EP3239514A1 - Pompe à carburant haute pression - Google Patents

Pompe à carburant haute pression Download PDF

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Publication number
EP3239514A1
EP3239514A1 EP17167344.5A EP17167344A EP3239514A1 EP 3239514 A1 EP3239514 A1 EP 3239514A1 EP 17167344 A EP17167344 A EP 17167344A EP 3239514 A1 EP3239514 A1 EP 3239514A1
Authority
EP
European Patent Office
Prior art keywords
plunger
inner chamber
high pressure
fuel pump
pressure 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.)
Granted
Application number
EP17167344.5A
Other languages
German (de)
English (en)
Other versions
EP3239514B1 (fr
Inventor
Daniel P. Cust
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 International Operations Luxembourg SARL
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 International Operations Luxembourg SARL filed Critical Delphi International Operations Luxembourg SARL
Publication of EP3239514A1 publication Critical patent/EP3239514A1/fr
Application granted granted Critical
Publication of EP3239514B1 publication Critical patent/EP3239514B1/fr
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
    • F02M59/02—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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/442—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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F04B39/0022—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons piston rods
    • 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

Definitions

  • the present invention relates to a cam actuated high pressure pump and more particularly to a plunger arrangement.
  • a diesel internal combustion engine comprises a fuel injection equipment wherein fuel sucked from a low pressure tank is pressurized at 2000 bars or higher in a cam actuated high pressure pump, prior to be delivered to a high pressure reservoir, or common rail, to which are connected a plurality of fuel injectors.
  • a command unit controls the equipment as a function of the demand of fuel from the ICE.
  • plungers provided with a deep recess opening on their head end.
  • the recess is filled with fuel and, when the pressure rises the peripheral wall of the recess slightly expands and closes, at least partially, the clearance.
  • a high pressure fuel pump having a pumping head wherein a compression chamber is defined between the blind end of a bore and the head end of a plunger slidably adjusted in said bore and adapted to perform therein a pumping cycle varying the volume of said compression chamber.
  • the pump is further provided with inlet and outlet valve assemblies for controlling fuel flowing in and out of said compression chamber.
  • the plunger is provided with an inner chamber arranged in the head end of the plunger that is in the vicinity of the compression chamber, said inner chamber being in fluid communication with the compression chamber via an opening orifice arranged in the head end of the plunger.
  • said plunger inner chamber is defined by a peripheral wall adapted to expand when the plunger inner chamber is under pressure.
  • the high pressure fuel pump is further provided with a check valve assembly arranged to control said fluid communication.
  • said check valve assembly is normally in a closed state of the opening orifice and is arranged to open the fluid communication only when the pressure in the compression chamber exceeds the pressure in the plunger inner chamber.
  • Said check valve assembly comprises a spring member biasing a valve member against a seating face surrounding said opening.
  • valve member and the spring member are both arranged inside the plunger inner chamber.
  • the plunger is provided with a recess arranged on its head end, said recess defining the inner chamber, the peripheral wall axially extending toward a top circular extremity. Said peripheral wall receiving a plugging cap adjusted and fixed to said top circular extremity.
  • the plugging cap is provided with a central opening defining the fluid communication between the compression chamber and the plunger inner chamber and, wherein the valve member and the spring member are arranged in the inner chamber prior to the fixation of the plugging cap on top circular extremity.
  • the plugging cap is screwed within the peripheral wall of the recess.
  • the plunger comprises a main part onto which is adjusted and fixed a tubular head member defining the inner chamber, and the check valve assembly being arranged in place prior to fixing the head member.
  • said head member has a cylindrical peripheral wall extending from a lower end, adapted to be complementary adjusted and fixed onto the main part of the plunger, to an upper end provided with a radial shoulder face provided with the opening orifice.
  • the check valve assembly is arranged in the plunger inner chamber by insertion through the opening orifice, the valve member being adjusted in sliding fit in the orifice of the fluid communication and, having at least one retractable arm member adapted to retract when inserted through said orifice and, to expand once inside the inner chamber, said retractable arm member preventing exit of the check valve assembly through the opening orifice.
  • Said retractable arm member is a flexible arm extending from a first extremity, fixed to said closing member, to a distant free extremity, the arm extending substantially along the lateral face of the closing member while distancing slightly from it, the first extremity being inserted first through the opening orifice when the check valve assembly is inserted in the plunger inner chamber.
  • a high pressure fuel pump 10 adapted to be arranged in a diesel fuel injection equipment not represented.
  • the pump 10 comprises a body 12 wherein a camshaft 14 having a cam 16 is arranged to rotate between two bearings about a cam axis Y.
  • a pumping head 18 On the body 12 is fixedly arranged a pumping head 18 wherein fuel entering via an inlet 20 in a compression chamber 22 exits after being pressurized via an outlet 24.
  • a plunger 26 reciprocally slides between a bottom dead center (BDC) position and a top dead center (TDC) position in a bore 28 of the pumping head 18.
  • the plunger 26 extends along a pumping axis X, perpendicular to the cam axis Y, from a foot end 30, protruding outward the pumping head 18 and cooperating with the cam 16 via a cam follower 32, to a head end 34 that is in the bore and which extreme transverse face 36, or top face 36 of the plunger, partly defines the compression chamber 22.
  • the inlet 20 in controlled by an inlet valve member 38 arranged at the end of the bore 28 and, the outlet 24 radially arranged relative to the compression chamber 22 in controlled by an outlet valve member 40, which in the representation of figure 1 is a check valve with a ball biased by a coil spring in a closed position against a conical seating face.
  • the compression chamber 22 is fully defined by the space comprised between said extreme transverse face 36 of the plunger and the end of the bore 28, being a cylindrical end of the bore and the under face of the inlet valve member 38.
  • the cam 16 In use, when the camshaft 14 rotates, the cam 16 imparts to the plunger 26 said reciprocating movement performing said pumping cycle during which the inner volume of the compression chamber 22 is varied.
  • the plunger 26 is provided on its head end 34 with an inner plunger chamber 46 in fluid communication FC with the compression chamber 22 via a top orifice 48 opening in the transverse top face 36. Said fluid communication FC is controlled by a check valve 50 arranged inside the chamber 46.
  • a first embodiment of the invention is presented on figure 2 where a deep recess provided at the head end of the plunger 26 defines a thin peripheral wall 52 threaded 54 in the region opening in the transverse top face 36.
  • the deepness D of the recess is such that, when in TDC, the peripheral wall 52 extends in the enlarged portion 44 of the bore and also in the lower main part of the bore that is not enlarged. Therefore, the outer face of the peripheral wall 52 is slidably guided against said main bore face.
  • a male threaded plugging cap 56 is complementary screwed in the threaded area of the peripheral wall of the plunger, said cap 56 defining the top transverse face 34 of the plunger and, at the opposite, a top face 58 of the inner chamber 46.
  • Said top face 58 is centrally provided with a conical face so as to form a valve seating face 59, the orifice 48, creating the fluid communication FC, being provided from the tip of said conical or sloped seating face 59 to the opposite top transverse face 36.
  • the position of the cap 56 is permanently secured via a weld seam 60 or any other known fixation means.
  • the check valve 50 is arrange prior to screwing the cap 56.
  • the check valve 50 comprises a valve member 62, which in this first embodiment is a ball, permanently biased by a valve spring 64 against the seating face 59.
  • the valve spring 64 has a relatively low stiffiiess and is just adapted to maintain the ball 62 in biasing contact against the seating face 58.
  • the plunger initiates a move from BDC toward TDC, the pressure in the compression chamber rises and the check valve 50 opens letting fuel to enter the inner chamber 46, the pressure rising in said chamber 46.
  • the pressure in the compression chamber and inside the inner chamber 46 are substantially equal.
  • the pressure in the compression chamber varies upon the demand of the engine while the pressure in the inner chamber 46 remains at said very high level.
  • the fluid communication FC only opens when the pressure in the compression chamber gets higher than the pressure in the inner chamber 46 and consequently, said pressure in the inner chamber 46 permanently remains very high.
  • the stiffness of the spring 64 is chosen to be low in order to enable the fluid communication FC to open upon superior pressure in the compression chamber 22.
  • peripheral wall 52 radially expands and reduces the functional gap between the main non-enlarged portion of the bore, and the plunger and, in doing this the fuel leakages around the plunger are reduced.
  • a second embodiment of the invention is now described in reference to figure 3 and by ways of differences to the first embodiment.
  • the main difference is that in the first embodiment the peripheral wall of the inner chamber is integral to the plunger while, in the second embodiment said wall is integral to an elongated head member 66 screwed at the end of the plunger.
  • the plunger 26 is shorter than previously and its very end portion has a reduced diameter which is threaded 54 for complementary arrangement of the elongated up-side-down cup-like head member 66 forming the complete head end 34 of the plunger and defining the inner chamber 46.
  • Said elongated head member 66 has a peripheral tubular wall 68 externally adjusted to be in sliding fit against the main non-enlarged part of the bore.
  • the inner chamber 46 is defined inside said peripheral wall 68 which extends, from a bottom end internally threaded for complementary arrangement on the top of the plunger, to an opposite transverse wall forming the transverse top face 36 and centrally pierced with the top orifice 48 which inner opening is surrounded by the seating face 59.
  • the final positioning of the elongated head member 66 on the plunger is secured via a weld seam 60 or via any other known fixing means.
  • check-valve 50 which is identical to the check valve of the first embodiment, is arranged inside the inner chamber 46 before screwing the head member 66 in place.
  • a third embodiment is now described in reference to figures 4 and 5 where the inner chamber is integrally formed in the head 34 of the plunger and, another check valve 70 is arranged in place by insertion through the top orifice 48.
  • the inner chamber 48 can be provided either fully integral to the plunger as represented on figure 4 , or can alternatively be in the form of either one of the previous embodiments, with a plugging cap or an elongated cap.
  • said another check-valve 70 is designed to be inserted through the top orifice 48.
  • the valve member 72 of said another check valve comprises a cylindrical portion that is adjusted in a sliding fit with the orifice 48.
  • side arms 74 one, two or more, that upwardly and radially extend from a first end attached to said cylindrical portion to a distant second end.
  • the side arms can be articulated at their first end or can be designed flexible.
  • the spring 64 of the check valve is attached to the valve member 72 and, as represented, a foot member 76 can be attached to the lower end of the spring.
  • the foot member 76 When arranged in place, the foot member 76 is engaged first, the spring follows and, when the valve member 72 is engaged the first end of the arms 74 engage first in the top orifice 48 and the arms 74 retracts and align in order to enable full engagement of the valve member 72.
  • the arms 74 radially expand and prevent any exit of the check valve. The spring forces the valve member 72 toward the outside while the arms 74 forbid such move.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
EP17167344.5A 2016-04-27 2017-04-20 Pompe à carburant haute pression Active EP3239514B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB1607311.6A GB2549745A (en) 2016-04-27 2016-04-27 High pressure fuel pump

Publications (2)

Publication Number Publication Date
EP3239514A1 true EP3239514A1 (fr) 2017-11-01
EP3239514B1 EP3239514B1 (fr) 2020-11-04

Family

ID=58579089

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17167344.5A Active EP3239514B1 (fr) 2016-04-27 2017-04-20 Pompe à carburant haute pression

Country Status (2)

Country Link
EP (1) EP3239514B1 (fr)
GB (1) GB2549745A (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2577081A (en) * 2018-09-12 2020-03-18 Delphi Tech Ip Ltd Fuel pump and plunger therefor

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080224417A1 (en) * 2007-03-16 2008-09-18 Cummins, Inc. Low leakage plunger assembly for a high pressure fluid system
DE102008040088A1 (de) * 2008-07-02 2010-01-07 Robert Bosch Gmbh Hochdruckpumpe
DE102008041176A1 (de) * 2008-08-12 2010-02-18 Robert Bosch Gmbh Hochdruckpumpe
KR20120045270A (ko) * 2010-10-29 2012-05-09 현대자동차주식회사 고압연료펌프
EP2492506A1 (fr) * 2011-02-28 2012-08-29 Delphi Technologies Holding S.à.r.l. Tête de pompage

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19854716B4 (de) * 1998-11-26 2006-06-22 Continental Teves Ag & Co. Ohg Kolbenpumpe
DE102007018235A1 (de) * 2007-04-18 2008-10-23 Robert Bosch Gmbh Pumpenvorrichtung zur Erzeugung hoher Drücke
GB201501282D0 (en) * 2015-01-27 2015-03-11 Delphi International Operations Luxembourg S.�.R.L. Plunger assembly

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080224417A1 (en) * 2007-03-16 2008-09-18 Cummins, Inc. Low leakage plunger assembly for a high pressure fluid system
DE102008040088A1 (de) * 2008-07-02 2010-01-07 Robert Bosch Gmbh Hochdruckpumpe
DE102008041176A1 (de) * 2008-08-12 2010-02-18 Robert Bosch Gmbh Hochdruckpumpe
KR20120045270A (ko) * 2010-10-29 2012-05-09 현대자동차주식회사 고압연료펌프
EP2492506A1 (fr) * 2011-02-28 2012-08-29 Delphi Technologies Holding S.à.r.l. Tête de pompage

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2577081A (en) * 2018-09-12 2020-03-18 Delphi Tech Ip Ltd Fuel pump and plunger therefor
GB2577081B (en) * 2018-09-12 2021-01-27 Delphi Tech Ip Ltd Fuel pump and plunger therefor

Also Published As

Publication number Publication date
EP3239514B1 (fr) 2020-11-04
GB2549745A (en) 2017-11-01

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