EP1344932A2 - Schmiermittelfördereinrichtung für Kraftstoffhochdruckpumpe - Google Patents

Schmiermittelfördereinrichtung für Kraftstoffhochdruckpumpe Download PDF

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Publication number
EP1344932A2
EP1344932A2 EP03005316A EP03005316A EP1344932A2 EP 1344932 A2 EP1344932 A2 EP 1344932A2 EP 03005316 A EP03005316 A EP 03005316A EP 03005316 A EP03005316 A EP 03005316A EP 1344932 A2 EP1344932 A2 EP 1344932A2
Authority
EP
European Patent Office
Prior art keywords
lifter
lubricant supply
supply hole
cam
guide
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
EP03005316A
Other languages
English (en)
French (fr)
Other versions
EP1344932A3 (de
EP1344932B1 (de
Inventor
Naoki Yamamoto
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.)
Renault SA
Nissan Motor Co Ltd
Original Assignee
Renault SA
Nissan Motor Co 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 Renault SA, Nissan Motor Co Ltd filed Critical Renault SA
Publication of EP1344932A2 publication Critical patent/EP1344932A2/de
Publication of EP1344932A3 publication Critical patent/EP1344932A3/de
Application granted granted Critical
Publication of EP1344932B1 publication Critical patent/EP1344932B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil

Definitions

  • the present invention relates to a high pressure fuel pump including a pump plunger driven by means of a rotating cam.
  • the present invention relates to a lubricant supply unit for lubricating a lifter which moves up and down (round trip) with an abutment on the cam.
  • a high pressure fuel pump of an internal combustion engine of high pressure injection type includes a pump plunger which is moved up and down, by means of a cam of a cam shaft, via a cylindrical bottomed lifter.
  • the above high pressure fuel pump is supposed to have a lubricant supply unit for lubricating the lifter sliding in a lifter guide.
  • the thus formed lubricant supply hole are opened and closed in accordance with up-and-down movement of the lifter acting as a valve of the lubricant supply hole.
  • the entire hydraulic pressure system having the thus fluctuating lubricant may cause seizure and wear to the sliding areas in a period of reduced amount of lubricant. Preventing the fluctuation in the lubricant (namely, potential seizure and wear) is, however, supposed to use a flow rate controller such as an orifice, resulting in increase in cost.
  • operating the high pressure fuel pump may cause a bearing pressure distribution to a side face of the lifter, which distribution can be determined relative to rotational direction of a cam.
  • Forming the lubricant supply hole in a position having the high bearing pressure means a reduction in a pressure-applicable area by an area covered by the lubricant supply hole, thus further increasing the bearing pressure in the position.
  • forming the lubricant supply hole in the position having the high bearing pressure may increase the bearing pressure relative to the supplied lubricant pressure, thus causing shortage of the lubricant to the side face of the lifter. As a result, the lifter and the lifter guide are likely to cause seizure and wear.
  • a lubricant supply unit of a fuel pump (1) comprising:
  • the lubricant supply hole (51) is disposed at such a height that the lifter (28) at a bottom dead center allows a first part of the lubricant supply hole (51) to open at an upper end of the lifter (28) and a second part of the lubricant supply hole (51) to be covered with an outer periphery of the lifter (28).
  • a lubricant supply unit of a fuel pump (1) comprising:
  • the lubricant supply hole (56) is disposed at such a height that the lifter (28) at a top dead center allows a first part of the lubricant supply hole (56) to open at a lower end of the lifter (28) and a second part of the lubricant supply hole (56) to be covered with an outer periphery of the lifter (28).
  • Fig. 1 shows an overall construction of a high pressure fuel pump 1 under the present invention.
  • Fig. 2 shows an entire fuel system of an internal combustion engine using high pressure fuel pump 1.
  • Fig. 3 shows a cross section of an essential part of high pressure fuel pump 1, according to a first embodiment of the present invention.
  • Fig. 4 shows a cross section taken along lines IV-IV in Fig. 3.
  • Fig. 5 shows a behavior of a lifter 28 as well as relation of a pump load F1, a reactive force F2 and a pressing load F3, when high pressure fuel pump 1 is under operation.
  • Fig. 6 shows a cross section showing a bearing pressure distribution between lifter 28 and a guide hole 41.
  • Fig. 7 shows a cross section (similar to the cross section in Fig. 4), according to a second embodiment of the present invention.
  • Fig. 8 shows a cross section of the essential part of high pressure fuel pump 1, according to a third embodiment of the present invention.
  • Fig. 1 shows an overall construction of a high pressure fuel pump 1 under the present invention.
  • Fig. 2 shows an entire fuel system of an internal combustion engine using high pressure fuel pump 1. Herein, fuel is directly injected into a cylinder of the internal combustion engine.
  • Fig. 2 shows a fuel tank 2, a low pressure feed pump 3, an electric motor 4, a fuel filter 5 and a low pressure regulator 6.
  • Low pressure feed pump 3 is disposed in fuel tank 2.
  • Electric motor 4 drives low pressure feed pump 3.
  • Low pressure regulator 6 regulates the fuel supplied from low pressure feed pump 3 at a predetermined pressure (0.3 MPa to 0.5 MPa). Subsequently, the thus regulated fuel is conveyed into high pressure fuel pump 1.
  • High pressure fuel pump 1 is mechanically driven by means of a cam shaft 20 interlocked with a crank shaft of the internal combustion engine (to be described afterward).
  • the pressure so pressurized (at its peak of 10 MPa to 20 MPa) by means of high pressure fuel pump 1 is then conveyed, by way of a high pressure fuel pass 8, to a fuel injection valve 9 of each cylinder of the internal combustion engine. Subsequently, the thus conveyed fuel is injected into each cylinder, in accordance with an injection signal from an engine control module 11.
  • the fuel pressure in high pressure fuel pass 8 is sensed with a fuel pressure sensor 10.
  • the thus sensed fuel pressure is a base for variably controlling fuel supply (amount) of high pressure fuel pump 1, to obtain a predetermined fuel pressure.
  • a relief pass 12 and a relief valve 13 extending toward fuel tank 2, while there is provided a return pass 14 for returning to fuel tank 2 low pressure fuel leaked from high pressure fuel pump 1.
  • cam shaft 20 also acts as a part of a dynamic valve system of the internal combustion engine.
  • cam shaft 20 has a part provided properly with a pair of cam lobes 21 for driving high pressure fuel pump 1.
  • high pressure fuel pump 1 is disposed above a cylinder head 22 so that high pressure fuel pump 1 can be disposed above cam shaft 20.
  • High pressure fuel pump 1 includes a lifter guide 23, a pump housing 25, a pump plunger 26 and an electromagnetic control valve 27.
  • Lifter guide 23 also acts as a member for mounting high pressure fuel pump 1.
  • Pump housing 25 is fixed to lifter guide 23 by way of a lubricant seal 24.
  • Pump plunger 26 is substantially cylindrical, and is disposed in substantially the center of pump housing 25 in such a manner as to move up and down.
  • the above described variable control of the fuel supply (amount) of high pressure fuel pump 1 is carried out by means of electromagnetic control valve 27.
  • Pump plunger 26 has a lower end 26a protruding down from pump housing 25, and cam shaft 20 presses lower end 26a by way of a lifter 28. Moreover, pump plunger 26 has an upper end 26b for pressurizing the fuel in a pressurizing chamber 29.
  • a seal member 31 seals an area defined between pump plunger 26 and pump housing 25.
  • Pump housing 25 has a low pressure fuel inlet 32 connecting to low fuel pressure fuel pass 7 (see Fig. 1), and a high pressure fuel outlet 33 connecting to high pressure fuel pass 8 (see Fig. 1).
  • Low pressure fuel pass 32 connects to pressurizing chamber 29 by way of a valve body 27a of electromagnetic control valve 27, while high pressure fuel outlet 33 connects to pressurizing chamber 29 by way of a check valve 34.
  • Electromagnetic control valve 27 controls timing of opening and closing valve body 27a, thereby variably controlling the fuel which is supplied from pressurizing chamber 29 to high pressure fuel outlet 33 in accordance with stokes of pump plunger 26.
  • Lifter 28 is shaped substantially into a bottomed cylinder having a cylindrical side wall portion 28a and a bottom wall portion 28b disposed beneath side wall portion 28a. Lifter 28 mates with a cylindrical guide hole 41 of lifter guide 23 in such a manner as to slide up and down and make a rotation. Lifter 28 is substantially concentric with pump plunger 26.
  • lower end 26a of pump plunger 26 abuts on an inner face (upper face in Fig. 1) of bottom wall portion 28b of lifter 28.
  • a return spring 42 disposed inside lifter 28 can continuously bias lifter 28 toward cam shaft 20, thereby allowing a bottom face (lower face in Fig. 1) of bottom wall portion 28b to abut on cam lobe 21.
  • cam lobe 21 in accordance with rotation of cam shaft 20 can move lifter 28 up and down. Integrally with lifter 28, pump plunger 26 can make movement up and down (round trip).
  • cam shaft 20 has its center line substantially orthogonal to a center line of lifter 28 such that cam lobe 21 with its maximum lift can press substantially the center of lifter 28.
  • a lubricant of the internal combustion engine lubricates an area defined between lifter 28 and lifter guide 23.
  • the lubricant is supplied through a lubricant pass 43 formed in cylinder head 22 and lifter guide 23.
  • Fig. 3 and Fig. 4 show details of lifter 28 and a lubrication mechanism of lifter 28, according to a first embodiment of the present invention.
  • Fig. 5 shows a behavior of lifter 28, while Fig. 6 shows bearing pressure (face pressure) caused by the behavior of lifter 28.
  • Pressurizing the fuel with pump plunger 26 causes a pump load F1 to act along the center line of pump plunger 26, as is seen in Fig. 5, and thereby pump load F1 causes a reactive force F2 to initial abutment point C.
  • Pump load F1 and reactive force F2 offset from each other may turn lifter 28 counterclockwise, as is seen in Fig. 5.
  • first portion A abuts on an upper portion of lifter 28, while second portion B abuts on a lower portion of lifter 28.
  • first portion A may have greater bearing pressure than second portion B. In other words, first portion A may have the greatest circumferential bearing pressure.
  • Fig. 6 shows a circumferential bearing pressure distribution of lifter 28.
  • the scale of the bearing pressure can be depicted by radial expansion.
  • the bearing pressure can be seen in only two portions, namely, the first portion A and second portion B which are disposed along a rotational plane of cam lobe 21, leaving substantially no (zero) bearing pressure in other area (including in a direction orthogonal to the rotational plane of cam lobe 21).
  • Fig. 6 also shows a maximum bearing pressure portion A'.
  • Lifter 28 and the lubrication mechanism of lifter 28 in Fig. 3 and Fig. 4 according to the first embodiment of the present invention mainly take into account the lubrication at first portion A in Fig. 5 and Fig. 6.
  • a pair of upper lubricant supply holes 51 are formed substantially symmetrical in such a manner as to open on respective sides of first portion A which is a high bearing pressure area.
  • a first radial line R1 of guide hole 41 (otherwise, of lifter guide 23) is disposed between the pair of upper lubricant supply holes 51.
  • Upper lubricant supply hole 51 is an outlet of lubricant pass 43.
  • first portion A has a third portion D having the bearing pressure of substantially 0 and included in an end opening of upper lubricant supply hole 51 shaped substantially into a circle. Moreover, upper lubricant supply hole 51 extends in a direction along a second radial line R2 of guide hole 41 (otherwise, of lifter guide 23).
  • the pair of upper lubricant supply holes 51 are the same in level in an axial direction of guide hole 41. Especially, as is seen in Fig. 3, lifter 28 at a bottom dead center causes the end opening of upper lubricant supply hole 51 to be disposed in such a height as to be partly open.
  • side wall portion 28a of lifter 28 has an upper end formed with a chamfer 52 shaped substantially into a taper.
  • Lifter 28 at the bottom dead center allows a boundary line 53 (defined between a vertical face of side wall portion 28a and chamfer 52) to intersect with the end opening of upper lubricant supply hole 51.
  • boundary line 53 is in such a position as to pass through (for example) substantially a center of the end opening of upper lubricant supply hole 51, with lifter 28 at the bottom dead center.
  • bottom wall portion 28b of lifter 28 is formed with a plurality of through communication holes 54.
  • a lubricant pressurized by means of a lubricant pump (not shown) of the internal combustion engine may be continuously discharged from upper lubricant supply hole 51, and thereby supplied to a clearance 55 defined between lifter 28 and guide hole 41's wall.
  • the pair of upper lubricant supply holes 51 supply the lubricant to the respective sides of first portion A (high bearing pressure area), thereby securely lubricating an area in the vicinity of first portion A.
  • upper lubricant supply holes 51 not opening to first portion A (high bearing pressure area) can prevent further increase in bearing pressure of first portion A (high bearing pressure area).
  • Lifter 28 at the bottom dead center may partly open an upper part of upper lubricant supply hole 51, as is seen in Fig. 3. With this, a first portion of the lubricant may flow into clearance 55, as indicated with a single downward arrow in Fig. 3. On the other hand, as indicated with three sequential arrows in Fig. 3, a second portion of the lubricant may pass, by way of chamfer 52, over side wall portion 28a of lifter 28 to flow into lifter 28, thus lubricating a contact defined between lower end 26a of pump plunger 26 and bottom wall portion 28b of lifter 28. Also lubricated with the second portion of the lubricant includes return spring 42.
  • the second portion of the lubricant in lifter 28 may drop down by way of communication hole 54, thus lubricating a contact defined between cam shaft 20 and lifter 28.
  • lifter 28 and the lubrication mechanism of lifter 28 according to the first embodiment can control fluctuation in lubricant pressure in the entire lubrication system and secure lubrication of members including those disposed inside lifter 28.
  • upper lubricant supply hole 51 can be opened and closed by way of chamfer 52, thus eliminating the need for excessive reduction in axial length of side wall portion 28a. This can allow lifter 28 to open and close upper lubricant supply hole 51 with stabilized movement (round trip) of lifter 28.
  • Fig. 7 shows details of lifter 28 with the pair of the upper lubricant supply holes 51 directing otherwise than those in Fig. 4, according to a second embodiment of the present invention.
  • the pair of upper lubricant supply holes 51 are inclined inward with each other.
  • each of the pair of upper lubricant supply holes 51 is inclined inward relative to second radial line R2 of guide hole 41 (otherwise, of lifter guide 23) in such a manner as to direct toward first portion A which is the high bearing pressure area.
  • second radial line R2 passes through substantially the center of the end opening of upper lubricant supply hole 51.
  • upper lubricant supply hole 51 in Fig. 7 according to the second embodiment is opened in the position including third portion D having the bearing pressure of substantially 0.
  • the thus inclined upper lubricant supply hole 51 in Fig. 7 can guide, toward first portion A (high bearing pressure area), the lubricant supplied to clearance 55 (see Fig. 3), thus further improving lubrication of first portion A.
  • Fig. 8 shows details of lifter 28, according to a third embodiment of the present invention.
  • a pair of lower lubricant supply holes 56 are disposed on respective sides of second portion B in a form of a symmetry.
  • First radial line R1 of guide hole 41 (otherwise, of lifter guide 23) is disposed between the pair of lower lubricant supply holes 56.
  • Second portion B has a portion (corresponding to its counterpart, namely, third portion D in Fig. 4 and Fig. 7) having bearing pressure of substantially 0 and included in an end opening of lower lubricant supply hole 56.
  • Lifter 28 at a top dead center in the axial direction of guide hole 41 allows an end opening of lower lubricant supply hole 56 to partly open due to a lower end of lifter 28.
  • lifter 28 and the lubrication mechanism of lifter 28 allow the pair of lower lubricant supply holes 56 to securely lubricate second portion B (high bearing pressure area second to first portion A), thus securely preventing local wear or seizure.
  • Lifter 28 at the top dead center can partly open lower lubricant supply hole 56, thus blowing the lubricant to cam lobe 21 and thereby further lubricating the area between cam lobe 21 and lifter 28.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
EP20030005316 2002-03-11 2003-03-11 Schmiermittelfördereinrichtung für Kraftstoffhochdruckpumpe Expired - Lifetime EP1344932B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2002064669A JP3788373B2 (ja) 2002-03-11 2002-03-11 高圧燃料ポンプの給油装置
JP2002064669 2002-03-11

Publications (3)

Publication Number Publication Date
EP1344932A2 true EP1344932A2 (de) 2003-09-17
EP1344932A3 EP1344932A3 (de) 2004-10-27
EP1344932B1 EP1344932B1 (de) 2005-12-14

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Application Number Title Priority Date Filing Date
EP20030005316 Expired - Lifetime EP1344932B1 (de) 2002-03-11 2003-03-11 Schmiermittelfördereinrichtung für Kraftstoffhochdruckpumpe

Country Status (3)

Country Link
EP (1) EP1344932B1 (de)
JP (1) JP3788373B2 (de)
DE (1) DE60302688T2 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1457667A1 (de) * 2003-03-11 2004-09-15 Denso Corporation Kraftstoffpumpe, die vom Kraftstoff geschmiert wird
WO2013092614A1 (de) * 2011-12-21 2013-06-27 Robert Bosch Gmbh Pumpe, insbesondere kraftstoffhochdruckpumpe für eine kraftstoffeinspritzeinrichtung
WO2018178502A1 (en) * 2017-03-29 2018-10-04 Wärtsilä Finland Oy A fuel pump for supplying fuel to an internal combustion piston engine
CN110691903A (zh) * 2017-03-29 2020-01-14 瓦锡兰芬兰有限公司 用于向内燃活塞发动机供应燃料的燃料泵
CN111594366A (zh) * 2019-02-20 2020-08-28 株式会社电装 燃料喷射泵

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4915249B2 (ja) * 2007-02-23 2012-04-11 トヨタ自動車株式会社 燃料噴出ポンプ
JP4930425B2 (ja) * 2008-03-25 2012-05-16 日産自動車株式会社 内燃機関
JP5642925B2 (ja) 2008-08-20 2014-12-17 日産自動車株式会社 高圧燃料ポンプ
EP2530315A1 (de) 2011-06-02 2012-12-05 Delphi Technologies Holding S.à.r.l. Kraftstoffpumpenschmierung
JP6091787B2 (ja) * 2012-07-20 2017-03-08 ヤンマー株式会社 燃料噴射ポンプ
JP6155962B2 (ja) * 2013-08-21 2017-07-05 スズキ株式会社 高圧燃料ポンプ
JP6818644B2 (ja) * 2017-06-30 2021-01-20 株式会社クボタ エンジン用回転軸
JP7049596B2 (ja) 2018-01-31 2022-04-07 いすゞ自動車株式会社 潤滑油供給構造

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58136669U (ja) * 1982-03-09 1983-09-14 株式会社ボッシュオートモーティブ　システム 燃料噴射ポンプの潤滑油供給装置
JPH0849632A (ja) * 1994-08-05 1996-02-20 Nissan Diesel Motor Co Ltd 燃料噴射ポンプの給油装置

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1457667A1 (de) * 2003-03-11 2004-09-15 Denso Corporation Kraftstoffpumpe, die vom Kraftstoff geschmiert wird
US7314351B2 (en) 2003-03-11 2008-01-01 Denso Corporation Fuel supply pump capable of lubricating cam bearings
WO2013092614A1 (de) * 2011-12-21 2013-06-27 Robert Bosch Gmbh Pumpe, insbesondere kraftstoffhochdruckpumpe für eine kraftstoffeinspritzeinrichtung
CN104011368A (zh) * 2011-12-21 2014-08-27 罗伯特·博世有限公司 泵、尤其用于燃料喷射装置的高压燃料泵
CN104011368B (zh) * 2011-12-21 2017-04-05 罗伯特·博世有限公司 用于燃料喷射装置的泵
WO2018178502A1 (en) * 2017-03-29 2018-10-04 Wärtsilä Finland Oy A fuel pump for supplying fuel to an internal combustion piston engine
CN110691903A (zh) * 2017-03-29 2020-01-14 瓦锡兰芬兰有限公司 用于向内燃活塞发动机供应燃料的燃料泵
CN110709598A (zh) * 2017-03-29 2020-01-17 瓦锡兰芬兰有限公司 用于向内燃活塞发动机供应燃料的燃料泵
CN110691903B (zh) * 2017-03-29 2021-04-16 瓦锡兰芬兰有限公司 用于向内燃活塞发动机供应燃料的燃料泵
CN111594366A (zh) * 2019-02-20 2020-08-28 株式会社电装 燃料喷射泵

Also Published As

Publication number Publication date
EP1344932A3 (de) 2004-10-27
DE60302688T2 (de) 2006-07-13
EP1344932B1 (de) 2005-12-14
JP3788373B2 (ja) 2006-06-21
JP2003269296A (ja) 2003-09-25
DE60302688D1 (de) 2006-01-19

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