US20060239847A1 - High pressure pump for a fuel injection system of an internal combustion engine - Google Patents

High pressure pump for a fuel injection system of an internal combustion engine Download PDF

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Publication number
US20060239847A1
US20060239847A1 US10/539,749 US53974903A US2006239847A1 US 20060239847 A1 US20060239847 A1 US 20060239847A1 US 53974903 A US53974903 A US 53974903A US 2006239847 A1 US2006239847 A1 US 2006239847A1
Authority
US
United States
Prior art keywords
drive shaft
conduit
housing
bearing bush
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.)
Abandoned
Application number
US10/539,749
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English (en)
Inventor
Ulrich Maier
Achim Koehler
Sascha Ambrock
Peter Bauer
Vittorio Caroli
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.)
Robert Bosch GmbH
Original Assignee
Individual
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 Individual filed Critical Individual
Assigned to ROBERT BOSCH GMBH reassignment ROBERT BOSCH GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CAROLI, VITTORIO, AMBROCK, SASCHA, BAUER, PETER, KOEHLER, ACHIM, MAIER, ULRICH
Publication of US20060239847A1 publication Critical patent/US20060239847A1/en
Abandoned legal-status Critical Current

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Classifications

    • 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
    • F04B1/0413—Cams
    • 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

Definitions

  • the invention is based on a high-pressure pump for a fuel injection system of an internal combustion engine as generically defined by the preamble to claim 1 .
  • This high-pressure pump has a housing, located in which is at least one pump element which has a pump piston that is driven in a reciprocating motion, via a transmission element in the form of a polygonal ring, by a drive shaft rotatably supported in the housing.
  • the drive shaft has an eccentric portion, on which the transmission element is rotatably supported via a bearing bush.
  • the drive shaft is supported in the housing via two bearing points, each with one bearing bush. Lubrication of the bearing point of the transmission element on the eccentric portion of the drive shaft and of the bearing points of the drive shaft in the housing is effected by means of the fuel present in the interior of the housing.
  • the high-pressure pump according to the invention as defined by the characteristics of claim 1 has the advantage over the prior art that the lubrication of at least the bearing point of the transmission element on the eccentric portion of the drive shaft is improved, at the cost of only little structural complexity, so that fuel can be pumped at very high pressure by the high-pressure pump with little wear to the bearing point.
  • the lubrication of the at least one bearing point of the drive shaft is also improved.
  • the embodiment in accordance with claims 4 and 5 makes a further-improved lubrication of the bearing point possible by means of improved distribution of the fuel at the bearing point.
  • the embodiment in accordance with claim 6 makes simple manufacture of the conduit system in the drive shaft possible.
  • the embodiment in accordance with claims 7 and 8 makes it simple to deliver fuel into the conduit system of the drive shaft, through a bearing point of the drive shaft.
  • FIG. 1 shows a fuel injection system of an internal combustion engine having a high-pressure pump
  • FIG. 2 shows the high-pressure pump in a longitudinal section on a larger scale
  • FIG. 3 shows a detail, marked III in FIG. 2 , with a bearing point of the high-pressure pump on a larger scale;
  • FIG. 4 shows a detail, marked IV in FIG. 2 , with a bearing point of the high-pressure pump on a larger scale.
  • a fuel injection system for an internal combustion engine that is a self-igniting internal combustion engine.
  • the fuel injection system has a high-pressure pump 100 , by which fuel is pumped into a reservoir 110 at high pressure of up to 2000 bar. From the reservoir 110 , lines 120 lead to injectors 130 , located at the engine cylinders, through which injectors fuel is injected into the combustion chamber of the cylinders.
  • injectors 130 located at the engine cylinders, through which injectors fuel is injected into the combustion chamber of the cylinders.
  • a feed pump 140 fuel is pumped from a tank 150 to the intake side of the high-pressure pump 100 .
  • a pressure of for instance approximately 2 to 10 bar is generated.
  • a fuel metering device 160 may be located, by which the inflow of fuel from the feed pump 140 to the high-pressure pump 100 can be variably adjusted.
  • a lubrication connection 170 branches off from the communication between the feed pump 140 and the high-pressure pump 100 toward a drive region of the high-pressure pump 100 ; both the high-pressure pump 100 and its drive region will be described in further detail hereinafter.
  • a pressure valve 180 is located in the lubrication connection 170 and opens the lubrication connection 170 only when a predetermined pressure is exceeded. The flow through the lubrication connection 170 is preferably limited by a throttle restriction 190 .
  • the high-pressure pump 100 is shown enlarged.
  • the high-pressure pump has a housing 10 , which is embodied in multiple parts and in which a drive shaft 12 is located.
  • the drive shaft 12 is rotatably supported in the housing 10 via two bearing points 14 and 16 , spaced apart from one another in the direction of the pivot axis 13 of the drive shaft 12 .
  • the bearing points 14 , 16 may be located in different parts of the housing 10 .
  • the housing 10 has a bore 18 , 20 , respectively, in which the drive shaft 12 is supported, via a respective bearing bush 22 , 24 .
  • the drive shaft 12 has an eccentric portion 26 , on which a transmission element 28 in the form of a polygonal ring is rotatably supported via a bearing point 30 .
  • the high-pressure pump 100 has at least one and preferably a plurality of pump elements 32 located in the housing 10 , each with a respective pump piston 34 that is driven by the transmission element 28 in a reciprocating motion in a direction at least approximately radial to the pivot axis 13 of the drive shaft 12 .
  • the pump piston 34 is guided tightly displaceably in a cylinder bore 36 in the housing 10 , or in an insert in the housing 10 , and with its face end facing away from the transmission element 28 , it defines a pump work chamber 38 in the cylinder bore 36 .
  • the pump work chamber 38 Via a fuel inlet conduit 40 extending in the housing 10 , the pump work chamber 38 has a communication with the feed pump 140 .
  • An inlet valve 42 which opens into the pump work chamber 38 and has a spring-loaded valve member 43 , is located at the orifice of the fuel inlet conduit 40 into the pump work chamber 38 .
  • the pump work chamber 38 furthermore has a communication with the reservoir 110 , via a fuel outlet conduit 44 extending in the housing 10 .
  • An outlet valve 46 opening out from the pump work chamber 38 , is located at the orifice of the fuel outlet conduit 44 in the pump work chamber 38 and likewise has a spring-loaded valve member 47 .
  • the pump piston 34 is kept with its piston base 50 in contact with the transmission element 28 by means of a prestressed spring 48 .
  • the transmission element 28 Upon the rotary motion of the drive shaft 12 , the transmission element 28 is not moved with the drive shaft, but because of the eccentric portion 26 , it executes a motion perpendicular to the pivot axis 13 of the drive shaft 12 , which brings about the reciprocating motion of the pump piston 34 .
  • the pump work chamber 38 is filled with fuel through the fuel inlet conduit 40 while the inlet valve 42 is open and the outlet valve 46 is closed.
  • fuel is pumped at high pressure by the pump piston 34 through the fuel outlet conduit 44 to the reservoir 110 , with the outlet valve 46 open and the inlet valve 42 closed.
  • the lubrication connection 170 originating at the feed pump 140 , extends in the housing 10 in a conduit 52 that discharges at the outer jacket of the drive shaft 12 .
  • a conduit system is embodied, into which the conduit 52 discharges and through which fuel is carried under pressure to the bearing point 30 of the transmission element 28 on the eccentric portion 26 of the drive shaft 12 , where the fuel emerges from the conduit system and lubricates the bearing point 30 .
  • the conduit system in the drive shaft 12 has a first conduit portion 54 , which extends for instance at least approximately radially to the pivot axis 13 of the drive shaft 12 and is embodied as a bore, made from the outer jacket of the drive shaft 12 into the drive shaft and extending approximately to the middle of the drive shaft 12 .
  • the first conduit portion 54 discharges at the outer jacket of the drive shaft 12 in a plane in which the orifice of the conduit 52 in the housing 10 is also located.
  • the first conduit portion 54 is adjoined by a second conduit portion 55 , which extends in the direction of the pivot axis 13 of the drive shaft 12 , for instance coaxially to the pivot axis 13 .
  • the second conduit portion 55 is embodied as a longitudinal bore, in particular in the form of a blind bore, made from one face end of the drive shaft 12 into the drive shaft.
  • the second conduit portion 55 is closed, toward the face end of the drive shaft 12 , by means of a closure element 56 inserted into the drive shaft.
  • the second conduit portion 55 is adjoined by a third conduit portion 57 , which extends for instance at least approximately radially to the pivot axis 13 of the drive shaft 12 and is embodied as a bore made into the drive shaft 12 from its outer jacket and which extends approximately to the middle of the drive shaft 12 and discharges into the second conduit portion 55 .
  • the third conduit portion 57 discharges at the outer jacket of the eccentric portion 26 of the drive shaft 12 , preferably at least approximately in the middle of the bearing point 30 of the transmission element 28 .
  • Fuel pumped by the feed pump 140 travels via the lubrication connection 170 , the conduit 52 , and the conduit system 54 , 55 , 57 in the drive shaft 12 to reach the bearing point 30 of the transmission element 28 on the eccentric portion 26 of the drive shaft 12 , where it emerges in order to lubricate it.
  • the transmission element 28 is supported directly on the eccentric portion 26 .
  • the transmission element 28 is supported on the eccentric portion 26 via a bearing bush 58 .
  • the bearing bush 58 may be embodied in one piece, as shown in FIG. 3 , or in two parts, as shown in FIG. 2 .
  • the bearing bush 58 is split into two parts, located side by side in the direction of the pivot axis 13 of the drive shaft 12 , and between which parts there is a gap 59 .
  • the gap 59 is preferably located in a plane in which the third conduit portion 57 discharges at the outer jacket of the eccentric portion 26 .
  • the lubrication of the bearing point 30 is improved further by the split bearing bush 58 , because the fuel emerging from the third conduit portion 57 can be distributed better in the bearing point 30 .
  • bearing points 14 , 16 of the drive shaft 30 in the housing 10 can also be lubricated through the conduit system in the drive shaft 12 .
  • the second conduit portion 55 continues in the direction of the pivot axis 13 of the drive shaft 12 as far as the bearing point 16 , where a fourth conduit portion 60 adjoins it.
  • the fourth conduit portion 60 extends for instance at least approximately radially to the pivot axis 13 of the drive shaft 12 and is embodied as a bore that is made into the drive shaft 12 from its outer jacket and that extends approximately to the middle of the drive shaft 12 and discharges into the second conduit portion 55 .
  • the fourth conduit portion 60 discharges at the outer jacket of the drive shaft 12 , preferably at least approximately in the middle of the bearing point 16 of the drive shaft 12 .
  • the bearing bush 24 of the bearing point 16 may be in one piece or, as described above for the bearing bush 58 , in two parts, with a gap 25 between the parts.
  • the bearing point 14 of the drive shaft 12 in the housing 10 can also be lubricated by the fuel pumped by the feed pump 140 via the lubrication connection 170 and the conduit 52 .
  • the first conduit portion 54 then discharges at the outer jacket of the drive shaft 12 in the region of the bearing point 14 , preferably at least approximately in the middle of the bearing point 14 .
  • the bearing shell 22 may be divided into two parts, as shown in FIG. 2 and as explained above for the bearing shell 58 ; the gap 23 between the parts of the bearing shell 22 is located in the plane of the orifice of the first conduit portion 54 at the outer jacket of the drive shaft 12 .
  • FIG. 4 a modified version of the bearing shell 22 is shown, in which the bearing shell is in one piece.
  • the bearing shell 22 In its inner jacket, the bearing shell 22 has an annular groove 62 , which is formed by a plunge cut.
  • the annular groove 62 is located at least approximately in the same plane as the orifice of the conduit 52 at the outer jacket of the bearing bush 22 and the orifice of the first conduit portion 54 at the inner jacket of the bearing bush 22 .
  • the bearing bush 22 furthermore has at least one bore 64 , which connects the annular groove 62 to the outer jacket of the bearing bush 22 . From the conduit 52 , fuel can flow through the bore 64 and the annular groove 62 into the first conduit portion 54 of the drive shaft 12 .
  • respective outlet conduits 66 may be provided in the housing 10 , through which conduits fuel can flow away again from the bearing points.
US10/539,749 2002-12-18 2003-12-16 High pressure pump for a fuel injection system of an internal combustion engine Abandoned US20060239847A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10259178.4 2002-12-18
DE10259178A DE10259178A1 (de) 2002-12-18 2002-12-18 Hochdruckpumpe für eine Kraftstoffspritzeinrichtung einer Brennkraftmaschine
PCT/DE2003/004134 WO2004055368A1 (de) 2002-12-18 2003-12-16 Hochdruckpumpe für eine kraftstoffeinspritzeinrichtung einer brennkraftmaschine

Publications (1)

Publication Number Publication Date
US20060239847A1 true US20060239847A1 (en) 2006-10-26

Family

ID=32477745

Family Applications (1)

Application Number Title Priority Date Filing Date
US10/539,749 Abandoned US20060239847A1 (en) 2002-12-18 2003-12-16 High pressure pump for a fuel injection system of an internal combustion engine

Country Status (6)

Country Link
US (1) US20060239847A1 (de)
EP (1) EP1576287A1 (de)
JP (1) JP2006510835A (de)
CN (1) CN1729360A (de)
DE (1) DE10259178A1 (de)
WO (1) WO2004055368A1 (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITMI20081928A1 (it) * 2008-10-31 2010-05-01 Bosch Gmbh Robert Metodo ed impianto di alimentazione di combustibile ad un motore a combustione interna
US20120266849A1 (en) * 2009-12-22 2012-10-25 Robert Bosch Gmbh System for feeding fuel from a tank to an internal combustion engine
WO2018178501A1 (en) * 2017-03-29 2018-10-04 Wärtsilä Finland Oy A high pressure fuel pump assembly for an internal combustion piston engine
IT201700076837A1 (it) * 2017-07-07 2019-01-07 Bosch Gmbh Robert Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, da un serbatoio di contenimento ad un motore a combustione interna

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1657429A1 (de) * 2004-11-12 2006-05-17 C.R.F. Società Consortile per Azioni Hochdruckpumpe für eine Brennkraftmaschine
WO2006053792A1 (de) * 2004-11-17 2006-05-26 Siemens Aktiengesellschaft Pumpenanordnung
DE602005021384D1 (de) 2005-12-27 2010-07-01 Fiat Ricerche Kraftstoffhochdruckpumpe, mit der kraftstoffzuleitung in verbindung mit dem pumpensumpf
DE102009028795A1 (de) * 2009-08-21 2011-02-24 Robert Bosch Gmbh Kraftstoffhochdruckpumpe
DE102011089959A1 (de) * 2011-12-27 2013-06-27 Robert Bosch Gmbh Kraftstoffhochdruckpumpe für ein Kraftstoffeinspritzsystem
DE102012222134A1 (de) * 2012-12-04 2014-06-05 Robert Bosch Gmbh Pumpe, insbesondere Kraftstoffhochdruckpumpe für eine Brennkraftmaschine
GB201508464D0 (en) * 2015-05-18 2015-07-01 Delphi Int Operations Lux Srl Pump assembly for a fuel injection system
JP6096255B2 (ja) * 2015-08-31 2017-03-15 中禾亞股▲ふん▼有限公司 液体加圧ポンプの出力軸潤滑構造
CN114738154A (zh) * 2022-04-25 2022-07-12 广西玉柴机器股份有限公司 一种喷油泵驱动轴结构

Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4078529A (en) * 1976-04-15 1978-03-14 Douglas Warwick Rotary engine
US4301777A (en) * 1979-11-28 1981-11-24 General Motors Corporation Fuel injection pump
US4476836A (en) * 1982-01-11 1984-10-16 Nippondenso Co., Ltd. Fuel-injecting apparatus
US5630708A (en) * 1993-12-28 1997-05-20 Zexel Corporation Radial piston pump for low-viscosity fuel
US5967123A (en) * 1996-07-10 1999-10-19 Robert Bosch Gmbh Fuel pump
US6009854A (en) * 1997-02-20 2000-01-04 Wartsila Nsd Oy Ab Arrangement for a injection pump in an internal combustion engine
US6345609B1 (en) * 1998-02-27 2002-02-12 Stanadyne Automotive Corp. Supply pump for gasoline common rail
US6457957B1 (en) * 1998-10-17 2002-10-01 Bosch Gmbh Robert Radial piston pump for generating high fuel pressure
US20020189436A1 (en) * 2001-06-19 2002-12-19 Robert Bosch Gmbh High-pressure fuel pump for internal combustion engine with improved partial-load performance
US20030108443A1 (en) * 2001-12-12 2003-06-12 Masashi Suzuki Fuel injection pump
US6694950B2 (en) * 1999-02-17 2004-02-24 Stanadyne Corporation Hybrid control method for fuel pump using intermittent recirculation at low and high engine speeds
US6796778B2 (en) * 2001-09-03 2004-09-28 Denso Corporation Fuel injection pump having throttled fuel path for fuel lubrication
US7134846B2 (en) * 2004-05-28 2006-11-14 Stanadyne Corporation Radial piston pump with eccentrically driven rolling actuation ring

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19924064B4 (de) * 1999-05-26 2007-07-05 Siemens Ag Verdrängerpumpe
DE10012306C2 (de) * 2000-03-14 2003-12-24 Bosch Gmbh Robert Verteilereinspritzpumpe

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4078529A (en) * 1976-04-15 1978-03-14 Douglas Warwick Rotary engine
US4301777A (en) * 1979-11-28 1981-11-24 General Motors Corporation Fuel injection pump
US4476836A (en) * 1982-01-11 1984-10-16 Nippondenso Co., Ltd. Fuel-injecting apparatus
US5630708A (en) * 1993-12-28 1997-05-20 Zexel Corporation Radial piston pump for low-viscosity fuel
US5967123A (en) * 1996-07-10 1999-10-19 Robert Bosch Gmbh Fuel pump
US6009854A (en) * 1997-02-20 2000-01-04 Wartsila Nsd Oy Ab Arrangement for a injection pump in an internal combustion engine
US6345609B1 (en) * 1998-02-27 2002-02-12 Stanadyne Automotive Corp. Supply pump for gasoline common rail
US6457957B1 (en) * 1998-10-17 2002-10-01 Bosch Gmbh Robert Radial piston pump for generating high fuel pressure
US6694950B2 (en) * 1999-02-17 2004-02-24 Stanadyne Corporation Hybrid control method for fuel pump using intermittent recirculation at low and high engine speeds
US20020189436A1 (en) * 2001-06-19 2002-12-19 Robert Bosch Gmbh High-pressure fuel pump for internal combustion engine with improved partial-load performance
US6817841B2 (en) * 2001-06-19 2004-11-16 Robert Bosch Gmbh High-pressure fuel pump for internal combustion engine with improved partial-load performance
US6796778B2 (en) * 2001-09-03 2004-09-28 Denso Corporation Fuel injection pump having throttled fuel path for fuel lubrication
US20030108443A1 (en) * 2001-12-12 2003-06-12 Masashi Suzuki Fuel injection pump
US7134846B2 (en) * 2004-05-28 2006-11-14 Stanadyne Corporation Radial piston pump with eccentrically driven rolling actuation ring

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITMI20081928A1 (it) * 2008-10-31 2010-05-01 Bosch Gmbh Robert Metodo ed impianto di alimentazione di combustibile ad un motore a combustione interna
US20120266849A1 (en) * 2009-12-22 2012-10-25 Robert Bosch Gmbh System for feeding fuel from a tank to an internal combustion engine
US9133804B2 (en) * 2009-12-22 2015-09-15 Robert Bosch Gmbh System for feeding fuel from a tank to an internal combustion engine
WO2018178501A1 (en) * 2017-03-29 2018-10-04 Wärtsilä Finland Oy A high pressure fuel pump assembly for an internal combustion piston engine
CN110691904A (zh) * 2017-03-29 2020-01-14 瓦锡兰芬兰有限公司 用于内燃机活塞发动机的高压燃料泵组件
IT201700076837A1 (it) * 2017-07-07 2019-01-07 Bosch Gmbh Robert Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, da un serbatoio di contenimento ad un motore a combustione interna

Also Published As

Publication number Publication date
JP2006510835A (ja) 2006-03-30
EP1576287A1 (de) 2005-09-21
DE10259178A1 (de) 2004-07-08
CN1729360A (zh) 2006-02-01
WO2004055368A1 (de) 2004-07-01

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Legal Events

Date Code Title Description
AS Assignment

Owner name: ROBERT BOSCH GMBH, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:MAIER, ULRICH;KOEHLER, ACHIM;AMBROCK, SASCHA;AND OTHERS;REEL/FRAME:018045/0597;SIGNING DATES FROM 20050511 TO 20050525

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION