EP1640604A1 - Servovalve et soupape d'injection - Google Patents

Servovalve et soupape d'injection Download PDF

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Publication number
EP1640604A1
EP1640604A1 EP05103812A EP05103812A EP1640604A1 EP 1640604 A1 EP1640604 A1 EP 1640604A1 EP 05103812 A EP05103812 A EP 05103812A EP 05103812 A EP05103812 A EP 05103812A EP 1640604 A1 EP1640604 A1 EP 1640604A1
Authority
EP
European Patent Office
Prior art keywords
valve body
valve
recess
closed position
sealing sleeve
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Withdrawn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
EP05103812A
Other languages
German (de)
English (en)
Inventor
Jürgen Dick
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.)
Siemens AG
Original Assignee
Siemens AG
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 Siemens AG filed Critical Siemens AG
Publication of EP1640604A1 publication Critical patent/EP1640604A1/fr
Withdrawn legal-status Critical Current

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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
    • 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
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • 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
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • F02M63/0042—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing combined with valve seats of the lift valve type
    • 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
    • F02M63/0045—Three-way 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
    • F02M63/0012—Valves
    • F02M63/0059—Arrangements of valve actuators
    • F02M63/0061—Single actuator acting on two or more valve bodies
    • 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
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies

Definitions

  • the invention relates to a servo valve and an injection valve which is suitable for metering fluid, in particular fuel.
  • register nozzle injection valves have become known with two injection nozzle circuits and associated first and second nozzle needles, by means of which a stepwise opening or closing of the individual injection nozzle circuits is possible.
  • a valve is known from EP 0 978 649 A2.
  • the valve has a housing in which a designed as a piezo actuator valve drive and a nozzle body are arranged.
  • the nozzle body has a first series of injection holes and axially spaced therefrom a second series of injection holes.
  • a nozzle needle In a recess of the nozzle body a nozzle needle is guided, which in its closed position prevents the flow of fuel through both the first and second series of injection holes and in its open position releases at least the fuel flow through the first series of injection holes.
  • the nozzle needle acts via a driver mechanism on an insert body, which forms an inner nozzle needle.
  • the inner nozzle needle in its closed position, prevents fuel flow through the second series of injection holes and, in the other positions, releases fuel flow through the second series of injection holes.
  • the piezo actuator acts on the nozzle needle via a servo valve.
  • the servo valve includes a drain hole, a valve stem, a closing member, a control chamber and a leakage space. By a correspondingly controlled expansion of the piezo actuator, the closing member is pushed away from its sealing seat via the closing rod. This has the consequence that fuel flows out of the control chamber.
  • the nozzle needle opens or moves from its closed position to its open position.
  • the object of the invention is to provide an injection valve which is simple and can be easily controlled.
  • the invention is characterized according to a first aspect by a servo valve with a valve housing, in which a recess is formed.
  • the valve housing (insert above) can be formed in one piece or even several pieces. It may in particular be formed by a valve plate and possibly an intermediate plate.
  • the servo valve has a first valve body which is arranged in the recess of the valve housing, extends into a recess of a second valve body and which has a closing body.
  • the closing body In a closed position of the first valve body, the closing body bears sealingly against a first seating area, which is formed in the wall of the recess of the valve housing. Outside the closed position, the closing body releases a region between the first seating area and the closing body of the first valve body.
  • the first valve body is designed so that fluid through the recess of the second valve body out can flow to the area of the first seating area.
  • the servo valve comprises a second valve body, which is arranged in the recess of the valve housing and which has a closing body, which bears in a closed position of the second valve body sealingly against a second seat portion, which is formed in the wall of the recess of the valve housing, and the outside the closed position releases an area between the second seating area and the closing body.
  • a sealing sleeve is provided, which is designed and arranged so that it is in the closed position of the second valve body, a free space which is enclosed by it and which is hydraulically coupled to the recess of the second valve body, of a region of the recess of the valve housing outside its radial circumference hydraulically decoupled.
  • the servo valve according to the invention has the advantage that a seat diameter of the second closing body can be selected substantially independently of the seat diameter of the closing body of the first valve body.
  • the respective seat diameter is to be understood as the diameter of the respective closing body at the location at which the respective closing body in the closed position of the respective valve body contacts the respective seating area of the valve body.
  • the force that is necessary to move the respective valve body from its closed position depends on the seat diameter of the closing body of the respective valve body.
  • Another advantage of the servo valve according to the invention is that the first and second seating areas can easily have a high rigidity.
  • the sealing sleeve is guided in the recess of the valve housing and the second valve body is guided in the sealing sleeve. In this way, the second valve body can be made compact.
  • the first valve body is guided in the recess of the second valve body.
  • these respective guides may be formed axially overlapping and so a particularly compact design of the servo valve can be achieved.
  • a spring which is supported on the one hand on a collar of the second valve body and on the other hand on a bearing surface of the sealing sleeve and on the one hand exerts a force on the second valve body in the direction of its closed position and on the other hand exerts a force on the sealing sleeve , which is directed towards a sealing edge of the sealing sleeve.
  • the spring thus advantageously has a dual function.
  • the servo valve of the first and the second valve body are formed and arranged to each other that the second valve body is movable out of its closed position by means of the first valve body.
  • the servo valve can be made particularly simple and it must be assigned to him only one actuator.
  • the first valve body has a collar, which is spaced in the closed position of the first valve body with a predetermined clearance to a contact surface of the second valve body.
  • the first valve body can thus be brought out of its closed position, particularly independently of the second valve body, and the second valve body can also be moved out of its closed position by means of a single actuator, which can be provided when the first valve body is outside the closed position to act on the first valve body.
  • a further spring is provided, which is supported on the one hand on a spring plate of the first valve body and on the other hand on a Federauflage Scheme the sealing sleeve and on the one hand to the second valve body exerts a force in the direction of its closed position and on the other hand on the sealing sleeve a Force exerts, which is directed towards a sealing edge of the sealing sleeve.
  • the other spring has a double function.
  • the spring plate can also not be formed integrally with the first valve body. However, it is mechanically coupled to the first valve body.
  • the first valve body has a pin which extends into the recess of the second valve body and which is provided along its circumference with at least one recess is.
  • a pin which extends into the recess of the second valve body and which is provided along its circumference with at least one recess is.
  • the invention is characterized by an injection valve having a body which has a recess, an outer nozzle needle which is arranged in the first recess, which has a recess and which in a closed position prevents fluid flow through a first injection hole and this otherwise free.
  • the injection valve further has an inner nozzle needle, which is arranged in the recess of the outer nozzle needle and which prevents a fluid flow through a second injection hole in a closed position and otherwise releases it.
  • the injection valve includes the servo valve.
  • the servo valve, the body and the inner and outer nozzle needle are formed so that the position of the inner nozzle needle is adjustable depending on the position of the first valve body and that the position of the outer valve needle is adjustable depending on the position of the second valve body.
  • An injection valve has an injector housing 1.
  • an actuator is arranged, which is preferably a piezoelectric actuator 4.
  • the drive may also be any other suitable actuator, such as an electromagnetic actuator.
  • a leakage chamber 14 is formed in the injector housing 1.
  • a nozzle assembly of the injector includes a valve plate 16, an intermediate plate 18, a needle guide body 20 and a nozzle body 22.
  • the nozzle assembly is mechanically coupled to the injector housing 1 by means of a nozzle lock nut 23.
  • a body may include the nozzle assembly, portions of the nozzle assembly, and / or the injector housing 1 and / or the nozzle retaining nut 23.
  • the needle guide body 20 has a recess 24, which continues axially in a recess 26 of the nozzle body 22.
  • An outer nozzle needle 27 is in the recess 24 of the needle guide body 20 and the recess 26 of the nozzle body 22 is arranged.
  • the outer nozzle needle 27 has a recess 28 penetrating it in the axial direction, in which an inner nozzle needle 29 is arranged.
  • the inner and outer nozzle needle 27, 29 are preferably arranged coaxially with each other.
  • a first nozzle spring 30 is provided, which exerts a force on the outer nozzle needle 27 in a closing direction of the outer nozzle needle 27 and thus without the presence of further forces, the outer nozzle needle 27 presses in a closed position in which they fluid flow through a first injection hole 34 prevents. If the outer nozzle needle is outside its closed position, it releases the flow of fluid through the first injection hole 34.
  • a second nozzle spring 32 ( Figure 2) is provided, which exerts a force on the inner nozzle needle 29 in a closing direction of the inner nozzle needle 29 and thus without the presence of further forces, the inner nozzle needle 29 presses in a closed position in which they fluid flow prevented by a second injection hole 36. If the inner nozzle needle is outside its closed position, it releases the fluid flow through the second injection hole 36.
  • the second nozzle spring is arranged in the recess 28 of the outer nozzle needle 27. Further, there is a sleeve 40 which is pressed by the second nozzle spring 32 against the intermediate plate 18. The sleeve 40 thus separates a first control chamber 48, which adjoins the contact surface 46 of the inner nozzle needle 29, by a second control chamber 50 which adjoins a contact surface 54 of the outer nozzle needle 27 and a recess 24 of the intermediate plate 18.
  • the position of the inner nozzle needle 29 is determined by a force balance from the force acting on the inner nozzle needle 29 by the second nozzle spring 32, the force acting on the inner nozzle needle 29 via the contact surface 46 by the pressure in the first control chamber 48 and a force, caused by the pressure of the fluid via a high-pressure paragraph 52 of the inner nozzle needle 29 acts against this against the closing direction.
  • the position of the outer nozzle needle 27 depends on the balance of forces of the force which is caused by the first nozzle spring 30, the pressure prevailing in the second control chamber 50, which couples a force via the contact surface 54 of the outer nozzle needle 27, the closing on the outer Nozzle needle 27 acts, and a force which acts by the fluid pressure in a region of a high pressure paragraph 56 of the outer nozzle needle opposite to the closing direction of the outer nozzle needle 27.
  • the respective free volume in the area of the high-pressure units 56, 52 is in each case hydraulically coupled to a high-pressure bore 58 of the injection valve.
  • a servovalve comprises a valve housing which, depending on the embodiment, comprises the valve plate and optionally the intermediate plate 18.
  • the valve housing may alternatively be formed in one piece or more than two pieces.
  • a recess 62 is formed in the valve plate 16.
  • a first valve body 64 (FIG. 3) is arranged in the recess 62 of the valve plate 16. It has a closing body 68, which bears in a closed position of the first valve body 64 in a sealing manner against a first seating area 66 which is formed in the wall of the recess 62 of the valve plate 16, and which outside the closed position forms a region between the first seating area 66 and the closing body 68 of the first valve body 64 releases.
  • a second valve body 70 is arranged, which has a closing body 74 which rests in a closed position of the second valve body 70 at a second seat portion 72 of the valve plate 16. Outside the closed position of the second valve body 70, the closing body 68 of the second valve body 70 releases a region between the second seating area 72 and the closing body 74 of the second valve body 70.
  • Both the closing body 74 of the second valve body 70 and the closing body 68 of the first valve body 64 may be conical or spherical.
  • a spherical shape has the advantage that an axial guidance of the respective valve body in the axial direction can be shorter than in the case of the conical design of the respective closing body 68, 74.
  • the second valve body 70 has a recess 76 which completely penetrates the second valve body 70.
  • the first valve body 64 has a pin 78 which extends into the recess 76 of the second valve body 70 inside.
  • the first valve body 64 has a spring plate 80, on which a first spring 82 is supported.
  • the first spring 82 is supported on the intermediate plate 18 and thus exerts a force in the direction of the closed position of the first valve body 64, caused by a corresponding pretensioning of the first spring 82.
  • the first valve body 64 further has a contact region 64, on which the piezo actuator 4 can act, either directly or via a transformer.
  • the first valve body 64 further comprises a collar 86, which in the closed position of the first valve body 64 with a predetermined clearance, so a predetermined distance, is arranged to a contact surface 88 of the second valve body 70.
  • the collar 86 is in contact with the contact surface 88 of the second valve body, the second valve body 70 is mechanically coupled to the piezo actuator 4 via the first valve body 64 and thus can change its axial position controlled by the piezo actuator 4.
  • the pin 78 has a recess 90, which is preferably chord-shaped.
  • the pin 78 has a cylindrical basic shape.
  • the recesses are preferably milled. This can be made very easily in terms of production, if the at least one recess 90 distributed around the circumference of the pin 78 has a chordal form. However, it may have any shape deviating from a chord, for example sector-shaped or of any curved shape.
  • the pin 78 may also be penetrated by at least one bore. Through the bore or the at least one recess 90 it is ensured that fluid can flow through the recess 76 of the second valve body 70.
  • the pin 78 and thus the first valve body 64 is guided in the recess 76 of the second valve body.
  • the first valve body 64 may also be guided in the region of its collar 86 in the recess 62 of the valve plate 16.
  • a recess 92 is formed in the collar 86 such that even in the case of a concern of the collar 86 on the contact surface 88 of the second valve body 70 fluid can pass through the recess 76 of the second valve body 70 in the free space between the at least one recess 90 of the pin 78 and the wall of the recess 76 of the second valve body and further through the recess 92 radially outward.
  • the cutout of the shape shown in FIG. 3 can be produced in a particularly simple manner by a milling operation together with the recess 90.
  • a groove 94 is further provided, which connects directly to the collar 86 in the pin 78. Through the groove 94 can be easily ensured that in the case of the concern of the Federation on the contact surface 88 is a good contact between the collar and the contact surface.
  • the second valve body 70 has a collar 96 on which a second spring 98 is supported with its one free axial end.
  • the second spring 98 is supported with its other free axial end on a support surface 100 of a sealing sleeve 102.
  • the support surface 100 is preferably formed as a paragraph.
  • the suitably biased second spring 98 thus exerts a force on the second valve body 70 in the direction of its closed position.
  • it exerts on the sealing sleeve 102 a force which is directed in the direction of a sealing edge 104 of the sealing sleeve and thus presses the sealing sleeve onto the intermediate plate 18.
  • the second valve body 70 protrudes into the sealing sleeve 102 and is preferably also guided in the sealing sleeve 102. Alternatively, the second valve body 70 may also be guided in the region of its collar 96 in the recess 62 of the valve plate 16.
  • a free space within the sealing sleeve 102 is hydraulically coupled via a first channel 112 and an outlet throttle 108 with the first control chamber 48.
  • the first control chamber 48 is hydraulically coupled via a first inlet throttle 106 with the high-pressure bore 58.
  • a free space radially outside the sealing sleeve 102 is hydraulically coupled by means of a second channel 114 with the second control chamber 50.
  • the second control chamber 50 is hydraulically coupled via a second inlet throttle 110 with the high-pressure bore 58.
  • the operation of the servo valve is described below, starting from a state in which both the first and the second valve body 64, 70 are in their respective closed position. If now transmitted via the actuator, so the piezoelectric actuator 4, an increasing force in the downward direction in the image plane, the first valve body 64 moves out of its closed position, when caused by the spring force and the hydraulic pressure forces on the first valve body are less than the force applied by the piezo actuator force. If now the first valve body 64 moves out of its closed position, an area between the first seat area 66 and the closing body 68 of the first valve body 64 is released.
  • the clearance between the collar 86 and the contact surface 88 of the second valve body is then used up, until finally the collar 86 bears against the contact surface 88 and thus the further stroke of the piezo actuator 4 on the second valve body 70th transfers.
  • the second valve body 70 is also moved out of its closed position and an area between the closing body 74 of the second valve body and the second seating area 72 is released.
  • the force is reduced, which is coupled by the pressure of the fluid in the second control chamber 50 via the contact surface 54 of the outer nozzle needle 27 to this in its closing direction. This ultimately leads to a movement of the outer nozzle needle 27 out of its closed position. If the stroke of the piezoelectric actuator 4 is subsequently reduced again, then the second valve body 70 moves back into its closed position. It can then no longer drain fluid from the second control chamber into the leakage chamber 14 and through the second inlet throttle 110 flowing fluid, the pressure in the second control chamber 50 increases again, which eventually leads to a moving back of the outer nozzle needle 27 in its closed position.
  • the seat diameter of the closing body 74 of the second valve body 70 is chosen as small as possible, taking into account the required properties of the servo valve, for example, its mechanical strength and its resistance to high compressive stresses.
  • the smaller the valve seat diameter of the closing body 74 of the second valve body 70 the lower the peak forces to be applied by the piezo actuator 4 for sequentially connecting both the first valve body 64 and the second valve body 70 sequentially from their respective closed positions bring.
  • the piezo actuator 4 For the removal of the second valve body 70 from its closed position by the piezo actuator 4, it is also necessary to apply an optionally very high force caused by the fluid, which is located in the free space inside the sealing sleeve 102. This force must be taken into account in the design of the piezo actuator 4 and can thus be reduced by suitably small dimensioning of the seat diameter of the closing body 74 of the second valve body 70.
  • the sealing sleeve 102 has a spring support region 116, on which the first spring 82 is supported.
  • the first spring 82 presses the sealing sleeve 102 onto the intermediate plate 18 with suitable pretensioning of the first spring 82 and, at the same time as in the first exemplary embodiment, exerts a force directed in the direction of the closed position on the first valve body 64.
  • the second spring 98 can also be supported, for example, on the intermediate plate 18 and thus can then account for the bearing surface 100 of the sealing sleeve, but this need not necessarily be the case.
  • the servo valve may also be arranged in a device other than the injection valve or be provided for the local arrangement.
EP05103812A 2004-09-23 2005-05-09 Servovalve et soupape d'injection Withdrawn EP1640604A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200410046191 DE102004046191B3 (de) 2004-09-23 2004-09-23 Servoventil und Einspritzventil

Publications (1)

Publication Number Publication Date
EP1640604A1 true EP1640604A1 (fr) 2006-03-29

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP05103812A Withdrawn EP1640604A1 (fr) 2004-09-23 2005-05-09 Servovalve et soupape d'injection

Country Status (2)

Country Link
EP (1) EP1640604A1 (fr)
DE (1) DE102004046191B3 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2275666A1 (fr) * 2009-07-07 2011-01-19 Robert Bosch GmbH Injecteur de carburant doté d'une soupape de distribution à pression compensée
EP2287460A1 (fr) * 2009-07-07 2011-02-23 Robert Bosch GmbH Injecteur de carburant pour un moteur à combustion interne
WO2013000635A1 (fr) * 2011-06-30 2013-01-03 Robert Bosch Gmbh Injecteur de carburant
EP2813698A1 (fr) * 2013-06-10 2014-12-17 Robert Bosch Gmbh Soupape d'injection de combustible
WO2016059069A1 (fr) * 2014-10-15 2016-04-21 Continental Automotive Gmbh Injecteur piezo à rampe commune à compensation de jeu hydraulique intégré dans la servosoupape
DE102009000170B4 (de) * 2009-01-13 2017-11-30 Robert Bosch Gmbh Kraftstoffinjektor
CN109958564A (zh) * 2017-12-26 2019-07-02 天津大学（青岛）海洋工程研究院有限公司 一种用于柴油机共轨式电控喷油器的电磁阀

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0949415A2 (fr) * 1998-04-11 1999-10-13 Robert Bosch Gmbh Dispositif d'injection de combustible pour moteurs à combustion interne
EP0978649A2 (fr) 1998-08-06 2000-02-09 Siemens Aktiengesellschaft Buse d'injection de combustible
EP1081372A2 (fr) * 1999-08-31 2001-03-07 Denso Corporation Dispositif d'injection de carburant
EP1338788A1 (fr) * 1999-04-01 2003-08-27 Delphi Technologies, Inc. Injecteur de carburant

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9914646D0 (en) * 1999-06-24 1999-08-25 Lucas Ind Plc Fuel injector
JP3865222B2 (ja) * 2002-03-05 2007-01-10 株式会社デンソー 燃料噴射装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0949415A2 (fr) * 1998-04-11 1999-10-13 Robert Bosch Gmbh Dispositif d'injection de combustible pour moteurs à combustion interne
EP0978649A2 (fr) 1998-08-06 2000-02-09 Siemens Aktiengesellschaft Buse d'injection de combustible
EP1338788A1 (fr) * 1999-04-01 2003-08-27 Delphi Technologies, Inc. Injecteur de carburant
EP1081372A2 (fr) * 1999-08-31 2001-03-07 Denso Corporation Dispositif d'injection de carburant

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009000170B4 (de) * 2009-01-13 2017-11-30 Robert Bosch Gmbh Kraftstoffinjektor
EP2275666A1 (fr) * 2009-07-07 2011-01-19 Robert Bosch GmbH Injecteur de carburant doté d'une soupape de distribution à pression compensée
EP2287460A1 (fr) * 2009-07-07 2011-02-23 Robert Bosch GmbH Injecteur de carburant pour un moteur à combustion interne
CN103635686B (zh) * 2011-06-30 2016-08-24 罗伯特·博世有限公司 燃料喷射器
CN103635686A (zh) * 2011-06-30 2014-03-12 罗伯特·博世有限公司 燃料喷射器
WO2013000635A1 (fr) * 2011-06-30 2013-01-03 Robert Bosch Gmbh Injecteur de carburant
EP2813698A1 (fr) * 2013-06-10 2014-12-17 Robert Bosch Gmbh Soupape d'injection de combustible
WO2016059069A1 (fr) * 2014-10-15 2016-04-21 Continental Automotive Gmbh Injecteur piezo à rampe commune à compensation de jeu hydraulique intégré dans la servosoupape
CN106795851A (zh) * 2014-10-15 2017-05-31 大陆汽车有限公司 具有集成到伺服阀中的液压的间隙补偿件的压电共轨喷射器
US10233885B2 (en) 2014-10-15 2019-03-19 Continental Automotive Gmbh Piezo common rail injector with hydraulic clearance compensation integrated into the servo valve
CN106795851B (zh) * 2014-10-15 2019-06-18 大陆汽车有限公司 具有集成到伺服阀中的液压的间隙补偿件的压电共轨喷射器
CN109958564A (zh) * 2017-12-26 2019-07-02 天津大学（青岛）海洋工程研究院有限公司 一种用于柴油机共轨式电控喷油器的电磁阀
CN109958564B (zh) * 2017-12-26 2023-09-29 天津大学（青岛）海洋工程研究院有限公司 一种用于柴油机共轨式电控喷油器的电磁阀

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