EP1302664A1 - Variable-Flow High-Pressure Pump - Google Patents

Variable-Flow High-Pressure Pump Download PDF

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Publication number
EP1302664A1
EP1302664A1 EP02022716A EP02022716A EP1302664A1 EP 1302664 A1 EP1302664 A1 EP 1302664A1 EP 02022716 A EP02022716 A EP 02022716A EP 02022716 A EP02022716 A EP 02022716A EP 1302664 A1 EP1302664 A1 EP 1302664A1
Authority
EP
European Patent Office
Prior art keywords
pressure pump
valve
fluid
fuel
flow
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.)
Withdrawn
Application number
EP02022716A
Other languages
German (de)
English (en)
French (fr)
Inventor
Alberto Bastia
Rita Di Gioia
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.)
Marelli Europe SpA
Original Assignee
Magneti Marelli Powertrain SpA
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 Magneti Marelli Powertrain SpA filed Critical Magneti Marelli Powertrain SpA
Publication of EP1302664A1 publication Critical patent/EP1302664A1/en
Withdrawn legal-status Critical Current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
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—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
    • F02M59/365—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages valves being actuated by the fluid pressure produced in an auxiliary pump, e.g. pumps with differential pistons; Regulated pressure of supply pump actuating a metering valve, e.g. a sleeve surrounding the pump 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
    • F02M59/20—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/462—Delivery valves
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing
    • F04B49/243—Bypassing by keeping open the inlet valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/02—Piston machines or pumps characterised by having positively-driven valving the valving being fluid-actuated
    • F04B7/0266—Piston machines or pumps characterised by having positively-driven valving the valving being fluid-actuated the inlet and discharge means being separate members

Definitions

  • the present invention relates to a variable-flow high-pressure pump.
  • the present invention relates, in particular, to a variable-flow high-pressure pump for diesel engines with a fuel supply system of the common rail type, to which the following description will explicitly refer without entering into general details.
  • the common rail supply system requires the use of a high-pressure pump which is able to supply fuel at very high pressure to a collection container for the pressurised fuel interposed between the high-pressure pump and the fuel injectors, with a variable flow so that the quantity of fuel supplied to the collection container can be regulated in real time as a function of the operating conditions of the engine.
  • the high-pressure pumps that are currently known receive the fuel from a low-pressure pump and normally comprise a piston which is mounted in an axially sliding manner within a cylindrical cavity obtained in the body of the pump so as to define a variable-volume pumping chamber adapted to be filled with fuel, and a pair of non-return valves adapted to regulate the flow of fuel from and to the pumping chamber during the variations of the volume of the pumping chamber caused by the alternating movement of the piston within the cylindrical cavity.
  • the pumping chamber is connected to the pressurised fuel collection container via a first non-return valve oriented so as to enable fuel to flow from the pumping chamber to the collection container, and is connected to the delivery of the low-pressure pump by means of a second non-return valve oriented so as to enable fuel to flow from the low-pressure pump to the pumping chamber.
  • the two non-return valves are normally positioned within the body of the pump along the two connection ducts via which the fuel enters and leaves the pumping chamber, and comprise a shutter body mounted in an axially sliding manner within a cylindrical duct obtained along a section of the connection duct, and an elastic member which is disposed within the cylindrical cavity so as to maintain the shutter body in abutment against a sealing seat obtained at the location of one of the two axial ends of the cylindrical cavity, so as to close the opening provided at the location of this opening in a leak-tight manner.
  • the cylindrical cavity is in practice in communication externally via two openings obtained at the location of the two axial ends of this cavity.
  • the high-pressure pumps currently known are further provided with a linear electromagnetic actuator able, on command, to interfere with the normal operation of the non-return valve interposed between the pumping chamber and the low-pressure pump, so as to enable the fuel also to flow freely via the valve in a direction opposite to the normal direction.
  • the output shaft of the linear electromagnetic actuator is able, on command, to counter and maintain the shutter body of the valve raised from its sealing seat, so as to enable the fuel to flow via the cylindrical cavity even when it comes from the opening disposed directly facing the elastic member, i.e. from the opposite portion of the shutter body with respect to this elastic member.
  • the non-return valve disposed at the location of the intake inlet of the pump is kept open when the pumping chamber starts to reduce in volume, it is possible to cause part of the fuel that has previously filled the pumping chamber to flow back again to the low-pressure pump rather than to the pressurised fuel collection container, thereby making it possible accurately to regulate the quantity of fuel supplied to the collection container during the end section of the piston stroke, when the action of the linear electromagnetic actuator ceases and the valve starts to operate normally again.
  • the system for regulating flow by means of the linear electromagnetic actuator is not suited to location in high-pressure pumps provided with two or more pistons: in this case, the high-pressure pump would have to be equipped with a linear electromagnetic actuator for each pumping chamber, with the problems of driving of the actuators and consumption of electrical energy that this entails.
  • the object of the present invention is therefore to provide a high-pressure pump with a flow regulation system that can also be readily used with pumps provided with two or more pistons.
  • the present invention relates to a variable-flow high-pressure pump comprising at least one pumping piston mounted to slide axially and in a leak-tight manner within a cylindrical cavity obtained in the body of the pump so as to define a variable-volume pumping chamber adapted to be filled with a generic fluid, at least one intake valve and a delivery valve adapted to enable the one-way flow of the fluid respectively into and out of the pumping chamber, the intake valve being formed by a non-return valve comprising a shutter body which can move to and from a closed position in which it prevents the passage of the fluid via this valve, the high-pressure pump further comprising flow regulation means adapted to interfere with the normal operation of the intake valve in order to enable the fluid also to flow freely via the valve in a direction opposite to the normal direction, the high-pressure pump being characterised in that the flow regulation means comprise a hydraulic piston selectively adapted to prevent the shutter body from returning to the closed position.
  • variable-flow high-pressure pump which may advantageously be used in diesel engines with a fuel supply system of the common rail type, in order to supply fuel at very high pressure to a pressurised fuel collection container interposed between this pump and the fuel injectors (not shown), is shown overall by reference numeral 1.
  • the pump 1 is provided with a delivery outlet 1a which, in the embodiment shown, is adapted to be connected to the pressurised fuel collection container, indicated below by reference numeral 2, by means of a first connection duct, and an intake inlet 1b which, in the embodiment shown, is adapted to be connected to the delivery of a low-pressure pump, indicated below by reference numeral 3, by means of a second connection duct.
  • the pressurised fuel collection container 2 and the low-pressure pump 3 are devices that are widely known in the art and are not therefore described in further detail below.
  • the high-pressure pump 1 comprises at least one pumping piston 4 mounted to slide axially and in a leak-tight manner in a cylindrical cavity 5 obtained in the body 6 of the pump in order to define a variable-volume pumping chamber 7 adapted to be filled with fuel.
  • the pumping piston 4 may move with an alternating movement in the cylindrical cavity 5 between a first operating position, normally called “bottom dead centre”, in which the top of the piston 4 is at the maximum distance from the base of the cylindrical cavity 5 and the volume of the pumping chamber 7 assumes the maximum value, and a second operating position, normally called “top dead centre” in which the top of the piston 4 is at the minimum distance from the base of the cylindrical cavity 5 and the volume of the pumping chamber 7 assumes the minimum value.
  • the high-pressure pump 1 is further provided with a pair of non-return valves 8 and 9 which are adapted to regulate the flow of fuel to and from the pumping chamber 7, during the variations of the volume of the chamber caused by the alternating movement of the piston 4 in the cylindrical cavity 5.
  • the two non-return valves 8 and 9 are disposed along the connection ducts which bring the pumping chamber 7 into communication with the delivery outlet 1a and the intake inlet 1b respectively of the pump 1, and are oriented such that the non-return valve 8 disposed along the duct that ends at the location of the delivery outlet 1a - also called the delivery valve - can enable the fuel to flow solely as output from the pumping chamber 7, while the non-return valve 9 disposed along the duct that ends at the location of the intake inlet 1b - also known as the intake valve - can enable the fuel to flow solely as input into the pumping chamber 7.
  • the delivery valve 8 enables the fuel to flow solely from the pumping chamber 7 to the collection container 2, while the intake valve 9 enables the fuel to flow solely from the low-pressure pump 3 to the pumping chamber 7.
  • the non-return valves 8 and 9 are substantially of known type, and comprise a shutter body 10 preferably, but not necessarily, of spherical shape which is mounted in an axially sliding manner in a cylindrical cavity 11 obtained along a section of the connection duct leading to the intake inlet 1b or the delivery outlet 1a of the pump 1.
  • the cylindrical cavity 11 is obviously in communication with the exterior via two openings obtained at the location of the two axial ends of this cavity.
  • the non-return valves 8 and 9 are further provided with an elastic member 12 adapted to maintain the shutter body 10 in a closed position, in which it is disposed in abutment against a sealing seat obtained at the location of one of the two axial ends of the cylindrical cavity 11, so as to close the opening present at that point in a leak-tight manner.
  • the elastic member 12 is in particular formed by a helical spring 12 disposed coaxially with the axis of the cylindrical cavity 11 so as to have a first end in abutment against the shutter body 10 and a second end in abutment against one of the two axial ends of the cylindrical cavity 11.
  • the non-return valves 8 and 9 are not provided with the elastic member 12, and the axial displacement of the shutter body 10 to or from the above-mentioned closed position takes place exclusively as a result of the pressure difference which is established between the two sides of the shutter body 10 when the fuel flows via the cylindrical cavity 11 of the valve.
  • the high-pressure pump 1 is lastly provided with a flow regulation device 13 for the pump, which is able to interfere, on command, with the normal operation of the intake valve 9, in order also to enable the fuel to flow freely via this valve in a direction opposite to the normal direction, so as to be able to regulate the quantity of fuel supplied to the delivery outlet 1a during the return stroke of the piston 4 towards the top dead centre.
  • the flow regulation device 13 comprises a single-acting hydraulic piston 14 which is adapted to be supplied by a pressurised fluid advantageously formed by part of the fuel from the low-pressure pump 2, and is able axially to displace the shutter body 10 within the cylindrical cavity 11 so as to distance it from the closed position, thereby enabling the free passage of the fuel via the non-return valve 9.
  • the flow regulation device 13 further comprises an electrically actuated exhaust valve 15 which is selectively adapted to cause a pressure drop in the fluid supplied to the hydraulic piston 14, i.e. the fuel from the low-pressure pump 3, so as to prevent any displacement of the hydraulic piston 14, and an electronic control unit 16 adapted to drive the exhaust valve 15 so as to control, in real time, the time interval in which the intake valve 9 is disabled in order to be able to regulate the quantity of fuel newly supplied to the delivery outlet 1a during the return stroke of the piston 4 to the top dead centre and, therefore, the quantity of fuel supplied to the collection container 2 during each stroke of the piston 4.
  • an electrically actuated exhaust valve 15 which is selectively adapted to cause a pressure drop in the fluid supplied to the hydraulic piston 14, i.e. the fuel from the low-pressure pump 3, so as to prevent any displacement of the hydraulic piston 14, and an electronic control unit 16 adapted to drive the exhaust valve 15 so as to control, in real time, the time interval in which the intake valve 9 is disabled in order to be able to regulate the quantity of fuel newly
  • the hydraulic piston 14 is in particular provided with an output shaft 14a which is adapted to be disposed with its point in abutment against the shutter body 10, and then axially to displace the shutter body 10 within the cylindrical cavity 11 so as to prevent the shutter body 10 from returning to its closed position so as to enable -the free passage of the fuel via the cylindrical cavity 11 of the valve.
  • the output shaft 14a of the hydraulic piston 14 extends coaxially to the longitudinal axis of the cylindrical cavity 11, from the opposite side of the elastic member 12 with respect to the shutter body 10, and can move axially between a retracted position and a forward position in which it is able to lock the shutter body remote from its closed position.
  • the exhaust valve 15 is, however, positioned in a branched manner along a connection duct 17 which carries the fuel from the low-pressure pump 3 to the hydraulic piston 14 so as to be able, on command, to bring the duct 17 into direct communication with the fuel recycling circuit 18 which connects, in a known manner, the delivery of the low-pressure pump 3 with the fuel tank 19 of the vehicle via the interposition of a non-return valve 20 of known type.
  • the non-return valve 20 is adapted to divert the excess delivery from the low-pressure pump 3 again upstream of the intake inlet of the low-pressure pump 3, and is oriented so as to enable the fuel to flow in one direction from the delivery of the low-pressure pump 3 to the fuel tank 19 and not vice versa, causing a pressure drop of a predetermined value, and the exhaust valve 15 is able to bring the duct 17 into direct communication with the fuel recycling circuit 18 immediately downstream of this non-return valve 20.
  • the high-pressure pump 1 is provided with a second non-return valve 21, disposed along the connection duct 17 that carries the fuel from the low-pressure pump 3 to the hydraulic piston 14, and with a throttle valve 22 disposed immediately upstream of the intake inlet 1b of the pump 1.
  • the non-return valve 21 is positioned upstream of the point at which the exhaust valve 15 is inserted on the duct 17 and is oriented so as to enable the fuel to flow from the delivery of the low-pressure pump 3 to the hydraulic piston 14 and the exhaust valve 15, causing a pressure drop of a predetermined value; while the throttle valve 22 is adapted to cause a pressure drop of predetermined value in the pressurised fuel that is flowing to the intake inlet 1b of the pump.
  • the intake valve 9 opens as a result of the pressure difference and the fuel starts to flow into the pumping chamber 7 of the pump 1.
  • the intake valve 9 tends to close so as to force the fuel to flow out of the pumping chamber 7 via the delivery valve 8, but the output shaft 14a of the hydraulic piston 14 prevents the shutter body 10 from returning to its closed position, as a result of which the fuel starts to emerge from the pumping chamber 7 via the intake valve 9.
  • the hydraulic piston 14 is still supplied with pressurised fuel from the low-pressure pump 3 and its output shaft 14a is thus in the forward position, preventing the shutter body 10 from returning to the closed position.
  • the intake valve 9 closes and the fuel pressure in the pumping chamber 7 rises until it reaches a sufficiently high value to cause the opening of the delivery valve 8 and the resultant discharge of the fuel to the pressurised fuel collection container 2.
  • an exhaust valve 15 has a consumption of electric current which is substantially lower than that of the linear electromagnetic actuators currently used.
  • a further advantage of the high-pressure pump 1 is that a single exhaust valve 15 can simultaneously control one or more hydraulic pistons 14, greatly simplifying the construction of variable-flow high-pressure pumps equipped with a plurality of pumping members.

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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)
  • Rotary Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
EP02022716A 2001-10-12 2002-10-10 Variable-Flow High-Pressure Pump Withdrawn EP1302664A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITBO20010625 2001-10-12
IT2001BO000625A ITBO20010625A1 (it) 2001-10-12 2001-10-12 Pompa ad alta pressione a portata variabile

Publications (1)

Publication Number Publication Date
EP1302664A1 true EP1302664A1 (en) 2003-04-16

Family

ID=11439654

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02022716A Withdrawn EP1302664A1 (en) 2001-10-12 2002-10-10 Variable-Flow High-Pressure Pump

Country Status (4)

Country Link
US (1) US20030091445A1 (it)
EP (1) EP1302664A1 (it)
BR (1) BR0204658A (it)
IT (1) ITBO20010625A1 (it)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010043314A1 (de) * 2010-11-03 2012-05-03 J. Eberspächer GmbH & Co. KG Dosierpumpe

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1724467B1 (en) * 2005-05-20 2016-07-13 Magneti Marelli S.p.A. Fuel pump for an internal combustion engine
US20130312706A1 (en) * 2012-05-23 2013-11-28 Christopher J. Salvador Fuel system having flow-disruption reducer
CN103967670B (zh) * 2013-02-04 2018-11-06 辽宁新风企业集团有限公司 一种高压油泵用油阀部件
DE102016124422A1 (de) * 2016-12-14 2018-06-14 Hammelmann GmbH Hochdruckplungerpumpe sowie Verfahren zur Funktionsunterbrechung eines Fluidstroms
CN112901386B (zh) * 2021-03-03 2024-03-19 钧风电控科技(泰州)有限责任公司 一种油阀柱塞组件及高压油泵

Citations (5)

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JPS6019974A (ja) * 1983-07-13 1985-02-01 Kobe Steel Ltd 往復動ポンプの制御装置
US4519752A (en) * 1982-09-03 1985-05-28 Applied Power Inc. Control system for a variable displacement pump
US6116870A (en) * 1996-10-29 2000-09-12 Robert Bosch Gmbh High pressure pump with solenoid operated valve
EP1061254A2 (en) * 1999-06-15 2000-12-20 Isuzu Motors Limited Common-rail fuel-injection system
GB2352780A (en) * 1999-03-23 2001-02-07 Nachi Fujikoshi Corp High pressure plunger pump

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US1466804A (en) * 1921-12-22 1923-09-04 Fingal C Orr Liquid-dispensing apparatus
US1510038A (en) * 1923-03-24 1924-09-30 Anthony R Edmondson Cut-off valve
US2375810A (en) * 1943-09-07 1945-05-15 Christian A Nelson Cutoff valve
US2778378A (en) * 1952-07-28 1957-01-22 Bendix Aviat Corp Combination sequence and locking valve
US4065230A (en) * 1975-01-17 1977-12-27 Hart Associates, Inc. Reciprocating infusion pump and directional adapter set for use therewith
US4838306A (en) * 1987-08-10 1989-06-13 Aladdin Engineering & Mfg., Inc. Pneumatic locking valve with manual override
JP2932952B2 (ja) * 1994-12-07 1999-08-09 株式会社豊田自動織機製作所 クラッチレス可変容量型圧縮機
US6488479B1 (en) * 2001-05-17 2002-12-03 Ford Global Technologies, Inc. Variable pressure oil pump

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4519752A (en) * 1982-09-03 1985-05-28 Applied Power Inc. Control system for a variable displacement pump
JPS6019974A (ja) * 1983-07-13 1985-02-01 Kobe Steel Ltd 往復動ポンプの制御装置
US6116870A (en) * 1996-10-29 2000-09-12 Robert Bosch Gmbh High pressure pump with solenoid operated valve
GB2352780A (en) * 1999-03-23 2001-02-07 Nachi Fujikoshi Corp High pressure plunger pump
EP1061254A2 (en) * 1999-06-15 2000-12-20 Isuzu Motors Limited Common-rail fuel-injection system

Non-Patent Citations (1)

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Title
PATENT ABSTRACTS OF JAPAN vol. 009, no. 139 (M - 387) 14 June 1985 (1985-06-14) *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010043314A1 (de) * 2010-11-03 2012-05-03 J. Eberspächer GmbH & Co. KG Dosierpumpe

Also Published As

Publication number Publication date
ITBO20010625A1 (it) 2003-04-12
BR0204658A (pt) 2003-09-16
US20030091445A1 (en) 2003-05-15

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