WO2005124153A1 - Pompe haute pression conçue pour un dispositif d'injection de carburant d'un moteur a combustion interne - Google Patents

Pompe haute pression conçue pour un dispositif d'injection de carburant d'un moteur a combustion interne Download PDF

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Publication number
WO2005124153A1
WO2005124153A1 PCT/EP2005/051738 EP2005051738W WO2005124153A1 WO 2005124153 A1 WO2005124153 A1 WO 2005124153A1 EP 2005051738 W EP2005051738 W EP 2005051738W WO 2005124153 A1 WO2005124153 A1 WO 2005124153A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
valve member
valve
pump piston
suction
Prior art date
Application number
PCT/EP2005/051738
Other languages
German (de)
English (en)
Inventor
Michael Mennicken
Andreas Kellner
Falko Bredow
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 JP2007515913A priority Critical patent/JP4589382B2/ja
Priority to US11/597,917 priority patent/US20080069712A1/en
Publication of WO2005124153A1 publication Critical patent/WO2005124153A1/fr

Links

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
    • 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
    • F04B53/12—Valves; Arrangement of valves arranged in or on pistons
    • F04B53/125—Reciprocating valves
    • F04B53/129—Poppet 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
    • F04B53/102—Disc valves
    • F04B53/1022—Disc valves having means for guiding the closure member axially

Definitions

  • the invention relates to a high-pressure pump for a fuel injection device of an internal combustion engine according to the preamble of claim 1.
  • Such a high pressure pump is known from DE 198 48 035 AI.
  • This high-pressure pump has at least one pump element, with a pump piston which is driven in a lifting movement and which is displaceably guided in a cylinder bore and delimits a pump working space in the latter.
  • the pump workspace can be filled with fuel via a suction valve.
  • the suction valve has a valve member which opens into the pump work space and which interacts with a valve seat.
  • the pump piston In its end region facing the suction valve, the pump piston has a blind bore into which the valve member of the suction valve is immersed and in which a closing spring acting on the valve member is arranged, which is supported on the one hand on the pump piston and on the other hand on the valve member.
  • the valve member has a shaft surrounded by the closing spring, with which the valve member is displaceably guided in the closing spring.
  • the outside diameter of the closing spring is only slightly smaller than the diameter of the blind hole in the pump piston, so that the closing spring is guided in the blind hole of the pump piston.
  • the high pressure pump according to the invention with the features according to claim 1 has the advantage that the valve member of the suction valve is precisely guided in the pump piston, whereby the function of the suction valve and thus the high pressure pump is improved.
  • the embodiment according to claim 3 enables a large guide length of the valve member in the blind bore with a space-saving arrangement of the closing spring.
  • the embodiment according to claim 4 enables the spring chamber to be filled and emptied during the movement of the valve member, the opening and / or closing movement of the at least one opening in the valve member being able to be influenced in a targeted manner.
  • the design according to claim 5 enables a very precise guidance of the valve member with respect to the valve seat, since the cylinder bore for the pump piston and the valve seat on one
  • Manufacturing device can be manufactured and can therefore be aligned very precisely to each other.
  • FIG. 1 shows a high-pressure pump for a fuel injection device of an internal combustion engine in a longitudinal section
  • FIG. 2 shows a section of the high-pressure pump designated by II in FIG Suction valve in the open state
  • Figure 3 shows the detail II with the suction valve in the closed state.
  • the high-pressure pump has a pump housing 10 in which a drive shaft 12 which can be driven in rotation by the internal combustion engine is rotatably mounted, for example via two bearing points spaced apart from one another in the axial direction.
  • the drive shaft 12 has at least one section eccentric to its axis of rotation 13 or a cam 16, wherein the cam 16 can also be designed as a multiple cam.
  • the high-pressure pump has at least one or more pump elements 18 arranged in the pump housing 10, each with a pump piston 20, which is driven by the eccentric section or the cam 16 of the drive shaft 12 in a stroke movement in at least approximately radial direction to the axis of rotation 13 of the drive shaft 12.
  • the pump piston 20 is guided in a tightly displaceable manner in a cylinder bore 22 formed in the pump housing 10 and bounded with its end facing away from the drive shaft 12
  • the pump work space 24 has a connection to a via a fuel feed channel 26 running in the pump housing 10
  • Fuel supply for example a feed pump 14.
  • Pump working chamber 24 has a suction valve 28 opening into pump working chamber 24.
  • the pump work chamber 24 also has a connection via a fuel drain channel 30 running in the pump housing 10 an outlet, which is connected to a high-pressure accumulator 110, for example.
  • One or preferably a plurality of injectors 120 which are arranged on the cylinders of the internal combustion engine, are connected to the high-pressure accumulator 110 and are used to inject fuel into the cylinders of the internal combustion engine.
  • An outlet valve 32 opening out of the pump work chamber 24 is arranged at the mouth of the fuel drain channel 30 into the pump work chamber 24.
  • a support element in the form of a tappet 34 can be arranged between the pump piston 20 and the eccentric section or cam 16 of the drive shaft 12, via which the pump piston 20 is supported at least indirectly on the cam 16.
  • the pump piston 20 is coupled to the tappet 34 in a manner not shown in the direction of its longitudinal axis 21.
  • the tappet 34 can be supported directly on the eccentric section or cam 16.
  • the plunger 34 is slidably mounted in a bore 36 in the pump housing 10 and takes on the implementation of the
  • the suction valve 28 is described in more detail below with reference to FIGS. 2 and 3.
  • the cylinder bore 22 of the pump housing 10 is adjoined by an at least approximately coaxial bore 40 in the pump housing 10 toward the outside of the pump housing 10 facing away from the drive shaft 12, which bore 40 has a smaller diameter than the cylinder bore 22.
  • an annular shoulder is formed, on which a valve seat 42 is formed, the for example, is at least approximately frustoconical.
  • the bore 40 opens into the fuel inlet anal 26.
  • the suction valve 28 has a valve member 44 which is arranged in the pump work chamber 24 and which is connected to the valve seat 42 for controlling the connection of the
  • the valve member 44 is piston-shaped and cup-shaped, the closed end of the valve member 44 facing the valve seat 42.
  • the valve member 44 has, for example, an at least approximately frustoconical sealing surface 45 with which it cooperates with the valve seat 42.
  • the pump piston 20 has in its end region facing the valve seat 42 an at least approximately coaxial to its longitudinal axis 21 blind bore 46, into which the valve member 44 of the suction valve 28 dips with its open end.
  • the valve member 44 is guided over a large part of its longitudinal extent in the blind bore 46 in the pump piston 20 with little radial play.
  • a spring chamber 48 is delimited in the blind bore 46 by the pump piston 20 and the valve member 44, in which a closing spring 50 of the suction valve 28, which is supported on the one hand at the bottom of the blind bore 46 on the pump piston 20 and on the other hand on the valve member 44, is arranged.
  • the closing spring 50 is designed as a helical compression spring and projects into the valve member 44 and is supported in this on an annular shoulder formed by a reduction in the internal cross section of the valve member 44. The valve member 44 is pressed toward the valve seat 42 by the closing spring 50.
  • At least one opening 52 is provided in the valve member 44, through which the spring chamber 48 is connected to the pump working chamber 24.
  • the at least one opening 52 enables the filling and emptying of the Spring chamber 48 during a movement of valve member 44 relative to pump piston 20, the dimensioning of at least one opening 52 being able to influence the volume flow when filling and emptying spring chamber 48.
  • the suction valve 28 is shown in the open state during the suction stroke of the pump piston 20.
  • fuel flows from the fuel inlet channel 26 into the pump work chamber 24.
  • the suction stroke of the pump piston 20 it moves away from the valve seat 42 of the suction valve 28 together with the closing spring 50 supported thereon, so that the pretension of the closing spring 50 is reduced.
  • the suction valve 28 therefore opens even at a small pressure difference between the fuel inlet channel 26 and the pump work chamber 24.
  • valve member 44 is guided in the blind bore 46 with high accuracy coaxially to the valve seat 42, since the cylinder bore 22, in which the pump piston 20 is guided, and the valve seat 42 in same pump housing 10 are formed. As a result, the valve member 44 securely comes into contact with the valve seat 42 when it closes and thus closes reliably.
  • the outlet valve 38 is closed.
  • fuel is compressed by the pump piston 20 in the pump work chamber 24, so that the suction valve 28 closes as a result of the increased pressure in the pump work chamber 24 while fuel is under high pressure is conveyed through the fuel outlet channel 30 to the high-pressure accumulator 110 with the outlet valve 32 open.
  • the suction valve 28 is shown in the closed state during the delivery stroke of the pump piston 20.
  • valve seat 42 is formed on a different part of the pump housing 10 than the cylinder bore 22 in which the pump piston 20 is guided.
  • the part of the pump housing 10 on which the valve seat 42 is formed is aligned very precisely with respect to the part of the pump housing 10 in which the cylinder bore 22 is formed in order to achieve the required coaxial alignment of the valve seat 42 with respect to FIG To reach cylinder bore 22.

Abstract

L'invention concerne une pompe haute pression comprenant au moins un élément pompe (18) pourvu d'un piston de pompe (20) qui est guidé de manière à pouvoir être déplacé dans un orifice cylindrique (22) d'une partie logement de pompe (10), qui est entraîné selon un mouvement de va-et-vient, et qui délimite, dans l'orifice cylindrique (22), une chambre de travail de pompe (24) pouvant être remplie de carburant par l'intermédiaire d'une soupape d'aspiration (28) lors de la course d'aspiration du piston de pompe (20). La soupape d'aspiration (28) comprend un obturateur (44) qui est ouvert dans la chambre de travail de pompe (24), et qui coopère avec un siège de soupape (42). Dans la zone terminale du piston de pompe (20) qui est orientée vers la soupape d'aspiration (28) se trouve un trou borgne (46) dans lequel est inséré l'obturateur (44) de la soupape d'aspiration (28), et dans lequel est disposé un ressort de fermeture (50) qui agit sur l'obturateur (44) et qui repose d'un côté contre le piston de pompe (20) et de l'autre côté contre l'obturateur (44). Cet obturateur (44) est guidé de manière à pouvoir être déplacé dans le trou borgne (44) du piston de pompe (20).
PCT/EP2005/051738 2004-06-16 2005-04-20 Pompe haute pression conçue pour un dispositif d'injection de carburant d'un moteur a combustion interne WO2005124153A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2007515913A JP4589382B2 (ja) 2004-06-16 2005-04-20 内燃機関の燃料噴射装置用の高圧ポンプ
US11/597,917 US20080069712A1 (en) 2004-06-16 2005-04-20 High-Pressure Pump for a Fuel Injection System of an Internal Combustion Engine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004028999.9 2004-06-16
DE102004028999A DE102004028999A1 (de) 2004-06-16 2004-06-16 Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine

Publications (1)

Publication Number Publication Date
WO2005124153A1 true WO2005124153A1 (fr) 2005-12-29

Family

ID=34967479

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2005/051738 WO2005124153A1 (fr) 2004-06-16 2005-04-20 Pompe haute pression conçue pour un dispositif d'injection de carburant d'un moteur a combustion interne

Country Status (4)

Country Link
US (1) US20080069712A1 (fr)
JP (1) JP4589382B2 (fr)
DE (1) DE102004028999A1 (fr)
WO (1) WO2005124153A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009000857A1 (de) 2009-02-13 2010-08-19 Robert Bosch Gmbh Pumpenanordnung
DE102009000835A1 (de) 2009-02-13 2010-08-19 Robert Bosch Gmbh Modulare Niederdruckeinheit und modulare Pumpenanordnung
DE102009000943A1 (de) 2009-02-18 2010-08-19 Robert Bosch Gmbh Einrichtung zur Durchflussmengenbegrenzung an einer Pumpe und Pumpenanordnung mit solch einer Einrichtung
DE102009003057A1 (de) 2009-05-13 2010-11-18 Robert Bosch Gmbh Steckpumpe
DE102010030586A1 (de) 2010-06-28 2011-12-29 Robert Bosch Gmbh Metallisches Bauteil für Hochdruckanwendungen
JP5197722B2 (ja) * 2010-11-26 2013-05-15 日立オートモティブシステムズ株式会社 ウォータポンプ
GB2549746B (en) * 2016-04-27 2020-04-01 Delphi Tech Ip Ltd High pressure fuel pump
GB2555599A (en) * 2016-11-02 2018-05-09 Delphi Int Operations Luxembourg Sarl Fuel pump
CN111794887B (zh) * 2019-04-08 2022-04-12 纬湃汽车电子(长春)有限公司 高压泵
DE112019007911T5 (de) * 2019-11-22 2022-09-08 Eric A. Benham Pumpenkolbenbaugruppe für einen verbesserten Pumpenwirkungsgrad

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DE19848035A1 (de) * 1998-10-17 2000-04-20 Bosch Gmbh Robert Radialkolbenpumpe für Kraftstoffhochdruckerzeugung

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DE19848035A1 (de) * 1998-10-17 2000-04-20 Bosch Gmbh Robert Radialkolbenpumpe für Kraftstoffhochdruckerzeugung

Also Published As

Publication number Publication date
DE102004028999A1 (de) 2006-01-05
JP4589382B2 (ja) 2010-12-01
JP2008502838A (ja) 2008-01-31
US20080069712A1 (en) 2008-03-20

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