EP2409015B1 - Hochdruckpumpe - Google Patents

Hochdruckpumpe Download PDF

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Publication number
EP2409015B1
EP2409015B1 EP10700433.5A EP10700433A EP2409015B1 EP 2409015 B1 EP2409015 B1 EP 2409015B1 EP 10700433 A EP10700433 A EP 10700433A EP 2409015 B1 EP2409015 B1 EP 2409015B1
Authority
EP
European Patent Office
Prior art keywords
bearing
valve
pressure
pressure pump
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.)
Not-in-force
Application number
EP10700433.5A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2409015A1 (de
Inventor
Christian Langenbach
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
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to PL10700433T priority Critical patent/PL2409015T3/pl
Publication of EP2409015A1 publication Critical patent/EP2409015A1/de
Application granted granted Critical
Publication of EP2409015B1 publication Critical patent/EP2409015B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04B1/0452—Distribution members, e.g. 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
    • 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
    • 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
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/005—Pressure relief valves
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/1002—Ball 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
    • F02M59/02—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
    • F02M59/06—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 with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • the present invention relates to a high pressure pump for a fuel injection system of an internal combustion engine, in particular for a common rail injection system, according to the preamble of claim 1.
  • a high-pressure fuel pump for an internal combustion engine in which the bearings of the drive shaft are forcibly traversed by fuel and thereby the mechanical and thermal capacity of the bearing and thus the entire high-pressure fuel pump is significantly increased.
  • a first and a second sliding bearing are provided for storage of the drive shaft while a first and a second sliding bearing are provided.
  • a first check valve is arranged downstream of and in series with the first bearing.
  • a second check valve is arranged downstream and in series with the second bearing.
  • the opening pressure of the check valves is chosen so that they are closed when starting the internal combustion engine and open only when the internal combustion engine is running.
  • the opening pressure which have the non-return valves used in the prior art, is in a range which is greater than 1.0 bar. This opening pressure is so high that the check valves open only after the suction valves of the high-pressure fuel pump, so that z. B. in the start case no leakage through the bearing occurs, which is disadvantageous for this.
  • a high-pressure pump for a fuel injection system of an internal combustion engine, in particular for a common rail injection system, which has one of at least one arranged in a bearing return bearing bearing drive shaft, wherein downstream of the at least one bearing at least one valve is arranged, which is an opening pressure which is in a range of 0.1 bar to 0.8 bar.
  • the high-pressure pump according to the invention which has the at least one valve with a low opening pressure, the mass balance situation becomes particularly at start-up the internal combustion engine improved.
  • the valve reduces the leakage through the at least one bearing in the starting of the internal combustion engine and thus improves the starting power (the required speed or the time to start).
  • the valve with a low opening pressure which is below or equal to 0.8 bar, opens early enough so that the permissible pressure on the commonly existing shaft seal is not exceeded, which in turn does not unduly shorten the service life.
  • the valve does not close even if there is a violation of the low-pressure quantity balance, so that a bearing flow is ensured in all operating cases. Therefore, the high pressure pump as a whole becomes more robust both in terms of functionality and durability.
  • the opening pressure of the valve in an opening pressure range of less than or equal to 0.8 bar and greater than or equal to 0.1 bar has the advantage that on the one hand - as already mentioned above - at low speeds and in particular at the operating point of the engine start to a significant reduction of Leakages leads, but on the other hand ensures a minimum leakage at the start. Even with massive violation of the low pressure quantity balance in the low pressure circuit of the fuel injection system, a minimum leakage for the at least one bearing is therefore ensured.
  • the at least one valve is a check valve, in particular a ball check valve.
  • the fuel can flow through at least one bearing.
  • the at least one bearing is a plain bearing. Therefore, when flowing through the bearing with fuel forms a hydrostatic lubricating wedge, which improves the load capacity of the bearing.
  • a first bearing and a second bearing for supporting the drive shaft are provided.
  • a first valve is provided in the bearing return downstream of the first bearing and a second valve is provided in the bearing return downstream of the second bearing.
  • the first valve is arranged in series with the first bearing and the second valve in series with the second bearing.
  • a valve in particular a ball check valve, individually or after merging of individual or all bearing returns for these can be positioned together.
  • the further fuel supply of the bearing returns is irrelevant.
  • the respective bearing return of the first bearing and the second bearing opens into a common bearing return, wherein a common valve is provided in the common bearing return.
  • the drive shaft is a camshaft or an eccentric shaft, which is arranged in an interior of a pump housing.
  • bearing return and the interior of the pump housing are hydraulically connected.
  • the configuration according to the invention can be used particularly advantageously in all fuel injection systems which have a mechanical feed pump in the pump inlet, the use being particularly advantageous in cases where there are no further consumers in the fuel return (eg tank jet pumps, temperature circuits, etc.) is, because then the maximum potential, d. H. the highest opening pressure in the opening pressure range of 0.1 to 0.8 bar according to the invention can be utilized.
  • a block diagram of a common rail fuel injection system 1 is shown with a high pressure pump 2, which consists essentially of a tank 3, a feed pump 4 with an element for flow limitation 5, a filter 6, a rail 7 and a pressure relief valve 8 and pressure control valve.
  • the injectors, which are connected to the rail 7, are in Fig. 1 not shown.
  • the element for limiting the flow rate 5 is designed as a throttle, which is arranged directly at the entrance of the prefeed pump 4.
  • the throttle causes the total compressed in the high-pressure pump 2 amount of fuel is limited.
  • the pressure resulting in an inner space 9 of the high-pressure pump 2 is limited in accordance with a characteristic curve of a pressure regulating valve 10.
  • the pressure relief valve 8 opens into a return line 11, in which the leakage quantities of the injectors, not shown, are discharged.
  • the return line 11 opens into the tank 3 and drives there possibly a jet pump (not shown).
  • the temperature sensor T can also be arranged.
  • the high-pressure pump 2 is hydraulically connected to the tank 3 via a fuel inlet 12, the filter 6 and the prefeed pump 4.
  • the fuel inlet 12 connects a delivery side of the prefeed pump 4 with the interior 9 of the pump housing, so that the entire flow of the prefeed pump 4 passes into the interior 9.
  • the prefeed pump 4 is designed as a gear pump. Between the prefeed pump 4 is a gap between the rotating components and the pump housing, causing leakage losses, which in FIG. 1 is represented by the symbol of a throttle (see reference numeral 29). The leaked through the gap leakage amount is discharged through a leakage line 30.
  • the leakage line 30 opens in front of a first valve 27 in the line (without reference numeral), which supplies the flowing through a first bearing 23 amount of fuel via the first valve 27 of the return line 11.
  • a fuel return 13 provides a hydraulic connection between the interior 9 of the pump housing on the one hand and a metering unit 14 and the return line 11 on the other. Between the fuel return line 13 and the return line 11, the pressure regulating valve 10 is arranged.
  • the metering unit 14 serves to control the amount of fuel sucked by pump elements 15 of the high-pressure pump and thus also the delivery rate thereof.
  • the suction sides of the pump elements 15 are hydraulically connected via a distribution line to the output of the metering unit 14.
  • the pump elements 15 consist essentially of suction valves 16, high pressure side check valves 17 and a piston 18 which oscillates in a cylinder bore (not shown).
  • the pistons 18 of the pump elements 15 are driven via roller tappet 19 by cams 20 of a drive shaft 21.
  • the pump elements 15 convey fuel under high pressure via a high-pressure line 22 into the rail 7.
  • the cams 20 are part of the drive shaft 21 which is rotatably mounted on both sides of the cams 20 in a first bearing 23 and in a second bearing 24 (each shown as a throttle in the figure) in a pump housing (not shown).
  • the drive shaft 21 is arranged in the interior 9 of the pump housing.
  • the pressure regulating valve 10 is downstream of the interior 9 of the high-pressure pump 2 arranged.
  • the pressure regulating valve 10 comprises a leakage line 25 in which optionally a throttle 26 may be provided.
  • the increased internal pressure in the interior 9 of the pump housing leads inter alia to the fact that, depending on the pressure prevailing in the interior 9, the viscosity of the fuel and the flow resistance of the first bearing 23 and a second bearing 24 of the drive shaft 21, a defined amount of fuel through the bearings 23 and 24 is pressed. This leads to a significant increase in the load capacity of both the first bearing 23 and the second bearing 24th
  • first bearing 23 and the second bearing 24 are formed as sliding bearings, formed by the forced flow through the bearings 23 and 24 in the bearings 23 and / or 24, a hydrostatic lubricating wedge. As a result, the load capacity of the first bearing 23 and the second bearing 24 increases considerably and at the same time the heat dissipation from the first bearing 23 and the second bearing 24 is improved.
  • a first valve 27 is arranged, which is formed as a check valve.
  • a second valve 28 is arranged, which is also designed as a check valve.
  • the first valve 27 and the second valve 28 open into the return line 11.
  • the opening pressure of the valves 27 and 28 according to the prior art is more than 1 bar and is chosen so that they are closed when starting the engine and only open when the internal combustion engine is running.
  • FIG. 2 shows a block diagram of a portion of the fuel injection system, which substantially like the fuel injection system 1 of FIG. 1 is constructed with a high-pressure pump 2 according to one embodiment.
  • a drive shaft accommodated in the interior 9 and not shown in detail is supported on both sides of the interior 9 by a first bearing 23 and a second bearing 24.
  • the first bearing 23 and the second bearing 24 are formed as sliding bearings and are each arranged in a bearing return 31 and 31 '.
  • a first valve 27 Downstream of the first bearing 23 and in series with it, a first valve 27 is arranged, which is designed as a check valve or as a ball check valve.
  • a second valve 28 Downstream of the second bearing 24 and in series with it, a second valve 28 is arranged, which is likewise designed as a check valve or as a ball check valve.
  • first and second valves 27, 28 of FIG. 1 The effect and operation is essentially the same as that already associated with the first and second valves 27, 28 of FIG. 1 has been described, but with the difference that the first valve 27 and / or the second valve 28 according to the embodiment have an opening pressure which is less than or equal to 0.8 bar and greater than or equal to 0.1 bar. Therefore, in contrast to the first and second valves 27, 28 of FIG. 1, the first valve 27 and / or the second valve 28 are open when the internal combustion engine is started.
  • FIG. 3 shows a further block diagram of a portion of the fuel injection system with a high pressure pump 2 according to another embodiment.
  • a common valve 32 which is designed as a check valve or as a ball check valve is provided.
  • the common valve 32 is arranged in a common bearing return 31 "into which the bearing returns 31, 31 'open, and the common valve 32 in this embodiment also has an opening pressure which is less than or equal to 0.8 bar and greater than or equal to zero , 1 bar, so that the common valve 32 is open at the start of the internal combustion engine.
  • the configuration according to the invention provides a high-pressure pump 2 which is improved in terms of its functionality and more robust in terms of its durability.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
EP10700433.5A 2009-03-16 2010-01-19 Hochdruckpumpe Not-in-force EP2409015B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL10700433T PL2409015T3 (pl) 2009-03-16 2010-01-19 Pompa wysokiego ciśnienia

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009001563A DE102009001563A1 (de) 2009-03-16 2009-03-16 Hochdruckpumpe
PCT/EP2010/050575 WO2010105861A1 (de) 2009-03-16 2010-01-19 Hochdruckpumpe

Publications (2)

Publication Number Publication Date
EP2409015A1 EP2409015A1 (de) 2012-01-25
EP2409015B1 true EP2409015B1 (de) 2013-07-24

Family

ID=41667533

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10700433.5A Not-in-force EP2409015B1 (de) 2009-03-16 2010-01-19 Hochdruckpumpe

Country Status (10)

Country Link
US (1) US8485159B2 (pl)
EP (1) EP2409015B1 (pl)
JP (1) JP5390692B2 (pl)
CN (1) CN102356229B (pl)
BR (1) BRPI1009474B1 (pl)
DE (1) DE102009001563A1 (pl)
ES (1) ES2425380T3 (pl)
PL (1) PL2409015T3 (pl)
RU (1) RU2523525C2 (pl)
WO (1) WO2010105861A1 (pl)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010043439A1 (de) * 2010-11-05 2012-05-10 Robert Bosch Gmbh Kraftstoffeinspritzsystem einer Brennkraftmaschine
DE102012212062A1 (de) * 2012-07-11 2014-01-16 Robert Bosch Gmbh Niederdruckkreislauf für ein Kraftstoffeinspritzsystem, Kraftstoffeinspritzsystem sowie Verfahren zum Betreiben eines Kraftstoffeinspritzsystems

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2003823C1 (ru) * 1991-06-21 1993-11-30 Центральный научно-исследовательский дизельный институт Топливовпрыскивающий насос высокого давлени двигател внутреннего сгорани
RU2059847C1 (ru) * 1993-05-07 1996-05-10 Виктор Альбертович Пилюш Роторный двигатель внутреннего сгорания
DE19746563A1 (de) * 1997-10-22 1999-04-29 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
DE19818385A1 (de) * 1998-04-24 1999-10-28 Bosch Gmbh Robert Zuschaltventil in einem Kraftstoffeinspritzsystem für Brennkraftmaschinen
DE19926308A1 (de) * 1999-06-09 2000-12-21 Bosch Gmbh Robert Pumpenanordnung für Kraftstoff
JP3915718B2 (ja) * 2003-03-11 2007-05-16 株式会社デンソー 燃料供給ポンプ
DE102005027851A1 (de) * 2005-06-16 2006-12-21 Robert Bosch Gmbh Kraftstoffeinspritzsystem für eine Brennkraftmaschine
DE602005021384D1 (de) * 2005-12-27 2010-07-01 Fiat Ricerche Kraftstoffhochdruckpumpe, mit der kraftstoffzuleitung in verbindung mit dem pumpensumpf
DE102006048356A1 (de) * 2006-10-12 2008-04-17 Robert Bosch Gmbh Kraftstoffhochdruckpumpe und Kraftstoffeinspritzsystem für eine Brennkraftmaschine
JP4483979B2 (ja) * 2008-05-15 2010-06-16 株式会社デンソー 燃料供給装置
JP5126097B2 (ja) * 2009-02-06 2013-01-23 株式会社デンソー 燃料供給装置

Also Published As

Publication number Publication date
BRPI1009474A2 (pt) 2016-03-01
CN102356229A (zh) 2012-02-15
BRPI1009474B1 (pt) 2020-08-04
ES2425380T3 (es) 2013-10-15
US8485159B2 (en) 2013-07-16
RU2011141707A (ru) 2013-04-27
PL2409015T3 (pl) 2013-12-31
RU2523525C2 (ru) 2014-07-20
WO2010105861A1 (de) 2010-09-23
JP5390692B2 (ja) 2014-01-15
DE102009001563A1 (de) 2010-09-23
CN102356229B (zh) 2013-11-20
EP2409015A1 (de) 2012-01-25
US20110315120A1 (en) 2011-12-29
JP2012520422A (ja) 2012-09-06

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