EP0972936A2 - Pompes volumétriques - Google Patents

Pompes volumétriques Download PDF

Info

Publication number
EP0972936A2
EP0972936A2 EP99305492A EP99305492A EP0972936A2 EP 0972936 A2 EP0972936 A2 EP 0972936A2 EP 99305492 A EP99305492 A EP 99305492A EP 99305492 A EP99305492 A EP 99305492A EP 0972936 A2 EP0972936 A2 EP 0972936A2
Authority
EP
European Patent Office
Prior art keywords
pumping
plunger
tappet
positive displacement
pump
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Withdrawn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
EP99305492A
Other languages
German (de)
English (en)
Other versions
EP0972936A3 (fr
Inventor
Stephen Michael Parker
Michael Peter Cooke
Ian Roy Thornthwaite
Peter Alban Collingborn
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.)
Delphi Technologies Inc
Original Assignee
Lucas Industries Ltd
Delphi Technologies Inc
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 Lucas Industries Ltd, Delphi Technologies Inc filed Critical Lucas Industries Ltd
Publication of EP0972936A2 publication Critical patent/EP0972936A2/fr
Publication of EP0972936A3 publication Critical patent/EP0972936A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F04B1/043—Hydraulic arrangements
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams

Definitions

  • This invention relates to a positive displacement pump and, in the preferred embodiment, provides a pump suitable for delivering high pressure fuel to the fuel injection system of an internal combustion engine. It is to be understood, however, that the invention is not limited to pumps of this particular type and is generally applicable to a wide range of positive displacement pumps.
  • a pumping plunger reciprocates within a cylinder to vary the volume of a pumping chamber and effect, with the aid of suitable valving, delivery of the pumped fluid.
  • a force is applied to the plunger in order to drive fluid from the pumping chamber.
  • Each delivery stroke is followed by a return stroke in which the plunger moves in the opposite direction to increase the volume of the pumping chamber.
  • the present invention provides a novel means of driving the pump plunger of a positive displacement pump in the return direction.
  • a positive displacement pump comprising a cylinder, a pump plunger slidably mounted in the cylinder to define therewith a pumping chamber, and drive means for driving the pump plunger in a forward direction to reduce the volume of the pumping chamber to effect delivery of a pumped fluid
  • a piston is coupled to the pump plunger; the piston is slidably mounted in a bore defined in the pump so as to define a working chamber the volume of which increases as the volume of the pumping chamber increases; and means are provided for supplying working fluid under pressure to the working chamber to generate a force on the piston in the return direction tending to increase the volume of the pumping chamber.
  • Working fluid under pressure may be supplied to the working chamber only during return strokes of the piston.
  • working fluid under pressure is present in the working chamber at all times and the drive means is effective to move the pump plunger against the force generated by the working fluid during forward strokes of the pump plunger.
  • the working fluid is a hydraulic fluid and in a particularly preferred embodiment of the invention the working fluid is lubricating oil.
  • the lubricating oil can advantageously be derived from the lubrication system of the internal combustion engine.
  • the piston is formed by a tappet assembly which, as well as performing its function as a piston, acts to transmit force from a drive cam to the pump plunger during forward strokes of the pump plunger.
  • the piston is a tappet assembly
  • the presence of pressurised lubricating oil in the working chamber will lubricate the tappet assembly as well as providing the required return force.
  • the working chambers associated with the respective pump plungers are preferably interconnected to allow working fluid to flow between the working chambers as the respective pump plungers reciprocate.
  • An accumulator may be provided to maintain working fluid pressure and to receive surplus working fluid as the total volume of the working chambers varies during rotation of the drive shaft of the pump.
  • each pump plunger is formed with a head which is secured to and forms part of the tappet assembly.
  • the head can conveniently be used to close the interior space of the tappet assembly and thereby allow the tappet assembly to act as a piston.
  • the tappet comprises a tappet shell within which the head is received and a slipper is interposed between the head of the plunger and the tappet shell.
  • the slipper includes a flat face which engages a complementary flat face of the tappet shell and a part-spherical or part-conical face which engages a complementary part-spherical face of the pump plunger head.
  • the invention is particular applicable to a fuel pump suitable for delivering high pressure fuel to the fuel injection system of an internal combustion engine, it should be appreciated that the invention is not limited to such applications. Further, the invention is generally applicable to a wide range of plunger configurations and can be applied successfully to constructions in which the plungers are arranged in axial (parallel) orientation, or in a fan or a conical arrangement. Further, the invention is applicable to a wide range of drive mechanisms, for example external or internal cams or swash plate drives. It is further to be appreciated that whilst lubricating oil, and in particular engine oil, is the preferred working fluid in the preferred embodiment of the invention, other arrangements are possible.
  • the high pressure fuel pump shown in Figure 1-3 is suitable for use in the fuel injection system of an internal combustion engine, and in particular is suitable for delivering high pressure fuel to an accumulator or the common rail of a common rail fuel injection system.
  • the illustrated pump 1 comprises three pumping assemblies 2,3 and 4 located in a common radial zone and spaced 120° apart around a drive shaft 5.
  • the shaft 5 carries a single cam 6 for driving the pumping assemblies to deliver high pressure fuel from an outlet 7.
  • the drive shaft 5 is supported in a pump body 8 by a front bearing 9 and a rear bearing 10.
  • the pump body 8 is secured to an internal combustion engine and an appropriate rotary drive from the engine is used to rotate the shaft 5.
  • the pumping assemblies 2,3,4 are substantially identical to each other and, in the interests of brevity, only the pumping assembly 3 will be described in detail.
  • the pumping assembly 3 comprises a cylinder block 11 which defines a pumping cylinder 12.
  • a pumping plunger 13 is slidably mounted in the cylinder 12 and, in use, is reciprocated along the cylinder 12 to vary the volume of a pumping chamber defined by the plunger, the cylinder and a cylinder head 14 in a cyclic manner.
  • the cylinder head 14 is secured to the cylinder block 11.
  • a delivery valve 15 is mounted in the cylinder head 14 and is normally biased against the cylinder block by a spring which is located within a bore 16 in the cylinder head, so that the delivery valve closes the end of the cylinder 12.
  • the delivery valve 15 is surrounded by a gallery 17 which is connected via passages 18 in the cylinder blocks 11 and pump body 8 to corresponding galleries surrounding the delivery valves of the other pumping assemblies.
  • the passages 18 are connected by a branch passage 19 to the delivery outlet 7.
  • each pump plunger 13 is driven towards associated cylinder head 14 fuel in the pumping chamber is pressurised and when the pressure of fuel within the cylinder 12 exceeds that in the gallery 17 and passages 18 the delivery valve 15 will open to allow fuel to flow from the pumping chamber 12 to the passages 18 and eventually via branch passage 19 to the outlet 7.
  • the delivery valves 15 automatically close under the influence of the associated springs when the pumping plungers reach top dead centre. Closure is assisted by the pressure difference resulting from the plunger beginning to move inwards after top dead centre.
  • Each plunger 13 is connected to an associated tappet assembly 20.
  • Each tappet assembly 20 comprises a tappet shell 21 which is slidably mounted in a bore 22 provided in the body 8.
  • a roller 23 is rotatably mounted on a shaft 24 which is secured to the tappet shell 21.
  • At the end thereof remote from the shaft 5 each tappet shell 21 is counterbored to provide a shoulder 25.
  • a slipper 26 is mounted within the counterbored portion of each tappet shell with a thrust surface of the slipper in engagement with the shoulder 25. The slipper is somewhat smaller in diameter than the counterbore in the tappet shell so that some lateral movement of the slipper relative to the tappet shell is possible.
  • Each slipper 26 defines a spherical seat 27 which is engaged with a complementary spherical surface 28 provided on a head 29 of the associated plunger 13.
  • part-spherical surfaces part-conical surfaces may be used.
  • Each plunger 13 is secured to its associated tappet shell by any appropriate method that preserves the necessary freedom for articulation and achieves adequate sealing. For example a resilient circlip, with or without one or more washers may be used. In use substantial separation of the pump plunger 13 from its associated tappet shell is not possible.
  • a chamber 30 which is defined in part by the bore 22, in part by the radially outer side of the tappet assembly, and in part by the cylinder block 11.
  • fluid under pressure can conveniently be in the form of pressurised lubricating oil derived from the lubrication system of the engine served by the illustrated pump.
  • lubricating oil can be supplied via an inlet fitting 31 and delivered via drilling 32 and slots 33 to the chambers 30.
  • pressurised lubricating oil within the chambers 30 will act over the area of the tappet assemblies (less the area of the pump plunger 13) to produce a force on the pump plunger 13 in the radial inward direction.
  • the oil pressure within the associated chamber 30 will cause the roller 23 to remain in contact with the cam 6 as the associated plunger is moved from its top dead centre to its bottom dead centre position.
  • no inlet valve is provided on or adjacent to the cylinder head 14.
  • one or more passages 34 extends from a fuel gallery 35 defined between the cylinder block 11 and cylinder head 14 to a point in the bore 12 just radially outwardly of the bottom dead centre position of the radially outer end of the pumping plunger 13. Fuel under slight super-ambient pressure is maintained within the gallery 35 by a transfer pump. As the pump plunger moves from top dead centre towards bottom dead centre the delivery valve 15 will close and thereafter a vacuum will be generated within the cylinder 12.
  • some lubricating oil is permitted to escape from the chambers 30 into the cam chamber 37 so as to lubricate of the tappet assembly bores 22 and to lubricate the rollers 23 and cam 6.
  • Such escaping oil will additionally lubricate the bearings 9,10 and is preferably permitted to flow back into the crankcase of the engine to which the fuel pump is attached via the front bearing 10.
  • a small net loss of lubricating oil past the tappet assemblies into the cam chamber 37 is in fact desirable in that it will allow a flow of lubricating oil through the pump and thereby reduce any tendency for the lubricating oil to overheat as a result of being shunted into and out of the chambers 30 as the pump operates.
  • the invention has been described with reference to a particular embodiment thereof, it is to be understood that it is generally applicable to a wide range of positive displacement pumps, and accordingly should not be regarded as limited to the particular embodiment described. More particularly, the invention is generally applicable to any positive displacement pump in which the pumping plunger is required to be driven from top dead centre to bottom dead centre. Although the use of lubricating oil for driving the pump plungers from top dead centre to bottom dead centre offers a number of significant advantages it is to be understood that the invention is not limited to such a fluid.
  • the pressurised fluid required to drive the pump plungers may be obtained from any suitable source.
  • a pressure accumulator may be used to receive variations in the total volume of the pressurised fluid system as the pump operates.
  • the invention may be applied to a pump having only a single pumping plunger, in which case a pressure accumulator having a volume sufficient to accommodate the entire displaced volume of working fluid will be required.
  • Such a pressure accumulator could be powered by means of a spring which would, in effect, then drive the pump plunger using the hydraulic fluid as an operating medium.
  • Such an arrangement would be akin to having a spring directly driving the pump plunger in the filling direction, but would not impose the design constraints associated with the use of a spring directly for this purpose.
  • a non-return valve in or near inlet 31, would permit the accumulator to determine an operating pressure which exceeds the oil supply pressure during part of the accumulator piston's reciprocation, such a higher pressure would allow the pump to run at higher speeds, by coping with increased tappet acceleration, or would allow for the increased acceleration consequent on employing a non-circular cam.
  • Such a cam could have one or more lobes. It could be arranged to produce a slow pumping action, for reduced drive torque, and then a rapid return stroke.
  • FIGS 4-6 illustrate schematically an alternative embodiment to the invention.
  • three pumping assemblies 102, 103 and 104 which are substantially identical to each other are provided axially spaced apart along a camshaft 105.
  • the camshaft 105 has three cams 106 located 120° out of phase with each other. Each cam is associated with a respective one of the pumping assemblies 102,103,104.
  • the camshaft 105 is supported in a pump body 108 by a front bearing 109 and a rear bearing 110.
  • the pump body 108 may be secured to an internal combustion engine and an appropriate rotary drive from the engine is used to rotate the camshaft 105.
  • Each of the pumping assemblies 102,103,104 is substantially identical to each other and is substantially identical to the pumping assemblies 2,3,4 of the embodiment of the invention shown in Figures 1-3. In the interests of brevity only the pumping assembly 102 will be described in detail.
  • the pumping assembly 102 comprises a cylinder block 111 which defines a pumping chamber 112.
  • a pumping plunger 113 is slidably mounted in the cylinder 112 and, in use, is reciprocated along the cylinder to vary the volume of a pumping chamber defined by the pumping plunger and the cylinder block 111.
  • a delivery valve 115 is provided to permit discharge of pumped fluid from the pumping chamber.
  • Suitable passages provided in the cylinder block 111 interconnect the discharge valves 115 of the respective pumping assemblies 102, 103 and 104 and provide a discharge passage for pumped fluid.
  • Each pumping plunger 113 is connected to an associated tappet assembly 120.
  • the tappet assembly, and the means of connection between the tappet assembly and the pumping plunger, may conveniently be as described above in relation to Figure 1. However, the invention is not limited to such an arrangement and any suitable arrangement may be made to connect the pumping plunger to the tappet assembly.
  • a roller 123 is carried by the tappet assembly 120 and engages the surface of the cam 106.
  • a working chamber 130 is defined between the tappet assembly 120 and the cylinder block 111. It will be noted that the working chamber 130 has a volume which increases as the volume of the pumping chamber increases, and decreases as the volume of the pumping chamber decreases.
  • Suitable means are provided for supplying a working fluid under pressure to the working chambers 130.
  • the working fluid can be pressurised lubricating oil and the means for delivering the working fluid can be a lubricating oil pump associated with the engine to which the high pressure pump of the present invention is attached. It is to be understood however that any suitable working fluid, supplied by any suitable means, may be used to pressurise the working chamber 130.
  • the working fluid acts on the tappet assembly 120 over a working area substantially equal to the difference between the diameter of the bore 122 in which the tappet assembly 130 works and the area of the cylinder 112 in which the pumping plunger 113 works.
  • This area is large compared with the working area of the pumping plunger 113 and the application of lubricating oil as a working fluid at a moderate pressure is able to produce a sufficiently large force on the pumping plunger 113 to move the pumping plunger from its second (top dead centre) position to its first (bottom dead centre) position.
  • During forward (pumping) strokes of the pumping plunger it is driven from its first (bottom dead centre) to its second (top dead centre) position by its associated cam 106.
  • This forward stroke of the pumping plunger working fluid under pressure remains within the working chamber 130.
  • the force available from the cam is sufficient to overcome the force created by the pressurised working fluid within the working fluid chamber 130 and, in addition, provides the necessary force to drive high pressure fluid from the pumping chamber of the pump.
  • the chambers 130 may conveniently be combined as a trough to permit fluid exchange with low flow resistance.
  • a suitable connection may be provided between the chambers by means of drillings and/or slots in a manner similar to that of the embodiment of Figures 1-3.
  • an accumulator may be provided to maintain working fluid pressure in the working chamber and to receive fluid from the working chambers as their volume varies in use.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
EP99305492A 1998-07-14 1999-07-12 Pompes volumétriques Withdrawn EP0972936A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GBGB9815272.1A GB9815272D0 (en) 1998-07-14 1998-07-14 Positive displacement pumps
GB9815272 1998-07-14

Publications (2)

Publication Number Publication Date
EP0972936A2 true EP0972936A2 (fr) 2000-01-19
EP0972936A3 EP0972936A3 (fr) 2000-07-19

Family

ID=10835501

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99305492A Withdrawn EP0972936A3 (fr) 1998-07-14 1999-07-12 Pompes volumétriques

Country Status (4)

Country Link
EP (1) EP0972936A3 (fr)
JP (1) JP2000038971A (fr)
KR (1) KR20000016935A (fr)
GB (1) GB9815272D0 (fr)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1184568A2 (fr) 2000-08-31 2002-03-06 Delphi Technologies, Inc. Pompe à carburant
EP1431577A1 (fr) * 2002-12-17 2004-06-23 Delphi Technologies, Inc. Pompe à carburant
WO2005054675A1 (fr) * 2003-12-03 2005-06-16 Robert Bosch Gmbh Pompe a pistons radiaux, destinee notamment a des systemes d'injection de carburant
WO2009013068A1 (fr) 2007-07-20 2009-01-29 Robert Bosch Gmbh Pompe haute pression avec poussoir à galet pour carburant
EP2050952A1 (fr) * 2007-10-16 2009-04-22 Delphi Technologies, Inc. Pompe à carburant
WO2009059834A1 (fr) * 2007-11-05 2009-05-14 Robert Bosch Gmbh Pompe à haute pression pour carburant
CN102121466A (zh) * 2011-04-15 2011-07-13 浙江大农实业有限公司 一种柱塞泵泵头结构
EP2535584A1 (fr) * 2011-06-15 2012-12-19 Delphi Technologies Holding S.à.r.l. Ensemble de pompe
CN103266973A (zh) * 2013-05-31 2013-08-28 龙口龙泵燃油喷射有限公司 一种径向式高速柴油机高压供油泵
JP2015507130A (ja) * 2012-02-09 2015-03-05 デルファイ・インターナショナル・オペレーションズ・ルクセンブルク・エス・アー・エール・エル 燃料ポンプに関する改善
CN106762273A (zh) * 2017-03-21 2017-05-31 北京亚新科天纬油泵油嘴股份有限公司 一种机油润滑的高压燃油泵
CN111594366A (zh) * 2019-02-20 2020-08-28 株式会社电装 燃料喷射泵
CN113931773A (zh) * 2020-07-13 2022-01-14 发动机引擎解决方案知识产权股份有限公司 用于发动机的系统和用于高压燃油泵的系统

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100686066B1 (ko) * 2000-02-28 2007-02-23 엘지전자 주식회사 광 기록매체의 제어 장치
JP4618416B2 (ja) * 2004-11-16 2011-01-26 株式会社アドヴィックス ラジアルプランジャポンプ
DE102015222463A1 (de) * 2015-11-13 2017-05-18 Hyundai Motor Company Pumpe für eine Einspritzdüse und Verfahren zum Herstellen einer Pumpe

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB533961A (en) * 1939-08-22 1941-02-25 Arthur John Rowledge Improvements in or relating to reciprocating pumps
US2702008A (en) * 1952-06-09 1955-02-15 John M Stockard Pumping apparatus
US4687426A (en) * 1984-07-31 1987-08-18 Fuji Techno Kogyo Kabushiki Kaisha Constant volume pulsation-free reciprocating pump
DE19531873C1 (de) * 1995-08-30 1996-11-07 Daimler Benz Ag Kraftstoffhochdruckpumpe für eine Brennkraftmaschine
EP0856661A2 (fr) * 1997-01-30 1998-08-05 Lucas Industries Public Limited Company Pompe de carburant

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB533961A (en) * 1939-08-22 1941-02-25 Arthur John Rowledge Improvements in or relating to reciprocating pumps
US2702008A (en) * 1952-06-09 1955-02-15 John M Stockard Pumping apparatus
US4687426A (en) * 1984-07-31 1987-08-18 Fuji Techno Kogyo Kabushiki Kaisha Constant volume pulsation-free reciprocating pump
DE19531873C1 (de) * 1995-08-30 1996-11-07 Daimler Benz Ag Kraftstoffhochdruckpumpe für eine Brennkraftmaschine
EP0856661A2 (fr) * 1997-01-30 1998-08-05 Lucas Industries Public Limited Company Pompe de carburant

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1184568A2 (fr) 2000-08-31 2002-03-06 Delphi Technologies, Inc. Pompe à carburant
EP1184568A3 (fr) * 2000-08-31 2002-06-12 Delphi Technologies, Inc. Pompe à carburant
EP1431577A1 (fr) * 2002-12-17 2004-06-23 Delphi Technologies, Inc. Pompe à carburant
WO2005054675A1 (fr) * 2003-12-03 2005-06-16 Robert Bosch Gmbh Pompe a pistons radiaux, destinee notamment a des systemes d'injection de carburant
WO2009013068A1 (fr) 2007-07-20 2009-01-29 Robert Bosch Gmbh Pompe haute pression avec poussoir à galet pour carburant
EP2050952A1 (fr) * 2007-10-16 2009-04-22 Delphi Technologies, Inc. Pompe à carburant
CN101849099B (zh) * 2007-11-05 2012-08-22 罗伯特·博世有限公司 高压燃料泵
WO2009059834A1 (fr) * 2007-11-05 2009-05-14 Robert Bosch Gmbh Pompe à haute pression pour carburant
CN102121466A (zh) * 2011-04-15 2011-07-13 浙江大农实业有限公司 一种柱塞泵泵头结构
CN102121466B (zh) * 2011-04-15 2012-10-10 浙江大农实业有限公司 一种柱塞泵泵头结构
EP2535584A1 (fr) * 2011-06-15 2012-12-19 Delphi Technologies Holding S.à.r.l. Ensemble de pompe
JP2015507130A (ja) * 2012-02-09 2015-03-05 デルファイ・インターナショナル・オペレーションズ・ルクセンブルク・エス・アー・エール・エル 燃料ポンプに関する改善
CN103266973A (zh) * 2013-05-31 2013-08-28 龙口龙泵燃油喷射有限公司 一种径向式高速柴油机高压供油泵
CN106762273A (zh) * 2017-03-21 2017-05-31 北京亚新科天纬油泵油嘴股份有限公司 一种机油润滑的高压燃油泵
CN106762273B (zh) * 2017-03-21 2022-05-20 北油电控燃油喷射系统(天津)有限公司 一种机油润滑的高压燃油泵
CN111594366A (zh) * 2019-02-20 2020-08-28 株式会社电装 燃料喷射泵
CN113931773A (zh) * 2020-07-13 2022-01-14 发动机引擎解决方案知识产权股份有限公司 用于发动机的系统和用于高压燃油泵的系统
CN113931773B (zh) * 2020-07-13 2024-02-23 发动机引擎解决方案知识产权股份有限公司 用于发动机的系统和用于高压燃油泵的系统

Also Published As

Publication number Publication date
EP0972936A3 (fr) 2000-07-19
GB9815272D0 (en) 1998-09-09
JP2000038971A (ja) 2000-02-08
KR20000016935A (ko) 2000-03-25

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