US20150300338A1 - Pump for Supplying High-Pressure Fuel - Google Patents

Pump for Supplying High-Pressure Fuel Download PDF

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Publication number
US20150300338A1
US20150300338A1 US14/439,419 US201314439419A US2015300338A1 US 20150300338 A1 US20150300338 A1 US 20150300338A1 US 201314439419 A US201314439419 A US 201314439419A US 2015300338 A1 US2015300338 A1 US 2015300338A1
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US
United States
Prior art keywords
cylinder
plunger
pressure fuel
pump
supplying high
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.)
Abandoned
Application number
US14/439,419
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English (en)
Inventor
Shunsuke ARITOMI
Kenichirou Tokuo
Satoshi Usui
Shingo Tamura
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Astemo Ltd
Original Assignee
Hitachi Automotive Systems Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Hitachi Automotive Systems Ltd filed Critical Hitachi Automotive Systems Ltd
Assigned to HITACHI AUTOMOTIVE SYSTEMS, LTD. reassignment HITACHI AUTOMOTIVE SYSTEMS, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: TAMURA, SHINGO, ARITOMI, SHUNSUKE, TOKUO, Kenichirou, USUI, SATOSHI
Publication of US20150300338A1 publication Critical patent/US20150300338A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
    • F04B19/20—Other positive-displacement pumps
    • F04B19/22—Other positive-displacement pumps of reciprocating-piston type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M59/442—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 means preventing fuel leakage around pump plunger, e.g. fluid barriers
    • 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
    • F04B1/0421—Cylinders
    • 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
    • F04B1/0448—Sealing means, e.g. for shafts or housings

Definitions

  • the present invention relates to a pump for supplying high-pressure fuel which supplies a fuel at high-pressure to an internal combustion engine.
  • a plunger reciprocates to pressurize the fuel in the pressurizing chamber, and therefore the inner wall face of the cylinder which guides the reciprocating movement of the plunger and the external wall face of the plunger serve as sliding portions.
  • Patent Literature 1 a cylinder which is formed by a separate component from a body is provided as a wall for guiding the plunger.
  • the patent document discloses a method for fixing the cylinder by pressing the cylinder into the body, forming a low-pressure fuel portion on the outer periphery of the sliding portion which slides against the plunger and cooling the sliding portion.
  • Patent Literature 2 discloses a method for fixing the cylinder which is formed as a separate member from the body by holding the cylinder between the body and a holder member.
  • the cylinder which guides the reciprocating movement of the plunger When the cylinder which guides the reciprocating movement of the plunger is formed as a separate member from the body, it is necessary to secure this cylinder to the body.
  • the cylinder When an external force is applied from the outside to the outer peripheral side face of the cylinder, the cylinder may be deformed and part or all of the inner peripheral side face (inner wall face) of the cylinder may contract. Since the cylinder guides the reciprocating movement of the plunger, it is necessary that the inner peripheral surface of the cylinder and the outer peripheral surface of the plunger form a sliding portion, ensuring a predetermined gap (clearance). If this gap is too large, fuel leakage from the pressurizing chamber increases and prevents sufficient pressurization, while too small a gap causes excessive frictional resistance in the sliding portion. Therefore, the gap in the sliding portion must be precisely managed.
  • the external force applied from the outside to the cylinder occurs, for example, when the cylinder is pressed into the body in fixing the cylinder. Further, the pressure generated by the fuel pressurized in the pressurizing chamber acts on the outer periphery of the cylinder, and acts as an external force which contracts part or all of the inner diameter of the cylinder.
  • An object of the present invention is to propose a structure which is capable of suppressing deformation of the sliding portion, and to provide a highly reliable high-pressure fuel pump.
  • the invention is a pump for supplying high-pressure fuel including a plunger for pressurizing a fuel in a pressurizing chamber, a cylinder which guides the reciprocating movement of the plunger on an inner peripheral side face thereof, a body on which the cylinder is arranged, and a holder member which fixes the cylinder to the body by urging the cylinder in the axial direction, characterized in that a sealing portion is formed by pressing an end of the cylinder on the pressurizing chamber side against the body.
  • a sealing portion formed by press-fitting the cylinder and the body prevents the fuel pressurized in the pressurizing chamber from leaking to the outer peripheral side face of the cylinder, and therefore the pressure of the pressurized fuel in the outer peripheral side face of the cylinder does not act as an external force to tighten the cylinder. Further, since the cylinder is fixed to the body by the holder member, an external force to tighten the cylinder when the cylinder is pressed into the body does not work. Therefore, the deformation of the inner peripheral side face of the cylinder, which is a sliding portion between the cylinder and the plunger, can be suppressed, and the reliability of the pump for supplying high-pressure fuel can be increased.
  • FIG. 1 shows the overall constitution of a system for carrying out first to third embodiments.
  • FIG. 2 shows a cross-sectional view of components around the cylinder (at top dead center) according to the first embodiment of the present invention.
  • FIG. 3 shows a cross-sectional view of components around the cylinder (at top dead center) according to the second embodiment of the present invention.
  • FIG. 4 shows a cross-sectional view of components around the cylinder (at top dead center) according to the second embodiment of the present invention.
  • FIG. 5 shows a cross-sectional view of components around the cylinder (at top dead center) according to the third embodiment of the present invention.
  • FIG. 6 shows a cross-sectional view of components around the cylinder (at top dead center) according to the third embodiment of the present invention.
  • FIG. 1 shows the overall constitution of a system for carrying out first to third embodiments.
  • a pump for supplying high-pressure fuel integrally incorporates a plurality of parts and mechanisms in a body 1 , and is attached to a cylinder head 20 of an internal combustion engine.
  • a fuel suction passage 10 In the body 1 , a fuel suction passage 10 , a pressurizing chamber 11 , and a fuel discharge passage 12 are formed.
  • an electromagnetic valve 5 and a discharge valve 8 are provided, and the discharge valve 8 serves as a check valve to restrict the flow direction of the fuel.
  • a plunger 2 is slidably inserted into a cylinder 120 , and a retainer 3 is attached to the lower end of the same.
  • the urging force of a return spring 4 acts on the retainer 3 in the downward direction in FIG. 1 .
  • a tappet 6 reciprocates in the vertical direction in FIG. 1 by the rotation of a cam 7 of the internal combustion engine.
  • the plunger 2 is displaced following the tappet 6 , which changes the capacity of the pressurizing chamber 11 to allow pumping action.
  • the electromagnetic valve 5 is held by the body 1 , and an electromagnetic coil 500 , an anchor 503 , an anchor spring 502 , and a valve spring 504 are disposed thereon.
  • An urging force of the anchor spring 502 acts on a valve body 501 in the valve opening direction via the anchor 503
  • the urging force of the valve spring 504 also acts in the direction of closing the valve.
  • the urging force of the anchor spring 502 is greater than that of the valve spring 504 , when the electromagnetic coil 500 is turned off (not energized), the valve body 501 is in an open state.
  • This system of the electromagnetic valve will be referred to as a normal open system since it is in the open state when the electromagnetic coil is turn off and is in the closed state when the coil is turned on.
  • the first to third embodiments can be similarly carried out based on a system using an electromagnetic valve system referred to as a normal closed system in which the operation is reversed, that is, the valve body 501 is in the closed state when the electromagnetic coil 500 is turned off (not energized).
  • valve body 501 and the anchor 503 are separate bodies, but the first to third embodiments can be similarly carried out based on the case where the components are integrally formed.
  • An injector 54 and a pressure sensor 56 are mounted on a common rail 53 .
  • the injector 54 is amounted to suit the number of cylinders of the engine, and injects fuel at the signals from an engine control unit (ECU 40 ).
  • ECU 40 engine control unit
  • suction stroke The state in which the plunger 2 is displaced downwardly in FIG. 1 by the rotation of the cam 7 of the internal combustion engine is referred to as a suction stroke, while the state in which the plunger is displaced upwardly is referred to as a compression stroke.
  • suction stroke the capacity of the pressurizing chamber 11 increases, and the fuel pressure therein is reduced.
  • this stroke when the fuel pressure in the pressurizing chamber 11 becomes lower than that in the low-pressure passage 9 , the valve body 501 opens, and fuel is drawn into the pressurizing chamber.
  • the electromagnetic coil 500 When the electromagnetic coil 500 is energized in the return stroke, the magnetic attraction acts on the anchor 503 , and the anchor 503 moves in the closing direction by overcoming the urging force of the spring anchor 502 . Then, the valve 501 is closed by the urging force of the valve spring 504 and the difference in the fluid pressure of the returning fuel. Then, immediately thereafter, the fuel pressure in the pressurizing chamber 11 is increases as the plunger 2 elevates. The discharge valve 8 opens automatically accordingly, and the fuel is pumped to the common rail 53 .
  • the flow rate of discharge of the pump can be controlled by adjusting the timing for the electromagnetic coil 500 to be turned on.
  • FIG. 2 shows a cross-sectional view of components around the cylinder 120 according to the first embodiment of the present invention. It also shows the case where the plunger 2 is positioned at the top dead center.
  • 1 represents a body, 2 a plunger, 120 a cylinder, 121 a holder member, 123 a sealing member, 4 a return spring, and 3 a retainer respectively.
  • the holder member 121 is coupled to the body 1 via a coupling portion 126 .
  • the coupling portion 126 is formed by screw fastening, press-fitting, or welding.
  • a holding unit 133 which is a part of the cylinder 120 , is urged in the direction of the body 1 by the body holder 121 , and a high-pressure sealing portion 124 is formed in the contact portion between the cylinder 120 and body 1 .
  • the pressurizing chamber 11 side of the high-pressure sealing portion 124 will be defined to as a high-pressure side, while the opposite side will be defined as a low-pressure side.
  • a sliding portion 125 is provided on the low-pressure side of the high-pressure sealing portion 124 in the cylinder 120 , and the plunger 2 is inserted into the cylinder 120 and supported by the sliding portion 125 .
  • the cylinder is not present in the pressurizing chamber, and therefore the pressure of the high-pressure fuel does not act on the cylinder and sliding portion, and deformation thereof can be suppressed. Further, since the cylinder 120 is fixed by the urging force in the axial direction with respect to the cylinder 120 and the high-pressure sealing portion 124 is formed, the deformation of the sliding portion 125 caused by an external force in fixing can be suppressed.
  • a small-diameter portion 129 and a large-diameter portion 128 are provided on the plunger 2 , and a low-pressure fuel portion 132 , of which volume increases or decreases by the reciprocating movement of the same, is formed on the outer periphery thereof.
  • the low-pressure fuel portion 132 is composed of a main low-pressure fuel portion 130 in contact with the plunger 2 , and a secondary low-pressure fuel portion 127 formed on the outer periphery of the cylinder 120 , both of which are connected to each other by a fuel passage slit 131 . Further, the secondary low-pressure fuel portion 127 is connected to a damper chamber 51 by a damper chamber passage (not shown).
  • the sealing member 123 is fixed to the holder member 121 , and the plunger 2 is inserted at the center of the same. Accordingly, even when the plunger 2 makes a reciprocating movement, the fuel does not leak from the low-pressure fuel portion 132 to the outside.
  • the discharge pressure and the external force in fixing do not act on the outer periphery of the cylinder 120 , and therefore even when the discharge pressure is increased to a high level, deformation of the cylinder 120 and the sliding portion 125 formed therein can be prevented, and the reliability of the sliding portion 125 can be increased.
  • FIG. 3 shows a cross-sectional view of components around the cylinder 120 according to the second embodiment of the present invention.
  • FIG. 3 also shows the case where the plunger 2 is located at the top dead center.
  • 1 represents a body, 2 a plunger, 120 a cylinder, 121 a holder member, 123 a sealing member, 4 a return spring, and 3 a retainer respectively.
  • a small-diameter portion 135 and large-diameter portion 134 are provided in the cylinder 120 , and the holding portion 133 is provided in the large-diameter portion 134 .
  • FIG. 3 shows, as an example, the case where the connecting portion between the small-diameter portion 135 and large-diameter portion 134 is formed by a stepped portion 122 having steps formed thereon.
  • the holding portion 133 as in the first embodiment, is urged in the direction of the body 1 by a holder member 121 coupled to the body 1 by a coupling portion 126 , and a high-pressure sealing portion 124 is formed in the contact portion between the body 1 and the cylinder 120 .
  • the cylinder 120 is provided with a sliding portion 125 on the low-pressure side of the high-pressure sealing portion 124 , as in the first embodiment.
  • the holding portion 133 which receives the urging force can be thick for securing the strength, and the outer periphery of the sliding portion 125 on which fiction heat is generated by sliding can be thin for improving the heat dissipation. Further, when an external force in the radial direction acts on the plunger 2 , the thick sliding portion 125 is deformed in the radial direction, and therefore the effect of reducing the generated surface pressure can be expected.
  • the connecting portion between the small-diameter portion 135 and large-diameter portion 134 may be formed by a tapered portion 136 in a tapered shape as in FIG. 4 , and a holding portion 133 may be formed on the tapered portion 136 .
  • the holding portion 133 is urged in the direction of the body 1 by the holder member 121 .
  • the tapered portion 136 is in contact with the holder member 121 , so that the cylinder 120 is automatically aligned. Therefore, more accurate positioning can be realized, and improved reliability of the sliding portion 125 can be expected.
  • the holding portion is tapered, the effect that the position of the cylinder is automatically aligned can be expected, and by realizing accurate positioning, unnecessary external force is not applied to the sliding portion.
  • FIG. 5 shows a cross-sectional view of components around the cylinder 120 according to the third embodiment of the present invention.
  • FIG. 5 also shows the case where the plunger 2 is located at the top dead center.
  • 1 represents a body, 2 a plunger, 120 a cylinder, 123 a sealing member, 4 a return spring, and 3 a retainer respectively.
  • a configuration in which the sliding portion 125 is not formed on the pressurizing chamber 11 side of the high-pressure sealing portion 124 is employed.
  • the cylinder 120 is prevented from entering the pressurizing chamber 11 , and the pressurizing chamber 11 can be configured to have a cylindrical shape whose inner diameter is approximately the same as that of the outer diameter of the plunger 2 .
  • a minute gap with a width A is formed between the two components.
  • the precompression volume which can be a cause of reduction in the volumetric efficiency (the volume of the pressurizing chamber 11 when the plunger 2 is located at the top dead center) can be reduced.
  • the pressurizing chamber can be formed in a cylindrical shape whose inner diameter is approximately the same as the outer diameter of the plunger, and the discharge passage and the suction passage can be arranged freely. Consequently, when the discharge pressure is increased to a high level, the precompression volume which can be a cause of reduction in the volumetric efficiency (the volume of the pressurizing chamber when the plunger is located at the top dead center) can be reduced.
  • the outer diameter of the cylinder can be highly precisely positioned by directly placing the same to the body, and the gaps in the pressurizing chamber can be further reduced. Thus, it is possible to further reduce the precompression volume.
  • This configuration also employs such a positional relationship that the positions in height (in the axial direction of the plunger 2 ) of the suction passage 10 and the discharge passage 12 relative to the plunger 2 coincide with the apex of the plunger 2 at the top dead center. Accordingly, the suction passage 10 and discharge passage 12 are not interrupted by the reciprocating movement of the plunger 2 , which allows smooth suction and discharge of the fuel.
  • a minute gap with a width B is formed between the outer periphery of the cylinder 120 and the inner periphery of the body 1 , and the dimensional relationship of the width A and the width B is A>B. Accordingly, since the outer periphery of the cylinder 120 and the inner periphery of the body 1 are in direct contact with each other during the assembly of the cylinder 120 , positioning with higher accuracy can be realized compared to the case of positioning through the holder member 121 , and the outer diameter of the plunger 2 and the inner diameter of the pressure chamber 11 can be more approximated to each other.
  • a gap with a width C is formed between the outer periphery of the cylinder 120 and the inner periphery of the holder member 121 , and the dimensional relationship between the width B and the width C is C>B. Accordingly, the outer periphery of the cylinder 120 and the inner periphery of the holder member 121 are kept out of contact, and unnecessary external force does not act on the cylinder 120 .
  • the holder member 121 is formed by two members: an urging member 121 a and a seal holder member 121 b.
  • the seal holder member 121 b is fitted to the urging member 121 a, and a gap with a width D is formed between the two members.
  • the dimensional relationship between the width B and the width D is preferably D>B. Accordingly, the position of the seal holder member 121 b in the radial direction aligns with that of the plunger 2 via the sealing member 123 , and therefore the axes of the two members coincide with each other, so that unnecessary external force does not act on the plunger 2 .
  • a fuel passage slit 131 which connects a main low-pressure fuel portion 130 and a secondary low-pressure fuel portion 127 may be formed on the cylinder 120 side.
  • FIG. 6 shows a variation of FIG. 5 .
  • FIG. 6 shows the case where the plunger 2 is located at the top dead center.
  • the pressurizing chamber 11 is formed by a capacity portion 11 a where the plunger 2 reciprocates, and a passage portion 11 b which connects the capacity portion 11 a to the suction passage 10 and discharge passage 12 .
  • the inner diameter portion of the capacity portion 11 a is formed in a cylindrical shape whose inner diameter is approximately the same as the outer diameter of the plunger 2 . Also with this configuration, the same effects as in FIG. 5 can be achieved.
  • a pump for supplying high-pressure fuel capable of improving reliability of the sliding portion at high pressures by reducing unnecessary external force acting on the sliding portion 125 , and further capable of preventing reduction in the volumetric efficiency can be realized with a small-sized and simple structure.
  • a pump for supplying high-pressure fuel capable of improving reliability of the sliding portion at high pressures and further preventing a reduction of the volumetric efficiency can be realized with a small-sized and simple structure.
  • the present invention can be applied not only to pumps for supplying high-pressure fuel in internal combustion engines but also widely to various high-pressure pumps.
  • damper chamber 53 . . . common rail, 54 . . . injector, 56 . . . pressure sensor, 120 . . . cylinder, 121 . . . holder member, 121 a . . . urging member, 121 b . . . seal holder member, 124 . . . high-pressure sealing portion, 125 . . . sliding portion, 126 . . . coupling portion, 127 . . . secondary low-pressure fuel portion, 128 . . . large-diameter portion, 129 . . . small-diameter portion, 130 . . . main low-pressure fuel portion, 131 . . .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
US14/439,419 2012-10-31 2013-10-09 Pump for Supplying High-Pressure Fuel Abandoned US20150300338A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2012-239738 2012-10-31
JP2012239738A JP6293994B2 (ja) 2012-10-31 2012-10-31 高圧燃料供給ポンプ
PCT/JP2013/077409 WO2014069192A1 (ja) 2012-10-31 2013-10-09 高圧燃料供給ポンプ

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2013/077409 A-371-Of-International WO2014069192A1 (ja) 2012-10-31 2013-10-09 高圧燃料供給ポンプ

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US16/238,807 Continuation US10851767B2 (en) 2012-10-31 2019-01-03 Pump for supplying high-pressure fuel

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US20150300338A1 true US20150300338A1 (en) 2015-10-22

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Family Applications (2)

Application Number Title Priority Date Filing Date
US14/439,419 Abandoned US20150300338A1 (en) 2012-10-31 2013-10-09 Pump for Supplying High-Pressure Fuel
US16/238,807 Active US10851767B2 (en) 2012-10-31 2019-01-03 Pump for supplying high-pressure fuel

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Application Number Title Priority Date Filing Date
US16/238,807 Active US10851767B2 (en) 2012-10-31 2019-01-03 Pump for supplying high-pressure fuel

Country Status (5)

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US (2) US20150300338A1 (enrdf_load_stackoverflow)
EP (1) EP2915995B1 (enrdf_load_stackoverflow)
JP (1) JP6293994B2 (enrdf_load_stackoverflow)
CN (1) CN104781543B (enrdf_load_stackoverflow)
WO (1) WO2014069192A1 (enrdf_load_stackoverflow)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10330066B2 (en) 2014-10-15 2019-06-25 Continental Automotive Gmbh High-pressure fuel pump
US10590897B2 (en) 2015-10-23 2020-03-17 Hitachi Automotive Systems, Ltd. High-pressure fuel supply pump, manufacturing method thereof, and method of bonding two members
US11002236B2 (en) 2016-11-18 2021-05-11 Hitachi Automotive Systems, Ltd. High-pressure fuel supply pump

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3088725B1 (en) * 2015-04-28 2019-07-03 Magneti Marelli S.p.A. Fuel pump for a direct injection system with a reduced stress on the bushing of the piston
DE102016201600B4 (de) * 2016-02-03 2017-10-12 Continental Automotive Gmbh Kraftstoffhochdruckpumpe und Kraftstoffeinspritzsystem
CN107917028B (zh) * 2016-10-10 2022-01-18 罗伯特·博世有限公司 柱塞式高压泵及其高压组件、柱塞套
DE102017212498A1 (de) * 2017-07-20 2019-01-24 Robert Bosch Gmbh Kolbenpumpe, insbesondere Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine
WO2020080005A1 (ja) * 2018-10-19 2020-04-23 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
US20230235729A1 (en) * 2020-03-11 2023-07-27 Cummins Inc. Compact opposed pump
CN111946580B (zh) * 2020-08-25 2021-04-09 兰州理工大学 数字变量式液压电机径向柱塞泵

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110303195A1 (en) * 2010-06-10 2011-12-15 Robert Lucas Single piston pump with dual return springs
US20120012084A1 (en) * 2010-05-17 2012-01-19 MAGNETI MARELLI S.p.A. Fuel Pump For A Direct Injection System

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6293162U (enrdf_load_stackoverflow) * 1985-12-03 1987-06-13
JPH09250427A (ja) * 1996-03-15 1997-09-22 Zexel Corp 燃料噴射ポンプ
JPH1018941A (ja) * 1996-07-01 1998-01-20 Mitsubishi Electric Corp 可変吐出量高圧ポンプ
DE19801398A1 (de) * 1998-01-16 1999-07-22 Bosch Gmbh Robert Radialkolbenpumpe zur Kraftstoffhochdruckversorgung
EP1950411B1 (en) * 1999-02-09 2012-09-12 Hitachi, Ltd. High pressure fuel supply pump for internal combustion engine
JP2001050174A (ja) * 1999-08-03 2001-02-23 Hitachi Ltd 燃料供給ポンプ
DE60128000T2 (de) * 2001-01-05 2008-01-17 Hitachi, Ltd. Fluidpumpe und hochdruckkraftstoffförderpumpe
JP2003148294A (ja) 2001-11-12 2003-05-21 Hitachi Ltd 燃料ポンプ及び筒内噴射エンジン
DE10212492B4 (de) * 2002-03-21 2012-02-02 Daimler Ag Kolbenpumpe
DE10322595B4 (de) * 2003-05-20 2013-02-28 Robert Bosch Gmbh Kolbenpumpe, sowie Verfahren zu ihrer Herstellung
JP2008064013A (ja) * 2006-09-07 2008-03-21 Hitachi Ltd 高圧燃料供給ポンプ
JP2009185613A (ja) * 2008-02-04 2009-08-20 Hitachi Ltd 高圧燃料ポンプ
JP5017233B2 (ja) * 2008-10-30 2012-09-05 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
JP5136919B2 (ja) * 2010-04-08 2013-02-06 株式会社デンソー 高圧ポンプ
JP5610829B2 (ja) 2010-04-23 2014-10-22 大成建設株式会社 充填材ストッパー
JP2012082849A (ja) * 2010-10-07 2012-04-26 Hitachi Automotive Systems Ltd 電磁駆動機構、この電磁駆動機構を用いた電磁弁およびこの電磁弁を用いた電磁吸入弁を備えた可変流量式高圧燃料供給ポンプ
JP5702984B2 (ja) 2010-10-15 2015-04-15 日立オートモティブシステムズ株式会社 電磁駆動型の吸入弁を備えた高圧燃料供給ポンプ
JP5673284B2 (ja) * 2011-03-28 2015-02-18 株式会社デンソー 高圧ポンプ
JP2020026736A (ja) * 2018-08-09 2020-02-20 トヨタ自動車株式会社 高圧燃料ポンプ

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120012084A1 (en) * 2010-05-17 2012-01-19 MAGNETI MARELLI S.p.A. Fuel Pump For A Direct Injection System
US20110303195A1 (en) * 2010-06-10 2011-12-15 Robert Lucas Single piston pump with dual return springs

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10330066B2 (en) 2014-10-15 2019-06-25 Continental Automotive Gmbh High-pressure fuel pump
US10590897B2 (en) 2015-10-23 2020-03-17 Hitachi Automotive Systems, Ltd. High-pressure fuel supply pump, manufacturing method thereof, and method of bonding two members
US11002236B2 (en) 2016-11-18 2021-05-11 Hitachi Automotive Systems, Ltd. High-pressure fuel supply pump

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US20190136841A1 (en) 2019-05-09
EP2915995A1 (en) 2015-09-09
EP2915995B1 (en) 2020-07-01
CN104781543A (zh) 2015-07-15
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US10851767B2 (en) 2020-12-01
EP2915995A4 (en) 2016-08-10

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