GB2563263B - HP pump for diesel injection systems - Google Patents

HP pump for diesel injection systems Download PDF

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Publication number
GB2563263B
GB2563263B GB1709139.8A GB201709139A GB2563263B GB 2563263 B GB2563263 B GB 2563263B GB 201709139 A GB201709139 A GB 201709139A GB 2563263 B GB2563263 B GB 2563263B
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GB
United Kingdom
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.)
Active
Application number
GB1709139.8A
Other versions
GB2563263A (en
GB201709139D0 (en
Inventor
Williams Ryan
Mercer Adam
Male Andrew
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 IP Ltd
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
Priority to GB1709139.8A priority Critical patent/GB2563263B/en
Publication of GB201709139D0 publication Critical patent/GB201709139D0/en
Priority to EP18729676.9A priority patent/EP3635240B1/en
Priority to PCT/EP2018/065097 priority patent/WO2018224624A1/en
Publication of GB2563263A publication Critical patent/GB2563263A/en
Application granted granted Critical
Publication of GB2563263B publication Critical patent/GB2563263B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F02M59/44—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

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 INVENTION 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 opening in said compression chamber 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 without touching the faces of the 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 46 outer face 48 inner face - recess lateral face 50 cylindrical member 52 lateral face of the cylindrical member 54 end face of the cylindrical member

Claims (3)

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 and opening in said 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 engage in said recess (40) without touching the faces of the recess (40) when the piston reaches the top dead centre (TDC) position.
2. HP pump (10) as claimed in claim 1 wherein the recess (40) is a cylindrical hollow.
3. 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.
GB1709139.8A 2017-06-08 2017-06-08 HP pump for diesel injection systems Active GB2563263B (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
GB1709139.8A GB2563263B (en) 2017-06-08 2017-06-08 HP pump for diesel injection systems
EP18729676.9A EP3635240B1 (en) 2017-06-08 2018-06-07 Hp pump for diesel injection systems
PCT/EP2018/065097 WO2018224624A1 (en) 2017-06-08 2018-06-07 Hp pump for diesel injection systems

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB1709139.8A GB2563263B (en) 2017-06-08 2017-06-08 HP pump for diesel injection systems

Publications (3)

Publication Number Publication Date
GB201709139D0 GB201709139D0 (en) 2017-07-26
GB2563263A GB2563263A (en) 2018-12-12
GB2563263B true GB2563263B (en) 2019-06-12

Family

ID=59358190

Family Applications (1)

Application Number Title Priority Date Filing Date
GB1709139.8A Active GB2563263B (en) 2017-06-08 2017-06-08 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 (1)

* 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

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090065292A1 (en) * 2007-09-07 2009-03-12 Gm Global Technology Operations, Inc. Low Noise Fuel Injection Pump
WO2015121010A1 (en) * 2014-02-13 2015-08-20 Delphi International Operations Luxembourg S.À R.L. High pressure fuel pump
WO2016119951A1 (en) * 2015-01-27 2016-08-04 Delphi International Operations Luxembourg S.À R.L. Plunger assembly

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5187255B2 (en) * 2009-03-27 2013-04-24 株式会社デンソー High pressure pump
GB201506173D0 (en) * 2015-04-13 2015-05-27 Delphi Internat Operations Luxembourg S � R L Fuel pump

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090065292A1 (en) * 2007-09-07 2009-03-12 Gm Global Technology Operations, Inc. Low Noise Fuel Injection Pump
WO2015121010A1 (en) * 2014-02-13 2015-08-20 Delphi International Operations Luxembourg S.À R.L. High pressure fuel pump
WO2016119951A1 (en) * 2015-01-27 2016-08-04 Delphi International Operations Luxembourg S.À R.L. Plunger assembly

Also Published As

Publication number Publication date
GB2563263A (en) 2018-12-12
EP3635240A1 (en) 2020-04-15
WO2018224624A1 (en) 2018-12-13
EP3635240B1 (en) 2021-08-11
GB201709139D0 (en) 2017-07-26

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