EP1716332A1 - Pompe haute pression, notamment pour un dispositif d'injection de carburant dans un moteur a combustion interne - Google Patents

Pompe haute pression, notamment pour un dispositif d'injection de carburant dans un moteur a combustion interne

Info

Publication number
EP1716332A1
EP1716332A1 EP05701509A EP05701509A EP1716332A1 EP 1716332 A1 EP1716332 A1 EP 1716332A1 EP 05701509 A EP05701509 A EP 05701509A EP 05701509 A EP05701509 A EP 05701509A EP 1716332 A1 EP1716332 A1 EP 1716332A1
Authority
EP
European Patent Office
Prior art keywords
valve
valve member
lateral surface
section
sealing surface
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Withdrawn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
EP05701509A
Other languages
German (de)
English (en)
Inventor
Nestor Rodriguez-Amaya
Michael Mennicken
Peter Brendle
Falko Bredow
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
Priority claimed from DE102004027825A external-priority patent/DE102004027825A1/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1716332A1 publication Critical patent/EP1716332A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/06—Check valves with guided rigid valve members with guided stems
    • F16K15/063—Check valves with guided rigid valve members with guided stems the valve being loaded by a spring
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • 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
    • F02M59/46—Valves
    • F02M59/462—Delivery 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
    • 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
    • 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
    • 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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/04—Check valves with guided rigid valve members shaped as balls
    • F16K15/044—Check valves with guided rigid valve members shaped as balls spring-loaded
    • 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

Definitions

  • High-pressure pump in particular for a fuel injection device of an internal combustion engine
  • the invention is based on a high-pressure pump, in particular 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 60 672 AI.
  • This high-pressure pump has at least one pump element with a pump piston which is driven in a lifting movement and delimits a pump working space.
  • fuel is drawn in from a fuel inlet via an inlet valve, and during the delivery stroke of the pump piston, fuel is displaced from the pump work space via an outlet valve.
  • the inlet valve has a valve member with a sealing surface inclined to its longitudinal axis, with which it cooperates with a valve seat arranged in a valve housing.
  • the outlet valve has a spherical valve member which interacts with a valve seat arranged in a valve housing.
  • a flow cross-section between the valve member and the valve housing is released by the respective valve member in the open state, when the sealing surface is lifted off the valve seat.
  • the smallest flow cross-section is arranged between the valve member and the valve housing in the area of the sealing surface of the valve member, as a result of which there is a high flow velocity and correspondingly a low static pressure in the area of the sealing area and consequently only a small in Force acting in the opening direction of the valve member.
  • even forces in the closing direction can act on the valve member.
  • the high pressure pump according to the invention with the features according to claim 1 has the advantage that the
  • FIG. 1 shows a high pressure pump for a fuel injection device of an internal combustion engine
  • FIG. 2 shows an inlet valve of the high pressure pump in an enlarged illustration in a longitudinal section
  • FIG. 3 shows a modified embodiment of the inlet valve
  • FIG. 4 shows an outlet valve of the high pressure pump in a longitudinal section.
  • the high-pressure pump 10 for a fuel injection device of an internal combustion engine, which is preferably a self-igniting internal combustion engine.
  • the high-pressure pump 10 delivers fuel under high pressure into a reservoir 12, from which fuel is taken for injection at the internal combustion engine.
  • the high-pressure pump 10 is supplied with fuel by a feed pump 14.
  • the high-pressure pump 10 has at least one pump element 16, which is driven at least indirectly by a drive shaft 18 of the high-pressure pump 10 in a lifting movement Has pump piston 20.
  • the pump piston 20 is tightly guided in a cylinder bore 22 that extends at least approximately radially to the drive shaft 18 and delimits a pump work chamber 24 in the outer end region of the cylinder bore 22 facing away from the drive shaft 18.
  • the drive shaft 18 has a cam or a shaft section 26 that is eccentric to its axis of rotation 19 , via which the stroke movement of the pump piston 20 is effected during the rotary movement of the drive shaft 18.
  • the pump working space 24 is via a opening in the pump working space 24 as
  • Check valve designed inlet valve 30 can be connected to a fuel supply from the feed pump 14.
  • the pump work chamber 24 can also be connected to a fuel outlet to the reservoir 12 via an outlet valve 32 that opens out of the pump work chamber 24 and is designed as a check valve.
  • Inlet valve 30 opened because the feed pump 14 generates a higher pressure than the pressure prevailing in the pump work chamber 24, so that fuel delivered by the feed pump 14 is drawn into the pump work chamber 24.
  • the outlet valve 32 is at the suction stroke of the
  • the inlet valve 30 is described in more detail by way of example with reference to FIG. 2.
  • the inlet valve 30 is inserted, for example, into a bore 34 of a housing part 36 of the high-pressure pump 10 that adjoins the cylinder bore 22 radially outward.
  • the bore 34 is larger in diameter than the cylinder bore 22.
  • the housing part 36 can be, for example, a cylinder head which is connected to a other housing part, in which the drive shaft 18 is mounted, is connected or a housing part in which the drive shaft 18 is also mounted.
  • a fuel feed channel 38 which is connected to the feed pump 14, opens into the bore 34 near its end region facing the cylinder bore 22, for example approximately radially to the axis of the bore 34.
  • the inlet valve 30 has a valve housing 40 in which there is a bore 42 which is stepped several times in diameter.
  • the bore 42 has a section 42a with a small diameter, a section 42b with a larger diameter adjoining the section 42a to the pump work chamber 24, a section 42c adjoining the section 42b to the pump work chamber 24 and a section 42c to the pump work chamber 24 on subsequent section 42d.
  • the inlet valve 30 has a piston-shaped valve member 44, which is displaceably guided with a cylindrical shaft 44a in the bore section 42a.
  • the valve member 44 also has a head 46 adjoining the shaft 44a and enlarged in diameter compared to the shaft 44a, a sealing surface 48 being arranged on the valve member 44 at the transition from the head 46 to the shaft 44a.
  • the sealing surface 48 extends at an angle ⁇ inclined to the longitudinal axis 45 of the valve member 44 in such a way that the sealing surface 48 approaches the longitudinal axis 45 towards the stem 44a.
  • the sealing surface 48 is preferably at least approximately frustoconical.
  • the head 46 of the valve member 44 can be at least approximately cylindrical.
  • the head 46 of the valve member 44 faces the pump working chamber 24.
  • the end 44a of the valve member 44 protrudes from the bore section 42a with its end facing away from the head 46 and a prestressed closing spring 43 engages it.
  • At least one inlet channel 50 is introduced into the valve housing 40 and opens into the bore section 42b.
  • several, for example three, inlet channels 50 are provided which are uniformly distributed over the circumference of the valve housing 40.
  • the bore section 42c is designed such that its diameter widens away from the bore section 42b towards the bore section 42d.
  • the lateral surface of the bore section 42c is preferably frustoconical, but can also be shaped in any other way, for example concave or convex.
  • the lateral surface of the bore section 42c is inclined at an angle ⁇ to the longitudinal axis 45 of the valve member 44.
  • the angle of inclination ⁇ of the lateral surface of the bore section 42c is preferably somewhat larger than the angle ⁇ at which the sealing surface 48 of the valve member 44 is inclined, but can also be somewhat smaller than the angle ⁇ .
  • the bore section 42c forms a valve seat with which the sealing surface 48 of the valve member 44 cooperates. In the closed state, the valve member 44 rests with its sealing surface 48 on the bore section 42c, the sealing surface 48 being in contact with the edge of the bore section 42c facing the bore section 42b due to the difference between the inclination angles ⁇ and ⁇ .
  • the bore section 42d is designed such that its diameter moves away from the bore section 42c
  • the lateral surface of the bore section 42d is preferably frustoconical, but can also be shaped in any other way, for example concave or convex.
  • the lateral surface of the bore section 42d is inclined at an angle ⁇ to the longitudinal axis 45 of the valve member 44.
  • the angle ⁇ , at which the lateral surface of the bore section 42d is inclined to the longitudinal axis 45, is smaller than the angle ⁇ , at which the lateral surface of the bore section 42c
  • Longitudinal axis 45 extends inclined.
  • the undercut 42e preferably has a lateral surface running at least approximately parallel to the longitudinal axis 45.
  • the outer diameter of the head 46 of the valve member 44 is slightly smaller than the diameter of the undercut 42e, so that the edge at the transition from the head 46 to the sealing surface 48 can dip somewhat into the undercut 42e in the closed state. The undercut 42e thus avoids a collision between the head 46 of the valve member 44 and the valve housing 40.
  • Valve housing 40 with the bore sections 42c and 42d, the angles of inclination ⁇ and ⁇ of which are different, is achieved in that in the open state, when the valve member 44 is raised with its sealing surface 48 from the bore section 42c forming the valve seat, the area 52 of the smallest flow cross section between the cylindrical portion of the head 46 of the valve member 44 and the bore portion 42d. In this area 52 of the smallest flow cross section, the highest is when the inlet valve 30 is open
  • the region 52 is thus arranged downstream of the sealing surface 48 of the valve member 44 in the flow direction of the fuel from the inlet channel 50 into the pump work chamber 24.
  • This static pressure acting on the sealing surface 48 of the valve member 44 generates a force acting on the valve member 44 in the opening direction and thus supports the Opening movement of the valve member 44 and the stable arrangement of the valve member 44 in its open state.
  • the inlet valve 30 opens when the force generated in the opening direction on the valve member 44 by the pressure prevailing in the fuel inlet 38, which acts on the part of the sealing surface 48 arranged within the valve seat 42c, is greater than the sum is the force generated by the pressure on the valve member 44 in the pump working space 24 and the force generated by the closing spring 43.
  • the valve member 44 with its sealing surface 48 is lifted off the valve seat 42c, the entire sealing surface 48 is pressurized, the area 52 having the smallest being arranged
  • FIG. 3 shows a modified embodiment of the inlet valve 30, in which the basic structure is the same as in the embodiment according to FIG. 2, but the valve member 44 is modified.
  • the head 46 of the valve member 44 has, toward its end facing the shaft 44a, an area 47 with a reduced diameter compared to the remaining diameter of the head 46.
  • the area 47 of the head 46 of the valve member 44 which has a reduced diameter, is arranged such that, when the valve member 44 is arranged in its closed position, it lies opposite the transition between the first lateral surface 42c and the second lateral surface 42d of the valve housing 40. Due to the reduction in diameter in the area 47, a collision of the head 46 of the Avoided valve member 44 with the valve housing 40.
  • a shoulder is formed on the head 46 of the valve member 44 at its transition to the sealing surface 48.
  • the transition from the area 47 to the remaining part of the head 46 of the valve member 44 with a large diameter can be rounded as shown in FIG.
  • the head 46 of the valve member 44 can be approximately cylindrical as shown in FIG. 2 or approximately frustoconical as shown in FIG. 3, the diameter of the head 46 increasing
  • Exhaust valve 32 is described in more detail below by way of example with reference to FIG. 4.
  • the outlet valve 32 is inserted, for example, into a bore 54 in the housing part 36.
  • a fuel drain channel 56 which is connected to the accumulator 12, opens into the bore 54 approximately radially to its longitudinal axis.
  • the housing part 36 forms a valve housing for the outlet valve 32, alternatively a separate valve housing for the outlet valve 32 inserted into the housing part 36 can also be provided.
  • the bore 54 in the housing part 36 has a multiple stepped diameter and has a small-diameter section 54a opening into the pump working space 24.
  • a further bore portion 54b adjoins the bore portion 54a away from the pump workspace 24, the diameter of which increases away from the pump workspace 24.
  • the bore section 54b is preferably at least approximately frustoconical, but can alternatively also have a concave or convex curved surface.
  • the lateral surface of the bore section 54b extends at an angle ⁇ inclined to the longitudinal axis 55 of the bore 54.
  • a further bore section 54c adjoins the bore section 54b away from the pump working space 24, the latter Diameter increases away from the pump working space 24.
  • the bore section 54c is preferably at least approximately frustoconical, but can alternatively also have a concave or convex curved surface.
  • the outer surface of the bore section 54b is preferably at least approximately frustoconical, but can alternatively also have a concave or convex curved surface.
  • the outer surface of the bore section 54b is preferably at least approximately frustoconical, but can alternatively also have a concave or convex curved surface.
  • Bore section 54c extends at an angle ⁇ inclined to the longitudinal axis 55 of the bore 54, the angle ⁇ being smaller than the angle ⁇ .
  • a further bore portion 54d with a constant diameter can be connected to the bore portion 54c and extends to the outside of the housing part 36.
  • a closure element 58 is inserted, for example screwed, into the bore section 54d from the outside of the housing part 36.
  • the outlet valve 32 has a valve member 60 which is at least approximately spherical.
  • a closing spring 62 can be provided, which is clamped between the valve member 60 and the closure element 58 and through which the valve member 60 is pressed toward the pump working space 24.
  • the valve member 60 cooperates with a sealing surface 64, which is formed by part of its surface, with the bore section 54b, which forms a valve seat for the valve member 60.
  • the valve member 60 is held by the closing spring 62 with its sealing surface 64 in contact with the valve seat 54b.
  • the outlet valve 32 opens because the force generated by the pressure acting on the valve member 60 in the opening direction is greater than the force of the closing spring 62.
  • a flow cross section is released between the sealing surface 64 of the valve member 60 and the valve seat 54b.
  • a region 66 with a released flow cross section is likewise arranged between the circumference of the valve member 60 and the bore section 54c, the flow cross section when the valve is open is smaller in the region 66 than the flow cross section released between the sealing surface 64 and the valve seat 54b. Throttling of the fuel flow when flowing through the opened outlet valve 32 thus takes place in the area 66 with the smallest flow cross-section and not in the area of the sealing surface 64 of the valve member 60. In the area of the sealing surface 64 of the valve member 60 there is therefore a lower flow velocity than in the area 66 of the smallest flow cross-section and therefore a higher static pressure than in area 66.
  • valve member 60 When the outlet valve 32 is opened, when its valve member 60 lifts with its sealing surface 64 from the valve seat 54b, the surface area of the valve member 60 under pressure is increased, since then it is no longer only the surface lying inside the valve seat 54b that is pressurized but the larger surface with the area 66 out. A large compressive force therefore acts on the valve member 60
  • Opening direction that holds the valve member 60 stably in its open state even when a large amount of fuel flows through the exhaust valve 32 at a high flow rate.
  • both the flow cross-section released between its sealing surface 64 and the valve seat 54b and the flow cross-section released in the region 66 increase, the flow cross-section released in the region 66 always being smaller than that between the sealing surface 64 and the valve seat 54b approved flow cross-section.
  • the angle ⁇ at which the valve seat 54b is inclined to the longitudinal axis 55 of the bore 54, can be chosen large, so that the valve seat 54b is relatively flat and thus has a high wear resistance.
  • the outlet valve 32 is designed as described above for FIG. 4, while the inlet valve 30 can be designed as a simple conical seat or ball valve.
  • a valve as described with reference to FIG. 4 as an outlet valve with a spherical valve member can also be used as an inlet valve on a high-pressure pump.
  • a valve as described with reference to FIG. 2 or 3 as an inlet valve with a valve member with a conical sealing surface can also be used as an outlet valve on a high-pressure pump.
  • both the inlet valve 30 and the outlet valve 32 are preferably designed as described above for FIGS. 2 or 3 and 4.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Details Of Reciprocating Pumps (AREA)

Abstract

L'invention concerne une pompe haute pression comprenant au moins un élément de pompe (16) dans lequel, lors de la course d'aspiration d'un piston (20) de pompe, du carburant provenant de la conduite d'alimentation en carburant (50) est aspiré par une soupape d'admission (30), le carburant étant refoulé par une soupape de refoulement (32) lors de la course de refoulement du piston (20) de pompe. La soupape d'admission (30) comporte un élément (44) dont une surface d'étanchéité (48) inclinée vers son axe longitudinal (45) coopère avec un siège de soupape (42c) disposé dans une cage de soupape (40). Cet élément de soupape (44) permet, à l'état ouvert, lorsque la surface d'étanchéité (48) de l'élément de soupape (44) est désolidarisée du siège de soupape (42c), de libérer entre ledit élément de soupape (44) et la cage de soupape (40) une section transversale d'écoulement entre la conduite d'alimentation en carburant (50) et l'espace de travail (24) de la pompe. L'élément de soupape (44) étant ouvert, une zone (52) pourvue de la plus petite section transversale d'écoulement entre l'élément de soupape (44) et la cage de soupape (40), dans le sens du flux s'écoulant de la conduite d'alimentation en carburant (50) vers l'espace de travail (24) de la pompe, est ménagée en aval du flux et de la surface d'étanchéité (48) de l'élément de soupape (44).
EP05701509A 2004-02-11 2005-01-13 Pompe haute pression, notamment pour un dispositif d'injection de carburant dans un moteur a combustion interne Withdrawn EP1716332A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102004006700 2004-02-11
DE102004027825A DE102004027825A1 (de) 2004-02-11 2004-06-08 Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
PCT/EP2005/050126 WO2005078273A1 (fr) 2004-02-11 2005-01-13 Pompe haute pression, notamment pour un dispositif d'injection de carburant dans un moteur a combustion interne

Publications (1)

Publication Number Publication Date
EP1716332A1 true EP1716332A1 (fr) 2006-11-02

Family

ID=34862902

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05701509A Withdrawn EP1716332A1 (fr) 2004-02-11 2005-01-13 Pompe haute pression, notamment pour un dispositif d'injection de carburant dans un moteur a combustion interne

Country Status (4)

Country Link
EP (1) EP1716332A1 (fr)
JP (1) JP2007501913A (fr)
KR (1) KR20060127128A (fr)
WO (1) WO2005078273A1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006242019A (ja) * 2005-03-01 2006-09-14 Jtekt Corp 燃料ポンプ用チェック弁
DE102005061886A1 (de) * 2005-12-23 2007-07-05 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
DE102006017037B4 (de) 2006-04-11 2015-09-17 Continental Automotive Gmbh Radialkolbenpumpe zur Kraftstoffhochdruckversorgung bei einer Brennkraftmaschine
DE102008040083A1 (de) * 2008-07-02 2010-01-07 Robert Bosch Gmbh Hochdruckpumpe
DE102010040617A1 (de) * 2010-09-13 2012-03-15 Robert Bosch Gmbh Ventil, insbesondere einer hydraulischen Kolbenpumpe
JP5491425B2 (ja) * 2011-01-20 2014-05-14 株式会社デンソー 高圧ポンプ
US9027594B2 (en) * 2012-03-30 2015-05-12 Ti Group Automotive Systems, L.L.C. Fuel system valve assembly
DE102013107950A1 (de) * 2012-08-01 2014-02-06 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Ventil
DE102015201520A1 (de) * 2015-01-29 2016-08-04 Robert Bosch Gmbh Verstelleinrichtung und Brennstoffeinspritzanlage mit einer Verstelleinrichtung

Family Cites Families (5)

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Publication number Priority date Publication date Assignee Title
DE3112100A1 (de) * 1981-03-27 1982-10-07 Robert Bosch Gmbh, 7000 Stuttgart "druckventil fuer eine brennstoffeinspritzpumpe"
JPS5973567U (ja) * 1982-11-09 1984-05-18 株式会社ボッシュオートモーティブ　システム 分配型燃料噴射ポンプのオ−バフロ−バルブ
SE465533B (sv) * 1990-02-19 1991-09-23 Saab Automobile Tyst backventil foer pulserande floede
DE19744577A1 (de) * 1997-10-09 1999-04-22 Bosch Gmbh Robert Radialkolbenpumpe zur Kraftstoffhochdruckversorgung
DE19860672A1 (de) 1998-12-29 2000-07-13 Bosch Gmbh Robert Kolbenpumpe zur Kraftstoffhochdruckerzeugung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2005078273A1 *

Also Published As

Publication number Publication date
KR20060127128A (ko) 2006-12-11
JP2007501913A (ja) 2007-02-01
WO2005078273A1 (fr) 2005-08-25

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