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US20080175731A1 - Transfer pump for injection of fuel at high pressure - Google Patents

Transfer pump for injection of fuel at high pressure Download PDF

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Publication number
US20080175731A1
US20080175731A1 US11/878,975 US87897507A US2008175731A1 US 20080175731 A1 US20080175731 A1 US 20080175731A1 US 87897507 A US87897507 A US 87897507A US 2008175731 A1 US2008175731 A1 US 2008175731A1
Authority
US
United States
Prior art keywords
piston
cam
oil
roller
fuel
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
US11/878,975
Inventor
Florent Sellas
Eric Martin
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.)
Siemens Automotive Hydraulics SA
Original Assignee
Siemens Automotive Hydraulics SA
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 Siemens Automotive Hydraulics SA filed Critical Siemens Automotive Hydraulics SA
Assigned to SIEMENS AUTOMOTIVE HYDRAULICS SA reassignment SIEMENS AUTOMOTIVE HYDRAULICS SA ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MARTIN, ERIC, SELLAS, FLORENT
Publication of US20080175731A1 publication Critical patent/US20080175731A1/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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • 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
    • 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
    • F04B1/0413—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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/08—Machines, pumps, or pumping installations having flexible working members having tubular flexible members
    • F04B43/084—Machines, pumps, or pumping installations having flexible working members having tubular flexible members the tubular member being deformed by stretching or distortion
    • 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
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements

Definitions

  • the present invention relates to improvements in pumps for the injection of fuel at high pressure, of the type comprising a piston delivering hydraulic fluid into a deformable element such as a bellows, the deformations of said bellows in a cylindrical chamber filled with fuel giving rise to a pumping effect of said fuel toward high pressure injectors.
  • the present invention has for its object to provide a solution to two problems which arise from mounting this type of pump on motors.
  • the solution of the first problem consists in designing the pump such that the oil portion comprises not only the pumping portion but also all the drive portion and angle change.
  • the solution of the second problem consists in providing a free wheel between the drive shaft and the cam.
  • FIG. 1 is a cross-sectional view of an embodiment of the transfer pump according to the invention
  • FIG. 2 is a cross-sectional view on A-A of FIG. 1 ,
  • FIG. 3 is a fragmentary view showing a modification of FIG. 2 .
  • the pump according to the invention comprises a drive shaft 1 , connected by an Oldham joint 2 to the drive member (camshaft for example) not shown.
  • the shaft is carried by a housing 3 .
  • the shaft carries a cam 5 , which, in the illustrated example, comprises four lugs 6 .
  • a piston 10 comes to bear by means of a spring 11 against the cam 5 , with interposition between the piston 10 and the cam 5 of roller 7 , carried by a shaft 8 by means a needle bearing 9 .
  • the external wall of the bearing member 12 comprises recesses which facilitate the passage of oil about this member 12 .
  • the piston 10 urged by spring 11 , slides in a sleeve 13 .
  • the end 13 a of the sleeve 13 enters a bellows 14 , provided at its lower end with a circular member 15 , urged by a return spring 16 .
  • a disc 17 which comprises at its center a bore 19 , in which slides a finger 18 , carried by said circular member 15 , at its center. This ensures correct guiding of the bellows 14 during its successive elongations.
  • the guidance of the bellows 14 permits decreasing and best adjusting the diameter of the chamber 20 in which said bellows expands; this chamber 20 being filled with fuel.
  • FIG. 1 it is seen that the cam 5 turns within a circular chamber 21 provided within the housing 3 .
  • This chamber 21 ; the bore 22 within which slides the roller 7 , the bearing member 12 and the upper portion of the piston 10 ; the internal bore 10 a of said piston; the internal bore of the sleeve 13 and the interior of the bellows 14 are filled with a hydraulic liquid.
  • This liquid passes about the member 12 and also within it where it traverses the partition 12 a through the openings 23 ; then it enters the internal bore 10 a of the piston 10 through the opening 24 and passes through the disc 17 by its openings 25 .
  • a volume compensator 26 which communicates with the chamber 21 in which the cam 5 acts ( FIG. 1 ).
  • volume compensator 27 which communicates with the bore 22 ( FIG. 2 ).
  • non-return valve 28 is disposed in the internal bore 10 a of the piston 10 .
  • the sealing of the oil portion of the pump is ensured by a simple joint with loops 30 disposed between the shaft 1 and housing 3 .
  • FIG. 3 shows a modified embodiment of the upper portion of FIG. 2 , showing the drive mechanism above the cam 5 .
  • the cam 5 is, in this example, of one piece with the motor shaft 1 , the transmission by Oldham joint 2 comprising a freewheel mechanism 3 .
  • the portion forming a cam 5 comprises a cylindrical cup 32 in which will engage a cylindrical axle 31 with interposition between said axle 31 and the internal wall of the cup, of a guide element.
  • the roller bearing 4 carrying shaft 1 is located outside the housing 3 , the sealing joint with loops 30 being in the housing 3 , between the roller bearing 4 and the cam 5 .
  • roller bearing 4 is not lubricated by the hydraulic oil but by the motor oil.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Jet Pumps And Other Pumps (AREA)

Abstract

A transfer pump for the injection of fuel under high pressure of the type comprising a piston (10) providing the hydraulic liquid to a deformable bellows (14), the deformations of said bellows (14) in a cylindrical chamber (20) filled with fuel giving rise to a high pressure pumping effect of said fuel; a cam (5) provided with lugs (6) carried by a drive shaft (1), is characterized in that the oil portion of the pump comprises: the portion of the drive shaft (1) bearing the cam (5); the cam (5) and its lugs (6); the roller (7) with its shaft (8) and its roller bearing (9) carried by a bearing member (12), by which roller the cam(5) bears on the piston (10); as well as the upper portion of said piston (10); such that all the mechanical drive portion and angle change are bathed in the oil of the oil portion.

Description

  • The present invention relates to improvements in pumps for the injection of fuel at high pressure, of the type comprising a piston delivering hydraulic fluid into a deformable element such as a bellows, the deformations of said bellows in a cylindrical chamber filled with fuel giving rise to a pumping effect of said fuel toward high pressure injectors.
  • Pumps of this type have been described in U.S. Pat. No. 2,826,068, 2,828,240 and patent application 06/02594 in the name of the applicant.
  • The present invention has for its object to provide a solution to two problems which arise from mounting this type of pump on motors.
  • The first problem arises because in certain motors it is necessary to integrate the direct injection high pressure injection pump at the end of the camshaft or on the transmission pulleys and not directly on the cylinder head. In the case of the utilization of a single piston pump an angle change is necessary, which gives rise to various drawbacks such as: the size of the pump, the requirement for an adaptation housing, lubricating means, noise, wear of the elements etc.
  • The second problem arises because for such a mounting, it is necessary to provide an operating play between the drive means of the pump and the latter, of the Oldham joint type, for example. When the pump is single piston, there are produced large vibrations from the resistive couple of the pump, possibly even with negative peaks, which vibrations can give rise to loosening the contact surfaces which transmit the couple, which loosening generates couple returns in the motor shaft. These couple returns constitute a disturbing element for the operation of the motor such as: coupling jolts on the camshaft or timing chain, unacceptable noise.
  • The solution of the first problem consists in designing the pump such that the oil portion comprises not only the pumping portion but also all the drive portion and angle change.
  • This has the advantages: on the one hand suppression of dynamic sealing in translation on the transfer single piston pump which is very cumbersome and remains difficult to control; on the other hand all the drive elements will be perfectly lubricated. Moreover, the increase of the closed cycle oil volume increases the resistance to oil temperature and decreases the risks of heating.
  • The solution of the second problem consists in providing a free wheel between the drive shaft and the cam.
  • By way of non-limiting example, and to facilitate understanding of the invention, there are shown the following drawings, in which:
  • FIG. 1 is a cross-sectional view of an embodiment of the transfer pump according to the invention,
  • FIG. 2 is a cross-sectional view on A-A of FIG. 1,
  • FIG. 3 is a fragmentary view showing a modification of FIG. 2.
    •
  • Referring to these drawings, it will be seen that the pump according to the invention comprises a drive shaft 1, connected by an Oldham joint 2 to the drive member (camshaft for example) not shown.
  • The shaft is carried by a housing 3.
  • The shaft carries a cam 5, which, in the illustrated example, comprises four lugs 6.
  • A piston 10 comes to bear by means of a spring 11 against the cam 5, with interposition between the piston 10 and the cam 5 of roller 7, carried by a shaft 8 by means a needle bearing 9.
  • Preferably, a bearing member 12 is interposed between the roller 7 and the piston 10. This bearing member 12 is preferably constituted by two oppositely facing cups 12 a, 12 b, separated by a partition 12 c provided with a plurality of openings 23.
  • The external wall of the bearing member 12 comprises recesses which facilitate the passage of oil about this member 12.
  • The piston 10, urged by spring 11, slides in a sleeve 13.
  • The end 13 a of the sleeve 13 enters a bellows 14, provided at its lower end with a circular member 15, urged by a return spring 16.
  • The interior within the sleeve 13 and at its end is disposed a disc 17 which comprises at its center a bore 19, in which slides a finger 18, carried by said circular member 15, at its center. This ensures correct guiding of the bellows 14 during its successive elongations. The guidance of the bellows 14 permits decreasing and best adjusting the diameter of the chamber 20 in which said bellows expands; this chamber 20 being filled with fuel.
  • In FIG. 1 it is seen that the cam 5 turns within a circular chamber 21 provided within the housing 3.
  • This chamber 21; the bore 22 within which slides the roller 7, the bearing member 12 and the upper portion of the piston 10; the internal bore 10 a of said piston; the internal bore of the sleeve 13 and the interior of the bellows 14 are filled with a hydraulic liquid. This liquid passes about the member 12 and also within it where it traverses the partition 12 a through the openings 23; then it enters the internal bore 10 a of the piston 10 through the opening 24 and passes through the disc 17 by its openings 25.
  • This ensures good communication between them, of the various elements filled with oil.
  • There is this obtained a relatively great volume of the volume of oil which his continually pumped, which improves the lifetime of this oil and decreases the risk of heating.
  • To avoid the effects of pulsations adapted to be provoked by the movements of the lugs 6 of the cam 5, there can preferably be used a volume compensator 26, which communicates with the chamber 21 in which the cam 5 acts (FIG. 1).
  • For the same reason, there can be provided a volume compensator 27, which communicates with the bore 22 (FIG. 2).
  • Moreover, the non-return valve 28 is disposed in the internal bore 10 a of the piston 10.
  • This has the result that only the portion 29 of said bore 10 a, located downstream of the non-return valve 28, is placed under pressure and hence only a small volume of oil is placed under pressure, whilst the rest of the volume of oil is not pressurized. During rising movement of the piston 10, under the action of the return spring 11, the communication is re-established between the oil which has been pressurized and all the rest which has not been.
  • To contributes to avoiding heating of the oil.
  • As the shaft 1 is driven by a freewheel mechanism, the shocks which are transmitted to the came 5 are not transmitted to the drive shaft 1.
  • The sealing of the oil portion of the pump is ensured by a simple joint with loops 30 disposed between the shaft 1 and housing 3.
  • All the components of the mechanical drive portion: cam 5, roller 7 and its roller bearing 9, bearing member 12 sliding in the bore 22, are immersed in the oil and are perfectly lubricated.
  • FIG. 3 shows a modified embodiment of the upper portion of FIG. 2, showing the drive mechanism above the cam 5.
  • In this figure, the same elements bear the same reference numerals.
  • The cam 5 is, in this example, of one piece with the motor shaft 1, the transmission by Oldham joint 2 comprising a freewheel mechanism 3.
  • The portion forming a cam 5 comprises a cylindrical cup 32 in which will engage a cylindrical axle 31 with interposition between said axle 31 and the internal wall of the cup, of a guide element.
  • The roller bearing 4 carrying shaft 1 is located outside the housing 3, the sealing joint with loops 30 being in the housing 3, between the roller bearing 4 and the cam 5.
  • In this embodiment, the roller bearing 4 is not lubricated by the hydraulic oil but by the motor oil.

Claims (7)

1. Transfer pump for injection of high pressure fuel of the type comprising a piston (10) supplying hydraulic liquid to a deformable bellows (14), the deformations of said bellows (14) in a cylindrical chamber (20) filled with fuel, giving rise to a pumping effect at high pressure of said fuel; a cam (5) provided with lugs (6) carried by a drive shaft (1), characterized by the fact that the oil portion of the pump comprises: the portion of the drive shaft (1) bearing the cam (5); the cam (5) and its lugs (6); the roller (7) with its shaft (8) and its roller bearing (9) carried by a bearing member (12), by which roller the cam (5) bears on the piston (10); as well as the upper portion of said piston (10): such that all the mechanical drive portion and the angle change bathe in the oil of the oil portion.
2. Transfer pump according to claim 1, in which the sealing between the oil portion and the drive shaft (1) is ensured by a simple joint with loops (30).
3. Transfer pump according to claim 1, in which the chamber (21) of the housing (3) in which the cam (5) works is connected to a volume compensator (26).
4. Transfer pump according to claim 3, in which a second volume compensator (27) is connected to the bore (22) in which operate the roller (7), the bearing member (12) and the upper portion of the piston (10).
5. Pump according to claim 4, in which the piston (10) comprises an internal bore (10 a) communicating with said bore (22) by an opening (24) and comprises a non-return valve (28); such that the volume of oil placed under pressure is small.
6. Pump according to claim 5, in which the piston (10) sides in a sleeve (13) provided at its base with a disc (17) having a bore (19) in which slides a finger (18) carried by a member (15) fixed to the base of the bellows (14); so as to ensure the guidance of said bellows (14) during its successive deformations.
7. Pump according to claim 1, in which the shaft drive mechanism for the shaft (1) is a freewheel mechanism.
US11/878,975 2006-08-04 2007-07-30 Transfer pump for injection of fuel at high pressure Abandoned US20080175731A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0607181A FR2904665B1 (en) 2006-08-04 2006-08-04 TRANSFER PUMP FOR HIGH PRESSURE FUEL INJECTION
FR06/07181 2006-08-04

Publications (1)

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US20080175731A1 true US20080175731A1 (en) 2008-07-24

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US11/878,975 Abandoned US20080175731A1 (en) 2006-08-04 2007-07-30 Transfer pump for injection of fuel at high pressure

Country Status (7)

Country Link
US (1) US20080175731A1 (en)
EP (1) EP1884656B1 (en)
JP (1) JP2008038909A (en)
KR (1) KR20080012799A (en)
AT (1) ATE449905T1 (en)
DE (1) DE602007003414D1 (en)
FR (1) FR2904665B1 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110088506A1 (en) * 2008-05-12 2011-04-21 Ntn Corporation Pump tappet
GB2481524A (en) * 2010-06-22 2011-12-28 Bosch Gmbh Robert Piston pump with bellows
EP3173611A1 (en) * 2015-11-24 2017-05-31 Delphi International Operations Luxembourg S.à r.l. High pressure fuel pump

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009270693A (en) * 2008-05-12 2009-11-19 Ntn Corp Pump tappet
JP2009293395A (en) * 2008-06-02 2009-12-17 Ntn Corp Pump tappet
JP2009293604A (en) * 2008-06-09 2009-12-17 Ntn Corp Pump tappet
JP2009293393A (en) * 2008-06-02 2009-12-17 Ntn Corp Pump tappet
DE102008059004A1 (en) * 2008-11-25 2010-05-27 Schaeffler Kg roller plunger
DE102010001237B4 (en) * 2009-12-01 2024-09-12 Continental Automotive Technologies GmbH Method for mounting a spring stop of a piston return spring by means of a locking mechanism on a pump piston of a piston pump
GB2559612B (en) * 2017-02-13 2020-04-01 Delphi Tech Ip Ltd Damper device with a capsule held in a rubber holder maintained in position by a metallic plug
FR3105252B1 (en) 2019-12-23 2023-01-20 Syctom Lagence Metropolitaine Des Dechets Menagers Device for injecting an organic resource under high pressure
FR3105207B1 (en) 2019-12-23 2022-04-29 Syctom Lagence Metropolitaine Des Dechets Menagers Device for high pressure injection of a wet mixture
FR3112089B1 (en) 2020-07-02 2024-01-19 Commissariat Energie Atomique DEVICE FOR INJECTING AN EFFLUENT UNDER HIGH PRESSURE
IT202300005475A1 (en) * 2023-03-22 2024-09-22 Fca Italy Spa “CYLINDER HEAD FOR AN INTERNAL COMBUSTION ENGINE WITH A FUEL PUMP INTEGRATED IN THE CYLINDER HEAD AND DRIVEN BY A CAMSHAFT”

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US2343962A (en) * 1941-02-25 1944-03-14 Dodson Edward Measuring pump
US2395330A (en) * 1942-09-11 1946-02-19 Dayton Liquid Meter Co Oil circulatory system employed in fuel injection pumps
US2410947A (en) * 1943-04-19 1946-11-12 Caterpillar Tractor Co Fuel injection pum mechanism
US2440194A (en) * 1946-01-29 1948-04-20 Texas Co Fuel pump
US2897808A (en) * 1956-07-31 1959-08-04 Bendix Aviat Corp Fuel injection system
US4008009A (en) * 1975-09-30 1977-02-15 Endre Kovacs Fuel injection pump
US4487173A (en) * 1978-12-08 1984-12-11 Luk Lamellen Und Kupplungsbau Gmbh Apparatus for starting an internal combustion engine
US20060062677A1 (en) * 2003-02-11 2006-03-23 Marco Ganser High pressure pump

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JPH1122648A (en) * 1997-07-04 1999-01-26 Nissan Motor Co Ltd Fuel pump
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JPH11324861A (en) * 1998-05-19 1999-11-26 Mitsubishi Electric Corp Fuel injection pump
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JP3758480B2 (en) * 2000-08-25 2006-03-22 国産電機株式会社 Diaphragm pump
FR2826068B1 (en) * 2001-06-19 2004-02-13 Siemens Automotive Hydraulics FLOW REGULATION DEVICE FOR TRANSFER FUEL PUMP
FR2828240B1 (en) * 2001-08-03 2003-12-12 Siemens Automotive Hydraulics REGULATING DEVICE FOR FUEL TRANSFER PUMP
JP4090382B2 (en) * 2003-04-21 2008-05-28 株式会社日立製作所 Fuel supply apparatus for in-cylinder injection internal combustion engine
JP2006118448A (en) * 2004-10-22 2006-05-11 Denso Corp Fuel injection pump

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2343962A (en) * 1941-02-25 1944-03-14 Dodson Edward Measuring pump
US2395330A (en) * 1942-09-11 1946-02-19 Dayton Liquid Meter Co Oil circulatory system employed in fuel injection pumps
US2410947A (en) * 1943-04-19 1946-11-12 Caterpillar Tractor Co Fuel injection pum mechanism
US2440194A (en) * 1946-01-29 1948-04-20 Texas Co Fuel pump
US2897808A (en) * 1956-07-31 1959-08-04 Bendix Aviat Corp Fuel injection system
US4008009A (en) * 1975-09-30 1977-02-15 Endre Kovacs Fuel injection pump
US4487173A (en) * 1978-12-08 1984-12-11 Luk Lamellen Und Kupplungsbau Gmbh Apparatus for starting an internal combustion engine
US20060062677A1 (en) * 2003-02-11 2006-03-23 Marco Ganser High pressure pump

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110088506A1 (en) * 2008-05-12 2011-04-21 Ntn Corporation Pump tappet
GB2481524A (en) * 2010-06-22 2011-12-28 Bosch Gmbh Robert Piston pump with bellows
EP3173611A1 (en) * 2015-11-24 2017-05-31 Delphi International Operations Luxembourg S.à r.l. High pressure fuel pump

Also Published As

Publication number Publication date
FR2904665A1 (en) 2008-02-08
EP1884656B1 (en) 2009-11-25
DE602007003414D1 (en) 2010-01-07
ATE449905T1 (en) 2009-12-15
JP2008038909A (en) 2008-02-21
FR2904665B1 (en) 2008-10-31
EP1884656A1 (en) 2008-02-06
KR20080012799A (en) 2008-02-12

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AS Assignment

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