EP2088309A1 - Pompe d'alimentation en combustible haute pression - Google Patents

Pompe d'alimentation en combustible haute pression Download PDF

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Publication number
EP2088309A1
EP2088309A1 EP07792693A EP07792693A EP2088309A1 EP 2088309 A1 EP2088309 A1 EP 2088309A1 EP 07792693 A EP07792693 A EP 07792693A EP 07792693 A EP07792693 A EP 07792693A EP 2088309 A1 EP2088309 A1 EP 2088309A1
Authority
EP
European Patent Office
Prior art keywords
fuel
leak
pressure
portions
pressure pump
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.)
Withdrawn
Application number
EP07792693A
Other languages
German (de)
English (en)
Other versions
EP2088309A4 (fr
Inventor
Osamu Takahashi
Shingo Nakata
Takeshi Terada
Takao Miyawaki
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.)
Bosch Corp
Original Assignee
Bosch Corp
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 Bosch Corp filed Critical Bosch Corp
Publication of EP2088309A1 publication Critical patent/EP2088309A1/fr
Publication of EP2088309A4 publication Critical patent/EP2088309A4/fr
Withdrawn legal-status Critical Current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
    • 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
    • F02M59/04—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • 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
    • F02M59/442—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

Definitions

  • the present invention relates to a high-pressure fuel supply pump.
  • a high-pressure fuel supply pump that has conventionally come to be used for the purpose of supplying high-pressure fuel to a common rail system, for example, has a configuration where, as shown in FIG. 6 , a plunger 102 housed so as to be capable of reciprocal motion inside a barrel 101 reciprocally moves in accordance with the rotation of a cam shaft 103 to pressurize fuel supplied to the inside of the barrel 101 via an inlet/outlet valve 104 and where the thus obtained high-pressure fuel is sent to the outside by the inlet/outlet valve 104.
  • JP-A-8-68370 there is disclosed a configuration of a high-pressure fuel supply pump that includes two return passages, with one of the two return passages being connected to a fuel tank.
  • the conventional high-pressure fuel pump shown in FIG. 6 is configured such that leak fuel, which is some of the high-pressure fuel pressurized inside the barrel 101 used for fuel lubrication of the barrel 101, is supplied back to the barrel 101 through a passage 105, so particularly in an operating state where the discharge fuel amount becomes small, the temperatures of the barrel 101 and the plunger 102 rise because of the above-described circulation of that fuel, and this has been a large factor causing fuel injection efficiency to be lowered.
  • the configuration disclosed in JP-A-8-68370 has the problem that, in the case of a configuration that includes plural high-pressure pump portions, the configuration of the return passages for handling the leak fuel becomes complicated and causes costs to rise.
  • a high-pressure fuel supply pump that includes plural high-pressure pump portions configured to pressurize, with plungers, fuel that has been sucked into the insides of barrels and to discharge high-pressure fuel, and with fuel lubrication between the plungers and the barrels being performed by at least some of the high-pressure fuel in each of the plural high-pressure pump portions, wherein each of the high-pressure pump portions includes a leak fuel takeout portion for taking out leak fuel generated for the fuel lubrication from the insides of the barrels to the outside, and the leak fuel that has been taken out from each of the leak fuel takeout portions is guided to a fuel low-pressure side by a leak separate feed path.
  • the leak fuel which is some of the fuel used for the fuel lubrication between the plungers and the barrels, is not circulated and supplied to the barrels, a rise in the temperature of the plungers is controlled, and fuel injection efficiency can be improved with a simple configuration.
  • FIG. 1 is a diagram generally showing the exterior of an embodiment of a high-pressure fuel supply pump to which the present invention has been applied.
  • a high-pressure fuel supply pump 1 is used as a supply pump of a common rail system (not shown) that is used as a fuel injection system for a diesel engine, and in a body 2, there are disposed four high-pressure pump portions comprising a first high-pressure pump portion 1A to a fourth high-pressure pump portion 1D that are driven with a predetermined phase difference by a cam shaft (see FIG. 2 ) that is driven by rotational driving force from the unillustrated diesel engine.
  • FIG. 2 is a pump cross-sectional diagram for describing the first high-pressure pump portion 1A.
  • the first high-pressure pump portion 1A will be described in detail with reference to FIG. 2 , but the configurations of the second high-pressure pump portion 1B to the fourth high-pressure pump portion 1D are also the same as the configuration of the first high-pressure pump portion 1A.
  • a pump housing a common base end portion 3Y of the pump housing 3 is formed in a substantial circular cylinder shape that has an axial line in a direction perpendicular to the page surface, and a cam shaft 4 is disposed on the same axis inside the common base end portion 3Y. Additionally, a first circular cylinder portion 3A is formed integrally on the common base end portion 3Y of the pump housing 3, and a main structure portion of the first high-pressure pump portion 1A is incorporated inside the first circular cylinder portion 3A.
  • second to fourth circular cylinder portions 3B, 3C and 3D are formed integrally on the common base end portion 3Y in the same manner as the first circular cylinder portion 3A for the second high-pressure pump portion 1B, the third high-pressure pump portion 1C and the fourth high-pressure pump portion 1D (see FIG. 1 ), and the first high-pressure pump portion 1A to the fourth high-pressure pump portion 1D are configured to be driven with a phase difference by the cam shaft 4.
  • 11 is a barrel that is disposed coaxially inside the first circular cylinder portion 3A
  • 12 is a plunger that is disposed so as to be capable of reciprocal motion along the axial line thereof inside a plunger chamber 11A of the barrel 11, and the plunger 12 is configured to be guided on an inner wall surface 3Aa of the barrel 11 and movable in the axial line direction of the first circular cylinder portion 3A.
  • a base end portion 12A of the plunger 12 is pushed against a movement guidance member 13 by a resilient spring 14 via a spring seat 14a.
  • a rotating roller 13B that is rotatably fitted together by a support rod 13A is disposed in the movement guidance member 13.
  • the movement guidance member 13 is resiliently energized toward the cam shaft 4 by the resilient spring 14 interposed between the barrel 11 and the movement guidance member 13 such that the rotating roller 13B disposed as mentioned above in the movement guidance member 13 always pressure-contacts the cam shaft 4.
  • Fuel inside an external fuel tank (not shown) is sucked into the plunger chamber 11A via fuel inlet paths 17, 15C and 15B when the plunger 12 moves back toward the cam shaft 4. This fuel that has been sucked in is pressurized when the plunger 12 rises, and high-pressure fuel is obtained.
  • FIG. 15 What is represented by reference numeral 15 is an inlet/outlet valve assembly that is fixedly disposed on the distal end portion of the barrel 11 in order to take out the high-pressure fuel from the plunger chamber 11A.
  • a leak fuel takeout portion 16 for taking out, to the outside, leak fuel generated as a result of the high-pressure fuel being supplied to the inside of the plunger chamber 11A in order to lubricate the area between the barrel 11 and the plunger 12 with fuel is disposed in the barrel 11.
  • the leak fuel takeout portion 16 is configured by a fuel leak hole 16A, an annular port 16B that is disposed in an end portion on the plunger 12 side of the fuel leak hole 16A and is for accumulating the leak fuel inside the barrel, and an annual leak separate feed oil chamber 16C that is formed by an annular groove formed in an outer peripheral wall of the barrel 11 at the other end portion of the fuel leak hole 16A.
  • FIG. 3 is a cross-sectional diagram along line A-A of FIG. 1 .
  • the leak fuel takeout portion 26 is configured by a fuel leak hole 26A, an annular port 26B and a leak separate feed oil chamber 26C.
  • the leak fuel takeout portion 36 is configured by a fuel leak hole 36A, an annular port 36B and a leak separate feed oil chamber 36C.
  • the leak fuel takeout portion 46 is configured by a fuel leak hole 46A, an annular port 46B and a leak separate feed oil chamber 46C.
  • the connecting transport path 50 is a leak separate feed path for collecting and guiding, toward a fuel low-pressure side, the leak fuel that has been taken out by each of the leak fuel takeout portions 16, 26, 36 and 46. Consequently, each of the quantities of the leak fuel that has been taken out by the leak fuel takeout portions 16, 26, 36 and 46 of the high-pressure pump portions is fed to the connecting transport path 50 from the corresponding leak separate feed oil chambers 16C, 26C, 36C and 46C and is separately fed to a fuel low-pressure side such as, for example, a fuel tank.
  • a fuel low-pressure side such as, for example, a fuel tank.
  • the high-pressure fuel pump 1 is configured as described above, so the leak fuel generated by the high-pressure fuel for the lubrication between the barrels and the plungers is fed to a fuel low-pressure portion such as a fuel tank via the leak fuel takeout portions 16, 26, 36 and 46 disposed in the high-pressure pump portions, respectively.
  • a fuel low-pressure portion such as a fuel tank via the leak fuel takeout portions 16, 26, 36 and 46 disposed in the high-pressure pump portions, respectively.
  • FIG. 3 there is shown a case where the leak fuel of each of the high-pressure pump portions is fed to a fuel tank via the connecting transport path 50 from the four leak separate feed oil chambers 16C, 26C, 36C and 46C.
  • FIG. 4 is a diagram schematically showing this. However, the way that the leak fuel is allowed to escape is not limited to this configuration.
  • FIG. 5 is a diagram showing another example of the way that the leak fuel is allowed to escape.
  • the leak fuel is allowed to escape by disposing a dedicated escape passage 70 that interconnects the leak separate feed oil chambers 16C, 26C, 36C and 46C and connects the leak separate feed oil chambers 16C, 26C, 36C and 46C to another return passage inside a high-pressure pump.
  • a dedicated escape passage 70 that interconnects the leak separate feed oil chambers 16C, 26C, 36C and 46C and connects the leak separate feed oil chambers 16C, 26C, 36C and 46C to another return passage inside a high-pressure pump.
  • the leak fuel used for the fuel lubrication between the plungers and the barrels is not circulated and supplied to the barrels, so the high-pressure fuel supply pump according to the present invention controls a rise in the temperature of the plungers, can thus improve fuel injection efficiency, and is useful for the improvement of a high-pressure fuel supply pump.

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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)
  • Details Of Reciprocating Pumps (AREA)
EP07792693A 2006-11-24 2007-08-14 Pompe d'alimentation en combustible haute pression Withdrawn EP2088309A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006316693A JP2008128164A (ja) 2006-11-24 2006-11-24 高圧燃料供給ポンプ
PCT/JP2007/066078 WO2008062589A1 (fr) 2006-11-24 2007-08-14 Pompe d'alimentation en combustible haute pression

Publications (2)

Publication Number Publication Date
EP2088309A1 true EP2088309A1 (fr) 2009-08-12
EP2088309A4 EP2088309A4 (fr) 2010-06-02

Family

ID=39429530

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07792693A Withdrawn EP2088309A4 (fr) 2006-11-24 2007-08-14 Pompe d'alimentation en combustible haute pression

Country Status (4)

Country Link
EP (1) EP2088309A4 (fr)
JP (1) JP2008128164A (fr)
CN (1) CN101542107A (fr)
WO (1) WO2008062589A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2530315A1 (fr) * 2011-06-02 2012-12-05 Delphi Technologies Holding S.à.r.l. Lubrification de pompe à carburant
EP2530316A1 (fr) * 2011-06-02 2012-12-05 Delphi Technologies Holding S.à.r.l. Lubrification de pompes à carburant

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102465801B (zh) * 2010-11-18 2014-08-13 博世汽车柴油系统有限公司 高压燃油泵
CN201851241U (zh) * 2010-11-18 2011-06-01 博世汽车柴油系统股份有限公司 高压燃油泵
CN201851248U (zh) * 2010-11-18 2011-06-01 博世汽车柴油系统股份有限公司 高压燃油泵

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS586960A (ja) * 1981-07-03 1983-01-14 Daido Steel Co Ltd 高マンガン鋼レ−ル
JPS586960U (ja) * 1981-07-04 1983-01-17 ヤンマーディーゼル株式会社 燃料噴射ポンプ
DE3313322A1 (de) * 1983-04-13 1984-10-18 Klöckner-Humboldt-Deutz AG, 5000 Köln Einspritzpumpe fuer eine hubkolbenbrennkraftmaschine
US5339724A (en) * 1991-03-05 1994-08-23 Wartsila Diesel International Ltd. Oy Arrangement for the lubrication of the piston member of a fuel injection pump
JP3522782B2 (ja) * 1993-02-12 2004-04-26 ロバート ボッシュ ゲーエムベーハー ポンプ装置
JP3199105B2 (ja) 1994-06-24 2001-08-13 株式会社デンソー 高圧燃料供給ポンプ
JP3885506B2 (ja) * 2001-03-22 2007-02-21 いすゞ自動車株式会社 ジメチルエーテルエンジンの燃料噴射ポンプ

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2530315A1 (fr) * 2011-06-02 2012-12-05 Delphi Technologies Holding S.à.r.l. Lubrification de pompe à carburant
EP2530316A1 (fr) * 2011-06-02 2012-12-05 Delphi Technologies Holding S.à.r.l. Lubrification de pompes à carburant
WO2012163686A2 (fr) 2011-06-02 2012-12-06 Delphi Technologies Holding S.A.R.L. Perfectionnements apportés aux pompes à carburant
WO2012163686A3 (fr) * 2011-06-02 2013-12-05 Delphi Technologies Holding S.A.R.L. Perfectionnements apportés aux pompes à carburant
US9291132B2 (en) 2011-06-02 2016-03-22 Delphi International Operations Luxembourg S.A.R.L. Fuel pump assembly

Also Published As

Publication number Publication date
EP2088309A4 (fr) 2010-06-02
JP2008128164A (ja) 2008-06-05
WO2008062589A1 (fr) 2008-05-29
CN101542107A (zh) 2009-09-23

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