EP1642023A1 - Raccordement pour espaces haute pression d'injecteurs de carburant - Google Patents

Raccordement pour espaces haute pression d'injecteurs de carburant

Info

Publication number
EP1642023A1
EP1642023A1 EP04726428A EP04726428A EP1642023A1 EP 1642023 A1 EP1642023 A1 EP 1642023A1 EP 04726428 A EP04726428 A EP 04726428A EP 04726428 A EP04726428 A EP 04726428A EP 1642023 A1 EP1642023 A1 EP 1642023A1
Authority
EP
European Patent Office
Prior art keywords
pressure
bore
connection point
space
point according
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.)
Granted
Application number
EP04726428A
Other languages
German (de)
English (en)
Other versions
EP1642023B1 (fr
Inventor
Heinz Haiser
Dominikus Hofmann
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
Publication of EP1642023A1 publication Critical patent/EP1642023A1/fr
Application granted granted Critical
Publication of EP1642023B1 publication Critical patent/EP1642023B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • F02M57/026—Construction details of pressure amplifiers, e.g. fuel passages or check valves arranged in the intensifier piston or head, particular diameter relationships, stop members, arrangement of ports or conduits
    • 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
    • F02M55/008—Arrangement of fuel passages inside of injectors
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • 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
    • F02M59/105—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 hydraulic drive
    • 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
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/03—Fuel-injection apparatus having means for reducing or avoiding stress, e.g. the stress caused by mechanical force, by fluid pressure or by temperature variations

Definitions

  • Stroke-controlled injection systems with a high-pressure storage space common rail
  • pump-injector systems or pump-line-injector systems are used to introduce fuel into direct-injection internal combustion engines.
  • the injection pressure can advantageously be adapted to the load and speed of an internal combustion engine over a wide range of operating conditions.
  • a high injection pressure is required to reduce emissions and achieve high specific performance.
  • the achievable pressure level of high-pressure fuel pumps is limited for reasons of strength, so that pressure boosters in the fuel injectors are used to further increase the pressure in fuel injection systems.
  • DE 101 23 913 AI relates to a fuel injection device for internal combustion engines with a fuel injector that can be supplied by a high-pressure fuel source. Between the fuel injector and the high-pressure fuel source, a pressure-translation device having a movable pressure-booster piston is connected.
  • the pressure booster piston separates a space that can be connected to the high-pressure fuel source from a high-pressure space that is connected to the fuel injector.
  • the fuel pressure in the high-pressure chamber can be varied by filling a rear chamber (differential pressure chamber) of the pressure booster device with fuel or by emptying the rear chamber of fuel.
  • the fuel injector has a movable closing piston for opening and closing injection openings.
  • the closing piston protrudes into a closing pressure chamber, so that fuel pressure can be applied to the closing piston to achieve a force acting on the closing piston in the closing direction.
  • the closing pressure chamber and the rear chamber are formed by a common closing pressure rear chamber, all partial areas of the closing pressure rear chamber being permanently connected to one another for the exchange of fuel.
  • a pressure chamber is provided to supply the injection openings with fuel and to apply a force acting in the opening direction to the closing piston.
  • a high-pressure chamber is connected to the high-pressure fuel source in such a way that High-pressure space, apart from pressure vibrations, at least the fuel pressure of the high-pressure fuel source can constantly be present, the pressure space and the high-pressure space being formed by a common injection space. All parts of the injection chamber are permanently connected to each other for the exchange of fuel.
  • a pressure-reinforced fuel injection device with an internal control line can be found.
  • the fuel injector which is connected to a high pressure source, has a multi-part injector body. This contains a pressure intensifier that can be actuated via a differential pressure space and whose pressure intensifier piston separates a working space from the differential pressure space.
  • the fuel injection device can be actuated via a switching valve.
  • a pressure change in the differential pressure chamber of the pressure booster takes place via a central control line which extends through the pressure booster piston.
  • the central control line is led through the work area of the pressure intensifier and sealed against it via a high-pressure-tight connection.
  • DE 196 11 884 AI relates to a fuel injection valve for internal combustion engines.
  • This comprises a piston-shaped valve member which is axially displaceable in a bore of a valve body. At its end on the combustion chamber side, this has a valve sealing surface which interacts with a valve seat provided at the end of the bore on the combustion chamber side in order to open an injection cross section. Furthermore, this has a pressure shoulder pointing in the direction of the valve sealing surface, by means of which the valve member is divided into a guide part with a larger diameter slidingly guided in the bore and a free shaft part with a smaller diameter.
  • a pressure chamber formed by a cross-sectional expansion of the bore is provided, which is connected to the valve seat via a gap formed between the free shaft of the valve member and the wall of the bore, and at the end facing away from the valve seat a guide section of the bore receiving the guide part of the valve member followed.
  • the valve body is traversed by a pressure channel which opens radially outward of the bore into the end of the pressure chamber facing away from the valve seat.
  • the pressure shoulder on the valve member constantly dips into the guide section of the bore such that an annular gap remains between the valve member and the wall of the bore at the end of the guide section of the bore adjacent to the pressure chamber. In this, a counterforce is built up on a web remaining between the bore and the pressure channel.
  • the differential pressure chamber is connected to a second valve-carrying bore by a generally horizontal bore.
  • the making of the horizontal hole turns out to be extremely difficult. Time-consuming and costly processes such as electro-chemical lowering or eroding have to be used here.
  • the highest stresses in the component occur at the intersections between the rear space and the horizontal bore. A higher surface quality and a rounding of the edges resulting from the manufacturing process are no longer sufficient with the desired system pressures to be increased in order to obtain durable components.
  • the inner central control line known from DE 102 47 903 AI requires a higher manufacturing and assembly effort than simple bores within the injector body.
  • the connection of the differential pressure chamber to the control line represents a potential weak point. Since the control valve for actuating the pressure booster is arranged above the pressure booster for reasons of installation space, the control line is guided past the pressure booster on the side.
  • the connection between the differential pressure chamber (rear chamber) and the control line which is generally designed as a bore and leads to the valve, is represented by a circumferential groove or a side pocket in the cylindrical rear chamber of the pressure booster.
  • the resultant advantage is that, especially at the high-pressure intersection between the differential pressure space (rear space) and a groove, or between the differential pressure space (rear space) and the cylindrically shaped pocket, there are no excessive stresses that impair the pressure resistance of the fuel injector.
  • the voltage increase can be significantly reduced, so that higher fuel injection pressures can be achieved with a fuel injector of this type with an optimized connection between the high-pressure chambers on the pressure intensifier to let.
  • connection points designed in this way in the high-pressure area between high-pressure rooms of components which are exposed to the highest pressures on the one hand, in the long term, the service life of fuel injectors with pressure boosters can be reduced due to the lower voltage level, and on the other hand, the connection of high-pressure rooms proposed according to the invention is extremely high - Pressure-carrying components can further increase the injection pressure level in fuel injectors.
  • FIG. 1 shows a pressure booster in the non-activated state activated by pressure variations in a differential pressure space
  • FIG. 2 shows the pressure booster according to FIG. 1 in the activated state
  • FIG. 3 shows a pressure amplifier in half section, the differential pressure chamber (rear chamber) of which is connected to a control line designed as a bore by means of a horizontal bore,
  • FIG. 4 shows a connection, configured according to the invention, of a rear space in the body of the pressure booster with a control line designed as a bore, likewise in half section
  • FIG. 5 shows a developed boundary wall of a pressure chamber, in which a cylindrically shaped pocket is formed, which forms a connection with a control line designed as a bore,
  • FIG. 6 shows a developed boundary wall of a high-pressure container, in which a circulation groove, also shown developed, is introduced, which is also connected to a control line designed as a bore, 7, 1 a connection of a differential pressure frame of a pressure booster with a control line designed as a bore,
  • FIG. IX shows a connection, configured according to the invention, of a control line designed as a bore with the differential pressure space (rear space) of a. Pressure booster and
  • FIG. 7.3 shows a connection of a differential pressure chamber (rear chamber) of a pressure booster designed as a circulation hat to a control line designed as a bore.
  • a pressure booster can be seen in a schematic representation, the working space of which is separated from a pressure-releasable or pressurizable ⁇ difference-edigrau ⁇ i via an booster piston.
  • a pressure booster 1 comprises a work space 2 and a pressure-relievable or pressurizable differential pressure space 4. Furthermore, the pressure booster 1 comprises a compression space 5 formed in its body 11.
  • the booster piston 3 separating the differential pressure space 4 (rear space) from the work space 2 comprises a first end face 6 and one the front space 7 delimiting the compression space 5.
  • the working space 2 of the pressure booster 1 is subjected to system pressure (praa) via a high pressure source, not shown in FIG. 1.
  • the system pressure also prevails in the differential pressure chamber 4 ( ⁇ n in the compression chamber 5 of the pressure booster 1, which is shown in FIG. 1 in its deactivated position 8, the system pressure level p ⁇ i also prevails.
  • the pressure booster 1 is accordingly pressure-balanced since it is on the second end face 7 and the annular surface in the differential pressure chamber 4 of the pressure intensifier 1 correspond to the pressing forces acting on the first end surface 6 of the booster piston 3.
  • Fig. 2 shows a pressure booster as shown in Fig. I in its activated state.
  • the booster piston 3 travels into the Kpm- due to the pressure force in the working chamber 2 which acts on its first Stiflofläßbe 6 and which is generated by the system pressure (prai press room 5 a.
  • FIG 3 shows a half section through a body of a pressure booster according to the prior art.
  • the pressure booster 1 comprises a body 11, in which a control line 12 designed as a bore runs.
  • the control line 12 designed as a bore is connected via a horizontal bore 13 to the differential pressure space 4 (rear space) of the pressure booster 1.
  • the horizontal bore 13 represents a critical area with regard to the voltage level that arises during operation of the pressure booster 1.
  • a first intersection point 15 is formed with the control line 12 and the horizontal bore 13, which is provided as a bore, and a second critical intersection 16 between the horizontal bore 13 and the rear space 4 of the pressure booster 1.
  • the compression chamber 5 is shown in a half section through the body 11 of the pressure booster 1 according to the illustration in FIG. 3, from which the inlet 10 branches off at an angle that is set depending on the design of the pressure booster 1 to an injection valve member (not shown in FIG. 3).
  • FIG. 4 shows an embodiment variant according to the invention of a connection between the control line 12 designed as a bore and a differential pressure space (rear space) of a pressure booster.
  • a circumferential groove 18 or a cylindrically shaped pocket 19 can be formed at the lower end of the differential pressure chamber 4 of the pressure booster 1.
  • the differential pressure chamber 4 is delimited at its lower end by an annular surface 20; 4 is shown at the lower end of the body 11 of the pressure booster 1, the compression space 5, of which below an angle of inclination of the inlet 10 branches off to the injection valve member, not shown in FIG. 4.
  • FIG. 5 shows a boundary wall of a high-pressure container with a cylindrically shaped pocket, shown in a stretched position of 180 °.
  • FIG. 5 shows the boundary wall of the differential pressure space 4 (rear space) of a pressure booster in a 180 ° extended position.
  • the tangential stresses in the body 11 of the pressure booster 1 caused by the internal pressure in the differential pressure space 4 (rear space) act in the developed cuboid as shown in FIG. 5 as tensile stresses shown by the two arrows pointing away from each other.
  • the notch effects occurring at the intersection 15 according to FIG. 3 add up along the bores 12 and 13 and there is consequently a significant increase in stress.
  • the connection of the control line 12, which is provided as a bore, to the differential pressure chamber 4 (rear chamber) is designed as a cylindrically shaped pocket 19, which has no notch effect.
  • FIG. 6 shows the connection of a high-pressure chamber to a control line designed as a bore by means of a circulation groove.
  • a circumferential groove 18, likewise shown in a stretched position, is embedded in a developed 21-position wall of a high-pressure chamber, such as a differential pressure chamber 4 of a pressure booster 1.
  • the circumferential groove 18 is free of notch effects, along the bore 12 the notch effect point 23 is formed, which represents the location at which the maximum stresses 24 occur. 6, those in the component, i.e. Tangential stresses occurring in the body 11 in the developed position 21 of the body 11 are shown as tensions.
  • a circumferential groove 18 according to FIG. 6 somewhat weakens the overall cross section of the body 11, but with regard to the mechanical load which arises, the circumferential groove 18 does not act like a notch under tensile load. This avoids an excessive stress at the notch effect point 23, so that only one notch effect point 23 is formed which represents the location 24 at which the maximum stresses occur.
  • a significantly lower stress level is established at the notch effect point 23.
  • connection between the control line 12 designed as a bore and a high-pressure container is designed as a cylindrical pocket 19
  • this embodiment variant of the connection offers the advantage that the cylindrical pocket 19 causes a smaller dead volume in comparison to a circumferential groove 18, i.e. the high-pressure container can be filled with a smaller volume when the connection is designed as a cylindrical pocket 19. If the dead volume can be reduced, for example in the differential pressure space 4 of the pressure booster 1, this advantageously leads to an increase in the efficiency; Furthermore, the hydraulic tuning can be improved and, last but not least, in the case of a pressure booster, smaller discharge quantities have to be moved when the pressure booster is activated.
  • a connection of a differential pressure chamber to a control line designed as a bore can be seen by means of a horizontal bore.
  • the differential pressure space 4 is constructed symmetrically to an axis of symmetry 25.
  • the control line 12 and the differential pressure chamber 4 are connected to one another via the horizontal bore 13, so that the first intersection point 15 results between the horizontal bore 13 and the control line 12, and the second intersection point 16 is represented by the horizontal bore 13 and the differential pressure chamber 4 (rear space) ,
  • the notch effects formed at the intersection point 15 add up, so that a first, very high voltage level ⁇ ma ⁇ , ⁇ occurs during the operation of the pressure booster.
  • the connection of the differential pressure space (rear space) to the control line designed as a bore is formed by a cylindrically shaped pocket.
  • the cylindrically shaped pocket 19 is formed in the lower region of the differential pressure space 4 in the inner wall thereof.
  • the cylindrically shaped pocket 19 forms the connection point between the control line 12 designed as a bore and the differential pressure space 4 (rear space) in the body 11.
  • the control line 12 can be designed both as a blind bore (FIG. 7.1) and as a through bore 12.1. Due to the shape of the connection point as a cylindrically shaped pocket 19, a first bore intersection 17 is produced, which represents the notch effect point 23. In comparison to the illustration according to FIG. 7.1, only a notch effect contribution through the bore intersection 17 is shown. This notch effect point 23 represents the location 24 at which a maximum stress ⁇ maX ⁇ 2 occurs which is considerably below the added maximum stress ⁇ max , ⁇ occurring in FIG. 7.1.
  • the voltage level occurring in its body 11 can be reduced by up to 30% in the operation of a high-pressure container, such as a differential pressure chamber 4 of a pressure booster.
  • the cylindrically shaped pocket 19 is molded in the lower region of the inner wall of the differential pressure space 4 (rear space) in the body 11 and, moreover, offers only a slight increase in the dead volume within the differential pressure space 4.
  • the maximum height of the cylindrically shaped pocket 19 is identified by reference numeral 30; the cylindrically shaped pocket 19 runs symmetrically in a semicircular shape and runs out in outlet areas 31 in the inner wall of the differential pressure space 4 (rear space).
  • the notch effect occurring at the second bore intersection 22 between the cylindrically shaped pocket 19 and the wall of the differential pressure space 4 is negligible compared to the stress increase caused by the notch effect at the first bore intersection 17.
  • Fig. 7.3 shows the cross section of the variant of action, in which the control line designed as a bore is connected to the differential pressure chamber via a circumferential groove in the pressurized body.
  • the first bore intersection 17 marks the transition point of the control line 12 designed as a bore to the circumferential groove 18; a second bore intersection 22 also occurs, which represents the transition region between the differential pressure space 4 (rear space) and the circumferential groove 18.
  • the lower ring surface of the circumferential groove 18 is identified by reference number 20.
  • Further holes 33 can be made in the circumferential groove 18 be connected, one of which is shown in Fig. 7.3.
  • the intersection 17 between the control line 12 designed as a bore and the circumferential groove 18 represents the notch effect point 23, which represents the location 24 of the maximum stress ⁇ maXr 3 . In comparison to the maximum stress ⁇ ma] occurring in the embodiment variant according to FIG. 2 (> 2 , the maximum stress ⁇ maX; 3 occurring in the embodiment variant according to FIG. 7.3 is reduced again.
  • the contour of the circumferential groove 18 and the cylindrically shaped pocket 19 can be arcuate, angular, with rounded corners or in another geometry.
  • connection points between high pressure-carrying spaces and a bore that extends essentially vertically through a body avoid sharp-edged transitions and thereby allow a reduction in the voltage level that occurs.
  • Control line (through hole) 33 further holes

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Braking Systems And Boosters (AREA)

Abstract

L'invention concerne un point de raccordement d'un espace (4) soumis à une pression élevée, dans un corps sollicité par une pression élevée (11) d'un système d'injection haute pression de carburant, à un trou (12) s'étendant à travers le corps (11). Ce trou s'étend sensiblement verticalement à l'intérieur du corps (11). Une poche de configuration cylindrique (19) ou une rainure périphérique (18) est formée dans l'espace (4) soumis à la pression élevée, poche dans laquelle débouche le trou (12) avec formation d'un point d'intersection (17).
EP04726428A 2003-06-27 2004-04-08 Raccordement pour espaces haute pression d'injecteurs de carburant Expired - Lifetime EP1642023B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10329052A DE10329052A1 (de) 2003-06-27 2003-06-27 Verbindung für Hochdruckräume von Kraftstoffinjektoren
PCT/DE2004/000743 WO2005010347A1 (fr) 2003-06-27 2004-04-08 Raccordement pour espaces haute pression d'injecteurs de carburant

Publications (2)

Publication Number Publication Date
EP1642023A1 true EP1642023A1 (fr) 2006-04-05
EP1642023B1 EP1642023B1 (fr) 2007-02-28

Family

ID=33521120

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04726428A Expired - Lifetime EP1642023B1 (fr) 2003-06-27 2004-04-08 Raccordement pour espaces haute pression d'injecteurs de carburant

Country Status (4)

Country Link
US (1) US7717087B2 (fr)
EP (1) EP1642023B1 (fr)
DE (2) DE10329052A1 (fr)
WO (1) WO2005010347A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005095216A1 (fr) 2004-03-26 2005-10-13 Csp Technologies, Inc. Film actif colle a des emballages flexibles et procede associe
DE102006036103A1 (de) * 2006-08-02 2008-02-07 Siemens Ag Kanalanordnung
JP4501983B2 (ja) 2007-09-28 2010-07-14 アイシン・エィ・ダブリュ株式会社 駐車支援システム、駐車支援方法、駐車支援プログラム
DE102008003347A1 (de) * 2008-01-07 2009-07-09 Robert Bosch Gmbh Druckverstärkeranordnung
US10034455B2 (en) 2015-12-17 2018-07-31 Lumo Llc Self-cleaning pet grooming implement

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1179542A (fr) * 1957-07-08 1959-05-26 Perfectionnements apportés à des pompes alternatives autorégulatrices, notamment pour l'injection de combustible dans des moteurs
US4700680A (en) * 1984-05-08 1987-10-20 Teledyne Industries, Inc. Two stage fuel pump
DE19948341A1 (de) 1999-10-07 2001-04-19 Bosch Gmbh Robert Kraftstoffhochdruckspeicher
DE19948339C1 (de) 1999-10-07 2000-12-14 Bosch Gmbh Robert Kraftstoffhochdruckspeicher
DE10022378A1 (de) 2000-05-08 2001-11-22 Bosch Gmbh Robert Hochdruckfester Injektorkörper
DE10146741A1 (de) 2001-09-22 2003-04-17 Bosch Gmbh Robert Kraftstoffhochdruckspeicher
DE10152261A1 (de) 2001-10-20 2003-04-30 Bosch Gmbh Robert Hochdruckspeicher wie Kraftstoffhochdruckspeicher

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2005010347A1 *

Also Published As

Publication number Publication date
DE10329052A1 (de) 2005-01-13
US7717087B2 (en) 2010-05-18
DE502004003063D1 (de) 2007-04-12
US20070095325A1 (en) 2007-05-03
EP1642023B1 (fr) 2007-02-28
WO2005010347A1 (fr) 2005-02-03

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