20 2009-11-26 Robert Bosch Gmbh Kraftstoffhochdruckpumpe
DE102008043436A1 (de) * 2008-11-04 2010-05-06 Robert Bosch Gmbh Kolbenpumpe mit einem Kolbenhalter
DE102010063328A1 (de) * 2010-12-17 2012-06-21 Robert Bosch Gmbh Hochdruckpumpe
DE102012205747A1 (de) * 2012-04-10 2013-10-10 Schaeffler Technologies AG & Co. KG Pumpenelement
KR101349642B1 (ko) * 2012-04-19 2014-01-10 (주)모토닉 내연기관의 고압펌프
EP2660459B1 (fr) * 2012-05-03 2016-04-06 Delphi International Operations Luxembourg S.à r.l. Réduction de charge
KR101371897B1 (ko) 2012-09-05 2014-03-07 현대자동차주식회사 윤활성능이 개선된 고압연료펌프
ITMI20122075A1 (it) * 2012-12-05 2014-06-06 Bosch Gmbh Robert Unita' di pompaggio per alimentare combustibile, preferibilmente gasolio, ad un motore a combustione interna
DE102014220881A1 (de) * 2014-10-15 2016-04-21 Continental Automotive Gmbh Rollenstößelvorrichtung und Verfahren zur Herstellung einer Rollenstößelvorrichtung
CN104791094A (zh) * 2015-03-11 2015-07-22 肖光宇 一种活塞往复式单缸内燃发动机
CN106065837B (zh) * 2016-07-16 2018-07-27 肖光宇 活塞往复内燃机综合调控系统

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Publication number Priority date Publication date Assignee Title
JPS61134566U (fr) * 1985-02-12 1986-08-22
JPH094542A (ja) * 1995-06-20 1997-01-07 Nippondenso Co Ltd 燃料供給装置
US5775203A (en) * 1997-01-28 1998-07-07 Cummins Engine Company, Inc. High pressure fuel pump assembly
DE19729793A1 (de) * 1997-07-11 1999-01-14 Bosch Gmbh Robert Kolbenpumpe zur Kraftstoffhochdruckversorgung
JP2001221131A (ja) * 2000-02-07 2001-08-17 Bosch Automotive Systems Corp 噴射ポンプのタペット潤滑機構

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WO2004040121A1 (fr) 2004-05-13
EP1557558A1 (fr) 2005-07-27
EP1557558A4 (fr) 2006-12-06
AU2003275677A1 (en) 2004-05-25
KR100674772B1 (ko) 2007-01-25
KR20050042081A (ko) 2005-05-04

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