EP3635240A1 - Hp pump for diesel injection systems - Google Patents

Hp pump for diesel injection systems

Info

Publication number
EP3635240A1
EP3635240A1 EP18729676.9A EP18729676A EP3635240A1 EP 3635240 A1 EP3635240 A1 EP 3635240A1 EP 18729676 A EP18729676 A EP 18729676A EP 3635240 A1 EP3635240 A1 EP 3635240A1
Authority
EP
European Patent Office
Prior art keywords
recess
pump
piston
bore
compression chamber
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.)
Granted
Application number
EP18729676.9A
Other languages
German (de)
French (fr)
Other versions
EP3635240B1 (en
Inventor
Ryan Williams
Adam MERCER
Andrew Male
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.)
Borgwarner US Technologies LLC
Original Assignee
Delphi Technologies IP 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 Delphi Technologies IP Ltd filed Critical Delphi Technologies IP Ltd
Publication of EP3635240A1 publication Critical patent/EP3635240A1/en
Application granted granted Critical
Publication of EP3635240B1 publication Critical patent/EP3635240B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F02M59/44—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
    • 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
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/464—Inlet valves of the check valve 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/167—Means for compensating clearance or thermal expansion
    • 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
    • F04B1/0408—Pistons
    • 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
    • F04B1/0452—Distribution members, e.g. 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F04B53/144—Adaptation of piston-rods
    • 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
    • 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
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0035—Poppet valves, i.e. having a mushroom-shaped valve member that moves perpendicularly to the plane of the valve seat

Definitions

  • the present invention relates to a cam actuated high pressure diesel pump and, more precisely to means preventing fuel leakage between the piston and the bore of the pump.
  • a cam actuated diesel fuel high pressure pump compresses fuel in a compression chamber defined at the end of a bore and which volume is cyclically varied by a piston guided and reciprocally moving in said bore.
  • Fuel enters the compression chamber via an inlet opening arranged at the end of the bore and which is controlled by an inlet valve member aligned with the piston and exits once compressed via an outlet controlled by a check valve.
  • TDC top dead centre
  • the end of the piston is provided with a recess defining a cylindrical peripheral wall that also radially dilates under pressure inside said recess, compensating the dilation of the bore and keeping the functional clearance minimal.
  • this recess helps in reducing the leaks, it also increases the "dead volume" of fuel in the pumping chamber, and this reduces the portion of the swept volume of the pump that can be delivered. This loss of delivery, or volumetric efficiency, may mean that the pump no longer meets the required specification and it will be necessary to increase plunger diameter or stroke to compensate. These changes are undesirable as they increase stress and pump size.
  • a high pressure pump adapted to be arranged in a diesel fuel injection system wherein, in use, said HP pump pressurises fuel in a compression chamber defined by a coaxial arrangement of a bore extending along a main axis, a piston guided in the bore and an inlet valve member axially controlling an inlet arranged at the very end of the bore and wherein, the piston is provided with a recess arranged at its end partially defining said compression chamber, said recess defining a peripheral wall and a bottom face and wherein, the inlet valve member is provided with a head member arranged to complementary engage in said recess when the piston reaches the top dead centre (TDC) position.
  • TDC top dead centre
  • peripheral wall is adapted to radially expand when the piston reaches said TDC.
  • the recess is a cylindrical hollow.
  • the head member is smaller in dimension than the recess defining between them a clearance of about 0.5 mm.
  • Figure 1 is an axial section of a HP pump as per the invention.
  • Figure 2 is a detail of figure 1.
  • a diesel internal combustion engine is provided with a fuel injection equipment arranged to cyclically spray compressed diesel fuel in its cylinders.
  • Said equipment comprises a high pressure pump 10, shown in axial section on figure 1, having a body 12 provided with a bore 14 extending along a main axis X from a closed top end partially defining a compression chamber 16 to an open bottom end.
  • a piston 18 axially X extending from a top end 20, also partially defining said compression chamber 16, to a lower end 22 protruding through the bore bottom opening for cooperating with a cam, not shown.
  • the cam rotates and imparts to the piston axial X reciprocal displacements defining a pumping cycle between a top dead center position (TDC) where the volume of the compression chamber is minimum and a bottom dead center position (BDC) where said volume is maximum.
  • TDC top dead center position
  • BDC bottom dead center position
  • the fuel enters the compression chamber 16 via an inlet 24 wherein it is compressed to thousands of bars then is expelled via an outlet 26.
  • the outlet 26 comprises a channel angularly drilled in the body 12 at about 45° from the main axis X, said channel opening in the upper wall of the compression chamber. Moreover, said channel is controlled by a check valve 28 comprising a ball biased by a spring against a seat face, said check valve 28 opening in use, when, around TDC, the pressure in the compression chamber 16 is high enough to push the ball away from the seating face.
  • a check valve 28 comprising a ball biased by a spring against a seat face, said check valve 28 opening in use, when, around TDC, the pressure in the compression chamber 16 is high enough to push the ball away from the seating face.
  • Other type of check valves are also known in the art .
  • the inlet 24 is aligned to the bore and to the piston and is arranged at the very end of the bore 14 where it is surrounded by an annular seat face 30 defined on the upper wall of the compression chamber. Said inlet 24 is controlled by an inlet valve member 32 cooperating with an electro -magnetic actuator but, in an alternative embodiment the inlet valve member 32 is passive and is only moving under the influence of pressure differences.
  • the inlet valve member 32 is a poppet valve type having an elongated stem 34 at an end of which is a head member 36.
  • the stem 34 is axially X guided in the body and, the head 36 widens from the stem and protrudes in the compression chamber 16.
  • the head 36 defines a sealing face 38 adapted to cooperate with the seat face 30 for opening and closing said inlet 24.
  • the top end 20 of the piston is provided with a recess 40 having a depth H40 and an diameter D40, said recess 40 opening in the upper face of said piston and defining a bottom face 42.
  • the piston forms a cylindrical peripheral wall 44 which outer face 46 slides against the face of the bore 14 and which inner face 48 is the lateral face of the recess.
  • the head 36 of the inlet valve member is a cylindrical member 50 having a lateral face 52 and a transverse end face 54 facing the bottom 42 of the recess.
  • Said cylindrical head member 50 deeply extends in the compression chamber 16 and, when the piston 18 is at TDC, as shown on the figure, said cylindrical head member 50 engages in the recess 40 without touching the faces of the recess, said end face 54 of the head remaining at a distance from the bottom 42 of the recess and, the lateral face 52 being also away from the recess lateral face 48.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

A high pressure pump (10) of a diesel fuel injection system wherein the inlet valve member (32) is provided with a head member (50) arranged to complementary engage in a recess (40) arranged at the end of the piston when said piston reaches the top dead centre (TDC) position.

Description

HP PUMP FOR DIESEL INJECTION SYSTEMS
TECHNICAL FIELD
The present invention relates to a cam actuated high pressure diesel pump and, more precisely to means preventing fuel leakage between the piston and the bore of the pump.
BACKGROUND OF THE FNVENTION
A cam actuated diesel fuel high pressure pump compresses fuel in a compression chamber defined at the end of a bore and which volume is cyclically varied by a piston guided and reciprocally moving in said bore. Fuel enters the compression chamber via an inlet opening arranged at the end of the bore and which is controlled by an inlet valve member aligned with the piston and exits once compressed via an outlet controlled by a check valve. When the piston approaches the top dead centre (TDC) position, the pressure in the compression chamber rises to a maximum and, the bore tends to dilate and further opening the functional clearance and a leak path between the bore and the piston. To prevent further leaks, the end of the piston is provided with a recess defining a cylindrical peripheral wall that also radially dilates under pressure inside said recess, compensating the dilation of the bore and keeping the functional clearance minimal. Although this recess helps in reducing the leaks, it also increases the "dead volume" of fuel in the pumping chamber, and this reduces the portion of the swept volume of the pump that can be delivered. This loss of delivery, or volumetric efficiency, may mean that the pump no longer meets the required specification and it will be necessary to increase plunger diameter or stroke to compensate. These changes are undesirable as they increase stress and pump size. Additionally the power required to compress this undelivered volume increases with the size of the volume and is either lost as heat or as torque reversal in the drive system, reducing the efficiency of the pump and increasing noise proportional to the size of the "dead volume". SUMMARY OF THE INVENTION
Accordingly, it is an object of the present invention to resolve the above mentioned problems in providing a high pressure pump adapted to be arranged in a diesel fuel injection system wherein, in use, said HP pump pressurises fuel in a compression chamber defined by a coaxial arrangement of a bore extending along a main axis, a piston guided in the bore and an inlet valve member axially controlling an inlet arranged at the very end of the bore and wherein, the piston is provided with a recess arranged at its end partially defining said compression chamber, said recess defining a peripheral wall and a bottom face and wherein, the inlet valve member is provided with a head member arranged to complementary engage in said recess when the piston reaches the top dead centre (TDC) position.
Also, wherein said the peripheral wall is adapted to radially expand when the piston reaches said TDC.
Also, wherein the recess is a cylindrical hollow.
Also, wherein the head member is smaller in dimension than the recess defining between them a clearance of about 0.5 mm.
BRIEF DESCRIPTION OF THE DRAWINGS
The present invention is now described by way of example with reference to the accompanying drawings in which:
Figure 1 is an axial section of a HP pump as per the invention.
Figure 2 is a detail of figure 1.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
A diesel internal combustion engine is provided with a fuel injection equipment arranged to cyclically spray compressed diesel fuel in its cylinders.
Said equipment comprises a high pressure pump 10, shown in axial section on figure 1, having a body 12 provided with a bore 14 extending along a main axis X from a closed top end partially defining a compression chamber 16 to an open bottom end. In the bore 14 is guided a piston 18 axially X extending from a top end 20, also partially defining said compression chamber 16, to a lower end 22 protruding through the bore bottom opening for cooperating with a cam, not shown. In use, the cam rotates and imparts to the piston axial X reciprocal displacements defining a pumping cycle between a top dead center position (TDC) where the volume of the compression chamber is minimum and a bottom dead center position (BDC) where said volume is maximum. In use, the fuel enters the compression chamber 16 via an inlet 24 wherein it is compressed to thousands of bars then is expelled via an outlet 26.
The outlet 26 comprises a channel angularly drilled in the body 12 at about 45° from the main axis X, said channel opening in the upper wall of the compression chamber. Moreover, said channel is controlled by a check valve 28 comprising a ball biased by a spring against a seat face, said check valve 28 opening in use, when, around TDC, the pressure in the compression chamber 16 is high enough to push the ball away from the seating face. Other type of check valves are also known in the art .
The inlet 24 is aligned to the bore and to the piston and is arranged at the very end of the bore 14 where it is surrounded by an annular seat face 30 defined on the upper wall of the compression chamber. Said inlet 24 is controlled by an inlet valve member 32 cooperating with an electro -magnetic actuator but, in an alternative embodiment the inlet valve member 32 is passive and is only moving under the influence of pressure differences.
The inlet valve member 32 is a poppet valve type having an elongated stem 34 at an end of which is a head member 36. The stem 34 is axially X guided in the body and, the head 36 widens from the stem and protrudes in the compression chamber 16. The head 36 defines a sealing face 38 adapted to cooperate with the seat face 30 for opening and closing said inlet 24. As it is shown on the section of figure 2, the top end 20 of the piston is provided with a recess 40 having a depth H40 and an diameter D40, said recess 40 opening in the upper face of said piston and defining a bottom face 42. Around the recess 40 the piston forms a cylindrical peripheral wall 44 which outer face 46 slides against the face of the bore 14 and which inner face 48 is the lateral face of the recess.
Complementary to said recess 40, the head 36 of the inlet valve member is a cylindrical member 50 having a lateral face 52 and a transverse end face 54 facing the bottom 42 of the recess. Said cylindrical head member 50 deeply extends in the compression chamber 16 and, when the piston 18 is at TDC, as shown on the figure, said cylindrical head member 50 engages in the recess 40 without touching the faces of the recess, said end face 54 of the head remaining at a distance from the bottom 42 of the recess and, the lateral face 52 being also away from the recess lateral face 48. For instance, successful tests have been carried out with a recess 40 having a depth H40 of 3mm and a diameter D40 of 5mm, the peripheral wall thickness being around 0.7mm and, a cylindrical head member 50 defining between its lateral face 52 and the recess lateral face 48 an annular clearance C of about 0.5 mm.
Thanks to this simple arrangement, when the piston reaches TDC, the volume of the compression chamber 16 reduces, the head member 50 engaging in the recess 48 and occupying the majority of the volume and, the pressure in said compression chamber 16 outwardly pushing the peripheral wall 44 reducing the clearance between the bore 14 and the piston 18 thus limiting the leak path.
LIST OF REFERENCES
X main axis
TDC top dead centre
BDC bottom dead centre
D40 diameter of the recess
H40 depth of the recess
C clearance
10 high pressure pump - HP pump
12 body
14 bore
16 compression chamber
18 piston
20 top end of the piston
22 lower end of the piston
24 inlet
26 outlet
28 check valve
30 seat face
32 inlet valve member
34 stem
36 head
38 sealing face
40 recess
42 bottom face
44 peripheral wall outer face
inner face - recess lateral face cylindrical member
lateral face of the cylindrical member end face of the cylindrical member

Claims

CLAIMS:
1. High pressure pump (10) adapted to be arranged in a diesel fuel injection system wherein, in use, said HP pump (10) pressurises fuel in a compression chamber (16) defined by a coaxial arrangement of a bore (14) extending along a main axis (X), a piston (18) guided in the bore and an inlet valve member (32) axially controlling an inlet (24) arranged at the very end of the bore in the compression chamber and wherein, the piston is provided with a recess (40) arranged at its end partially defining said compression chamber, said recess defining a peripheral wall (44) and a bottom face (42) and wherein, the inlet valve member (32) is provided with a head member (50) arranged to complementary enter in said recess (40) when the piston reaches the top dead centre (TDC) position.
2. HP pump (10) as claimed in the preceding claim wherein said the peripheral wall (44) is adapted to radially expand.
3. HP pump (10) as claimed in any one of the preceding claims wherein the recess (40) is a cylindrical hollow.
4. HP pump (10) as claimed in any one of the claims 1 or 2 wherein the head member (50) is smaller in dimension than the recess (40) defining between them a clearance (C) of about 0.5 mm.
EP18729676.9A 2017-06-08 2018-06-07 Hp pump for diesel injection systems Active EP3635240B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB1709139.8A GB2563263B (en) 2017-06-08 2017-06-08 HP pump for diesel injection systems
PCT/EP2018/065097 WO2018224624A1 (en) 2017-06-08 2018-06-07 Hp pump for diesel injection systems

Publications (2)

Publication Number Publication Date
EP3635240A1 true EP3635240A1 (en) 2020-04-15
EP3635240B1 EP3635240B1 (en) 2021-08-11

Family

ID=59358190

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18729676.9A Active EP3635240B1 (en) 2017-06-08 2018-06-07 Hp pump for diesel injection systems

Country Status (3)

Country Link
EP (1) EP3635240B1 (en)
GB (1) GB2563263B (en)
WO (1) WO2018224624A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2599659B (en) * 2020-10-07 2023-03-29 Delphi Tech Ip Ltd Fuel pump
JP7783702B2 (en) * 2021-07-06 2025-12-10 三菱重工エンジン＆ターボチャージャ株式会社 fuel pump
GB2629351A (en) * 2023-04-24 2024-10-30 Phinia Delphi Luxembourg Sarl Fuel pump

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7610902B2 (en) * 2007-09-07 2009-11-03 Gm Global Technology Operations, Inc. Low noise fuel injection pump
JP5187255B2 (en) * 2009-03-27 2013-04-24 株式会社デンソー High pressure pump
GB201402528D0 (en) * 2014-02-13 2014-04-02 Delphi Int Operations Luxembourg Sarl High pressure fuel pump
GB201501282D0 (en) * 2015-01-27 2015-03-11 Delphi International Operations Luxembourg S.�.R.L. Plunger assembly
GB201506173D0 (en) * 2015-04-13 2015-05-27 Delphi Internat Operations Luxembourg S � R L Fuel pump

Also Published As

Publication number Publication date
EP3635240B1 (en) 2021-08-11
WO2018224624A1 (en) 2018-12-13
GB2563263A (en) 2018-12-12
GB201709139D0 (en) 2017-07-26
GB2563263B (en) 2019-06-12

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