EP3176422A2 - Pompe à carburant - Google Patents

Pompe à carburant Download PDF

Info

Publication number
EP3176422A2
EP3176422A2 EP16201691.9A EP16201691A EP3176422A2 EP 3176422 A2 EP3176422 A2 EP 3176422A2 EP 16201691 A EP16201691 A EP 16201691A EP 3176422 A2 EP3176422 A2 EP 3176422A2
Authority
EP
European Patent Office
Prior art keywords
piston
fuel pump
bore
end cap
follower assembly
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
EP16201691.9A
Other languages
German (de)
English (en)
Other versions
EP3176422B1 (fr
EP3176422A3 (fr
Inventor
Levent AKIN
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 EP3176422A2 publication Critical patent/EP3176422A2/fr
Publication of EP3176422A3 publication Critical patent/EP3176422A3/fr
Application granted granted Critical
Publication of EP3176422B1 publication Critical patent/EP3176422B1/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
    • 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
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/03—Fuel-injection apparatus having means for reducing or avoiding stress, e.g. the stress caused by mechanical force, by fluid pressure or by temperature variations
    • 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
    • F02M2200/26—Fuel-injection apparatus with elastically deformable elements other than coil springs

Definitions

  • the present disclosure relates generally to a fuel pump having a piston reciprocating in a bore under the influence of a cam follower.
  • the invention particularly focuses on the interface between the piston and the cam follower assembly.
  • Fuel injection equipment comprise high pressure pump aiming at pressurizing fuel at several thousands of bars prior to flow said fuel to injectors that spray the fuel in combustion chambers of an internal combustion engine.
  • Well known pumps comprise a pump head member provided with an inlet and an outlet both opening in a compression chamber that is near the blind end of a bore in which a piston slidably reciprocates along the pumping axis of the bore.
  • the piston performs a pumping cycle between a Top Dead Centre (TDC) position around which fuel in the compression chamber is compressed and released toward the injectors and, a Bottom Dead Centre (BDC) position around which fuel is aspired in the chamber.
  • TDC Top Dead Centre
  • BDC Bottom Dead Centre
  • the piston reciprocates under the influence of a cam rotating about a cam axis perpendicular to the pumping axis.
  • the cam is followed by a follower assembly combined to an external extremity of the piston, said follower assembly typically having a cup-like body member in which a roller is free to rotate about a rolling axis perpendicular to the piston axis and parallel to the cam axis.
  • a spring is compressed between the pump head member and the follower assembly in order to permanently bias the follower assembly against the cam.
  • the spring pulls the piston down as it travels from the Top Dead Centre (TDC) position to the Bottom Dead Centre (BDC) position.
  • TDC Top Dead Centre
  • BDC Bottom Dead Centre
  • This function is important for filling efficiency of the pump and transfer of the spring load to the follower assembly in order to maintain contact with the cam.
  • a spring seat member is provided for receiving the spring.
  • One approach is to mount the spring seat member to an outer diameter of the piston by pressing.
  • the spring seat member may be fixedly mounted to the piston such that relative movement is inhibited.
  • a mounting collar may be fixedly mounted to an outer diameter of the piston to support the spring seat member, for example by press fitting.
  • the spring seat member may be movable relative to the piston, but is operatively biased against the collar by the action of the spring.
  • a further alternative is to form a keyed interface for mounting the spring seat member to the piston.
  • the keyed interface may not require a press fit arrangement, but machining is required to form the keyed interface on the piston and/or the spring seat member.
  • Increased pumping loads place additional demands on the fuel pump. For example, higher pumping loads may lead to high contact stresses between the plunger and the cam follower assembly.
  • the contact area between the piston and the cam follower assembly is determined by the outer diameter of the piston in known arrangements.
  • the piston In order to deliver higher pumping pressures, the piston must be capable of sustaining higher operating loads to avoid contact stress problems.
  • increased engine speeds places higher loads on the spring to inhibit separation between the cam and the cam follower assembly. To reduce the loads on the spring, the inventor(s) has recognised that it would be desirable to reduce the mass of moving components in the fuel pump.
  • aspects of the present invention relate to a fuel pump of an injection system.
  • a fuel pump having a head member provided with a blind bore in which a piston is adapted to perform a pumping cycle by reciprocating along the main axis of the bore between a top dead center position and a bottom dead center position, fuel being pressurized during the cycle in a compression chamber defined between the top extremity of the piston and the blind end of the bore, the piston reciprocating under the influence of a rotating cam cooperating with a follower assembly, the pump further comprising a spring compressed between the head member and the follower assembly in order to bias the follower assembly toward the cam, characterized in that an end cap is mounted to the piston for engaging the follower assembly.
  • the end cap defines a contact surface for engaging the follower assembly.
  • the end cap may be configured to reduce the contact stresses applied to the piston.
  • the contact surface may provide a larger contact area which is suitable for reducing contact stresses and may withstand higher pumping loads.
  • blind bore is used herein to refer to a bore which is closed at one end to form the compression chamber.
  • the bore may be an open bore having an inlet valve, such as an inlet poppet valve.
  • the inlet valve may selectively close the bore to form the compression chamber.
  • the end cap may be configured to locate a spring seat member on the piston.
  • the spring seat member may be biased against the end cap by said spring.
  • the end cap may comprise a head.
  • the head may be formed integrally with said end cap.
  • the head may have a diameter which is substantially equal to or less than the diameter of the piston.
  • the head may have a diameter which is larger than the piston.
  • the head may be suitable for cooperating with said spring seat member.
  • the head may define a shoulder for locating the spring seat member.
  • the spring may bias the spring seat member against the end cap.
  • the head may form a spring seat member.
  • the spring seat member may be formed integrally with the end cap.
  • the head may comprise a contact surface for engaging the follower assembly.
  • the contact surface may be a convex contact surface.
  • the contact surface may be part-spherical or part-spheroidal. Alternatively, the contact surface may be substantially planar.
  • the head may comprise a circumferential flange which forms a radially outer portion of the contact surface.
  • the circumferential flange may be deformable elastically under load.
  • One or more aperture may be formed in an outer sidewall of the head to form said circumferential flange.
  • Each aperture may be in the form of a groove or channel. More particularly, a circumferential groove may be formed in an outer sidewall of the head to form said circumferential flange.
  • the piston may comprise a longitudinal bore.
  • the longitudinal bore may extend along a central axis of the piston.
  • the longitudinal bore may reduce the mass of the piston.
  • the end cap may close the longitudinal bore.
  • the end cap may seal the longitudinal bore.
  • the end cap may have a projection disposed in said longitudinal bore to mount the end cap.
  • the projection may be a press fit in said longitudinal bore.
  • the end cap may form a plug which closes the longitudinal bore.
  • the end cap may comprise a bore for receiving a projection formed on the piston.
  • Other types of connectors are also contemplated for mounting the end cap.
  • the end cap may be formed from the same material as the piston or a different material.
  • a fuel pump having a head member provided with a blind bore in which a piston is adapted to perform a pumping cycle by reciprocating along the main axis of the bore between a top dead center position and a bottom dead center position, fuel being pressurized during the cycle in a compression chamber defined between the top extremity of the piston and the blind end of the bore, the piston reciprocating under the influence of a rotating cam cooperating with a follower assembly, the pump further comprising a spring compressed between the head member and the follower assembly in order to bias the follower assembly toward the cam, the piston having a contact surface for engaging the follower assembly;
  • the circumferential flange may be formed by a separate component mounted to an end of the piston.
  • the circumferential flange may be formed integrally with the piston.
  • the piston may be machined to form the circumferential flange.
  • One or more aperture may be formed in an outer sidewall of the piston to form said circumferential flange.
  • Each aperture may be in the form of a groove or channel.
  • one or more circumferential groove may be formed in an outer sidewall of the piston to form said circumferential flange.
  • the one or more circumferential groove may be offset from the contact surface along a longitudinal axis of the piston.
  • the contact surface may be substantially planar.
  • the circumferential groove can be used as an alternative to machining a convex profile on the contact surface of the piston.
  • the contact surface may be substantially planar.
  • the circumferential flange may have an outer diameter which is substantially the same as, less than or greater than the outer diameter of the piston.
  • the unit pump 10 comprises a head member 12 provided with a blind bore 14 axially extending along a main axis X1 and opening centrally in an under face 16 of a turret projection 18 that downwardly protrudes from the underside 20 of the head member 12.
  • An inlet poppet valve 22, arranged at the top of the bore 14 controls a fuel inlet orifice 24 opening into the bore 14.
  • the bore 14 is identified as a "blind" bore even if it is open on its very top where is arranged the fuel inlet orifice 24 controlled by the inlet poppet valve 22. Indeed, in operation the inlet poppet valve 22 sealingly closes the fuel inlet orifice 24, the bore 14 actually being blind.
  • said inlet valve may be radially arranged relative to the bore while an outlet check valve is arranged on the very top of the bore. A truly permanently blind bore can also be considered.
  • a shaft-like piston 26 slidably arranged in the bore 14 is inside the head member 12, where its top extremity 28 defines with the blind end of the bore a compression chamber 30 and also, partially extending outside the bore 14, downwardly protruding from the turret projection 18 toward a lower end 32.
  • a follower assembly 34 is combined to the lower end 32, the follower assembly 34 cooperating with a rotating cam 36 which rotates about a cam axis X2 to actuate the piston 26 in reciprocal axial displacements inside the bore 14.
  • the follower assembly 34 comprises a cup-like body 38 provided with aligned bearing means 40 for a roller 42 to freely rotate about a roller axis X3 perpendicular to the main axis X1 and parallel to the cam axis X2.
  • a spring seat member 44 Inside the cup-like body 38 is arranged a spring seat member 44 for receiving a coil spring 46 axially arranged around the piston 26 and compressed between said spring seat member 44 and the underside 20 of the head member 12.
  • the final upper spirals of the spring 46 are engaged around the turret 18 for the compression spring to be guided and to generate an upward force on the pump head member 12 and an opposite downward force on the follower assembly 34.
  • the piston 26 reciprocally translates between a top dead center (TDC) position, represented in figure 1 , and, after a 90° rotation of the cam a bottom dead center (BDC) position (not shown), the stroke of the piston 26 depending on the profile of the cam 36.
  • the angle of rotation here 90°, depends on the cam profile which here has two lobes.
  • Alternative cam design having just one lobe, or three, or four or more lobes enable to reach BDC after an angle rotation of 180° or 60° or 45°.
  • An end cap 48 is disposed on the low pressure side of the piston 26.
  • the end cap 48 is fixedly mounted to the piston 26 and arranged to engage the follower assembly 34.
  • the end cap 48 comprises a projection 50 and a head 52.
  • the piston 26 has a longitudinal bore 54 for receiving the projection 50 to mount the end cap 48.
  • the longitudinal bore 54 is a blind bore extending partway along the length of the piston 26.
  • the projection 50 has a cylindrical profile and is a press fit in the longitudinal bore 54.
  • the end cap 48 plugs the longitudinal bore 54.
  • the head 52 of the end cap 48 has a diameter which is larger than that of the piston 26.
  • the head 52 projects radially outwardly from the piston 26 and forms an annular shoulder 56 for locating the spring seat member 44.
  • the spring 46 biases the spring seat member 44 against the annular shoulder 56.
  • the head 52 has a contact surface 58 for engaging the follower assembly 34.
  • the contact surface 58 has a convex profile. In the present embodiment, the contact surface 58 is part-spherical or part-spheroidal. This can help to avoid edge contact which would otherwise cause a high stress concentration under load. By avoiding edge contact, stress concentration in the middle of the contact surface 58 may increase but stresses at the edges of the head 52 may be decreased.
  • a circumferential groove 60 is formed in an outer sidewall 62 of the head 52 proximal to the contact surface 58.
  • the circumferential groove 60 is offset from the contact surface 58 along the main axis X1 such that a circumferential flange 64 is formed at a lower end of the head 52.
  • the circumferential flange 64 forms a radially outer portion of the contact surface 58 and is adapted to undergo elastic deformation under load.
  • the elastic deformation of the circumferential flange 64 may help to avoid edge contact and/or to reduce contact stress at the edges of the end cap 48.
  • the contact surface 58 in this arrangement may be substantially planar. In use, the circumferential flange 64 deforms under load, thereby reducing operating stresses.
  • the circumferential flange 64 can be used as an alternative to machining the contact surface 58 to form the aforementioned convex profile.
  • the end cap 48 is disposed between the piston 26 and the follower assembly 34.
  • the spring 46 biases the spring seat member 44 against the end cap 48.
  • the annular shoulder 56 formed by the head 52 retains the spring seat member 44.
  • the contact surface 58 engages the follower assembly 34 and causes the piston 26 to reciprocally translate between the top dead center (TDC) position and the bottom dead center (BDC) position as the cam 36 rotates.
  • the contact surface 58 provides a larger contact area suitable for reducing contact stresses and at least in certain embodiments may withstand higher pumping loads.
  • the longitudinal bore 54 reduces the mass of the piston 26.
  • FIG. 3 A second embodiment of the high pressure fuel pump 10 is shown in Figures 3 and 4 .
  • the second embodiment is similar to the first embodiment and the description herein focuses on the differences.
  • Like references are used for like components.
  • the fuel pump 10 according to the second embodiment is modified such that the spring seat member 44 is formed integrally with the end cap 48.
  • the end cap 48 comprises a support flange 66 for engaging the lower end of the spring 46.
  • the support flange 66 has an annular profile and extends radially outwardly from an upper end of the head 52.
  • the contact surface 58 of the end cap 48 comprises a part-spherical surface for engaging the follower assembly 34.
  • the circumferential groove 60 is formed in the outer sidewall 62 of the head 52 proximal to the contact surface 58.
  • the mounting arrangement of the end cap 48 in the piston 26 is unchanged from the first embodiment.
  • a third embodiment of the high pressure fuel pump 10 is shown in Figures 5 and 6 .
  • the third embodiment is a modification of the second embodiment and the description herein focuses on the differences.
  • Like references are used for like components.
  • the piston 26 has an outer sidewall 68 and a longitudinal axis arranged coaxially with the main axis X1.
  • a contact surface 70 for engaging the follower assembly 34 is defined at a lower extremity 72 of the piston 26.
  • the end cap 48 is omitted from the high pressure fuel pump 10 in the third embodiment. Instead, the contact surface 70 of the piston 26 engages the follower assembly 34.
  • An aperture in the form of a circumferential groove 74 is formed in the sidewall 68 of the piston 26.
  • the circumferential groove 74 is offset from the contact surface 70 such that a circumferential flange 76 is formed at the lower extremity 72 of the piston 26.
  • the circumferential flange 76 is adapted to undergo elastic deformation under load.
  • the circumferential flange 76 defines a radially outer portion of the contact surface 70.
  • the radially outer portion of the contact surface 70 can undergo elastic deformation. At least in certain embodiments, this elastic deformation of the circumferential flange 76 may help to avoid edge contact and/or to reduce contact stress at the edges of the piston 26.
  • the contact surface 70 of the piston 26 is substantially planar.
  • the circumferential groove 74 can be used as an alternative to machining a convex profile on the contact surface 70 of the piston 26.
  • the spring seat member 44 is mounted to the sidewall 68 of the piston 26 above the circumferential groove 74.
  • the spring seat member 44 in the present embodiment is a press fit on the piston 26. It will be appreciated that other mounting or fastening arrangements may be used to locate the spring seat member 44.
  • the first and second embodiments comprise an end cap 48 having a projection 50 which is a press fit in the longitudinal bore 54 in the piston 26.
  • the end cap 48 could comprise a longitudinal bore for receiving a projection formed at the end of the piston 26. It will be appreciated that other types of cooperating male and female connectors may be employed to mount the end cap 48.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP16201691.9A 2015-12-01 2016-12-01 Pompe à carburant Active EP3176422B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GBGB1521130.3A GB201521130D0 (en) 2015-12-01 2015-12-01 Fuel pump

Publications (3)

Publication Number Publication Date
EP3176422A2 true EP3176422A2 (fr) 2017-06-07
EP3176422A3 EP3176422A3 (fr) 2017-06-21
EP3176422B1 EP3176422B1 (fr) 2020-03-11

Family

ID=55177473

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16201691.9A Active EP3176422B1 (fr) 2015-12-01 2016-12-01 Pompe à carburant

Country Status (2)

Country Link
EP (1) EP3176422B1 (fr)
GB (1) GB201521130D0 (fr)

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10147981A1 (de) * 2001-09-28 2003-04-24 Siemens Ag Verbindungselement zur Verbindung eines Kolbens mit einem Rückstellelement
GB201012634D0 (en) * 2010-07-28 2010-09-15 Delphi Technologies Holding Intermediate drive assembly
DE102012202205A1 (de) * 2012-02-14 2013-08-14 Robert Bosch Gmbh Kraftstoffhochdruckpumpe
DE102012203230A1 (de) * 2012-03-01 2013-09-05 Robert Bosch Gmbh Pumpenelement für eine Kraftstoffhochdruckpumpe

Also Published As

Publication number Publication date
EP3176422B1 (fr) 2020-03-11
GB201521130D0 (en) 2016-01-13
EP3176422A3 (fr) 2017-06-21

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