EP2006528A1 - Injecteur de carburant doté d'une fonction de clapet anti-retour et de compensation à basse pression - Google Patents

Injecteur de carburant doté d'une fonction de clapet anti-retour et de compensation à basse pression Download PDF

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Publication number
EP2006528A1
EP2006528A1 EP08104180A EP08104180A EP2006528A1 EP 2006528 A1 EP2006528 A1 EP 2006528A1 EP 08104180 A EP08104180 A EP 08104180A EP 08104180 A EP08104180 A EP 08104180A EP 2006528 A1 EP2006528 A1 EP 2006528A1
Authority
EP
European Patent Office
Prior art keywords
fuel injector
valve seat
pressure
sleeve
valve member
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Withdrawn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
EP08104180A
Other languages
German (de)
English (en)
Inventor
Christoph Buehler
Bernd Rosenau
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 EP2006528A1 publication Critical patent/EP2006528A1/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Withdrawn legal-status Critical Current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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • 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
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • fuel injectors for injecting fuel into the combustion chamber of the self-igniting internal combustion engine used.
  • a dependent number of fuel injectors is used.
  • the fuel injectors are hydraulically connected to each other in a piping system within the fuel injection system, such as the high-pressure accumulator injection system (common rail). It has been found that pressure pulsations or pressure waves occurring during actuation of a fuel injector are not without side effects on the further fuel injectors present in the high-pressure accumulator injection system.
  • the other fuel injectors are hydraulically connected to each other via the already mentioned piping within the high-pressure accumulator injection system (common rail).
  • Pressure pulsations propagate after actuation of a fuel injector, for example, within the low-pressure region in to this adjacent fuel injectors.
  • the result is an inadmissibly high mechanical material removal due to the effects of adjusting cavitation erosion, which occurs especially in the region of the valve seat of these fuel injectors.
  • the pressure pulsations or pressure waves retroacting from adjacent fuel injectors on the respective fuel injector can lead to hydraulic forces acting in the opening direction which preclude the closing force of the respectively affected fuel injector, so that the fuel injector opens unintentionally in the extreme case.
  • the object of the present invention is to provide a fuel injector in which pressure waves or pressure pulsations occurring in the high-pressure accumulator injection system are kept away from the valve seat of the fuel injector.
  • a fuel injector which has a particularly needle-shaped injection valve member.
  • the preferably needle-shaped injection valve member is guided in an injector body of the fuel injector, which is located above a disk-shaped throttle plate.
  • the throttle plate In the throttle plate is at least one throttle point, which connects a channel within the injector body with a pressure booster return.
  • the valve seat In the disc-shaped throttle plate, the valve seat is further formed on the upper plan side. The valve seat is opened or closed by a collar on the circumference of the preferably needle-shaped injection valve member. Below the valve seat on the needle-shaped injection valve member forming annular surface, the needle-shaped injection valve member has a diameter taper. As a result, a first hydraulic space is formed in the throttle plate.
  • the first hydraulic space is limited on the one hand by the diameter reduction of the preferably needle-shaped injection valve member and on the other hand by a spring plate which is slidably received in the lower portion of the needle-shaped injection valve member.
  • the spring plate in turn, has a collar on which a spring engages, which in turn acts on the pressure booster part, i. whose top plan side of the pressure intensifier of the inventively proposed fuel injector is supported.
  • the pressure is raised immediately behind the valve seat, without any problems of tightness occurring upon actuation of the preferably needle-shaped injection valve member in the closing direction.
  • the single FIGURE shows a section through the fuel injector in the region of the throttle plate below the injector body and above the pressure booster part of the invention proposed Kraftstoffinj injector.
  • FIG. 1 shows a section through the inventively proposed fuel injector 10, which includes an injector body 12, a throttle plate 14 and a pressure booster body 16, in which a not fully shown here pressure booster is received.
  • the pressure booster body 16 includes a plan side 18.
  • the throttle plate 14 is located further - the return passage 20 upstream - a throttle point 22.
  • the return passage 20 and the throttle point 22 are flowed through from the direction of a pressure booster return region 24 of fuel, after passage the throttle point 22 and merges into the low pressure region of the fuel injector 10 at this subsequent return channel 20.
  • injection needle member 26 which is in particular of a needle-shaped design.
  • the injection valve member 26 has a collar 28.
  • the diameter of the collar 28 is designated by reference numeral 30 (d 1 ).
  • FIG. 1 further states that in the in FIG. 1 shown position a valve seat 32 is closed below the collar 28 on the throttle plate 14. Below the Federal 28 is an annular surface 34, which is a component of the valve seat 32.
  • the taper 36 on the injection valve member 26 merges into a pin 38.
  • a hydraulic chamber 48 is formed, which is limited on the one hand by the lateral surface of the taper 36 on the injection valve member 26 and on the other hand by a hydraulic shield 42, which is preferably designed as a spring plate, reference numeral 42.
  • the injection valve member 26 and the slidably received on the pin 38 hydraulic shield, designed as a spring plate 42 are formed symmetrically to an axis 40 of the injection valve member 26.
  • the axially movable relative to the pin 38 of the needle-shaped injection valve member 26 hydraulic shield 42 is acted upon by a spring element, see position 50.
  • the hydraulic shield 42 comprises a collar 44, which is under attacked by the spring element 50 designed as a spiral spring.
  • the spring element 50 is supported on the flat side 18 of the pressure booster body 16.
  • Reference numeral 58 denotes a stroke, which the hydraulic shield 42, designed as a spring plate, executes with respect to the plane side 18 of the pressure intensifier body 16.
  • the upper plane side of the hydraulic shield 42 is placed in contact with a contact surface 46 by the spring element 50 designed as a spiral spring.
  • the diameter of the abutment surface 46 is denoted by reference numeral 52 (d 2 ).
  • the diameter of the pin 38, on which the hydraulic shield 42, which is preferably designed as a spring plate, is displaceably guided is designated by reference numeral 54 (d 3 ).
  • the outer diameter of the hydraulic shield 42 is designated by reference numeral 56 (diameter d 4 ).
  • the sealing force is generated by surface pressures between the plan sides of the components screwed together injector body 12, throttle plate 14 and pressure booster 16.
  • the sleeve-shaped shield 42 on the pin 38 that occurs at pressure pulsations occurring in the pressure booster return region 24, the sleeve-shaped shield 42 to the system 46 of the throttle plate 14, so that the valve seat 32 as such in the closed state of the Shielded pressure waves remains.
  • the trained as a spring plate hydraulic shield 42 is pressed by the spring element 50 up in abutment against the contact surface 46 on the throttle plate 14. Opens the injection valve member 26, the pressure in the hydraulic chamber 48 increases. The increasing pressure acts on an annular surface, which is defined by the following relation: ⁇ / 4 (d 2 2 - d 3 2 ). If the force acting on the sleeve-shaped shielding 42 is greater than the sealing force exerted by the spring element 50 on the sleeve-shaped shield 42, in particular its collar 44, the sleeve-shaped shield 42 opens and after passing through the stroke 58, a Abberichtquerites free.
  • the pressure in the hydraulic chamber 48 can be adjusted to a relatively high level via a corresponding dimensioning of the spring element 50 and the diameter d 3 or d 2 , so that a non-return valve function can be achieved. Zero crossings, which occur in the pressure curve, can be prevented, so that cavitation erosion is excluded due to collapsing vapor bubbles occurring in suppression and concomitant unacceptably high material stress by this measure. Due to the higher pressure levels that can be maintained in the hydraulic chamber 48, closing problems can be eliminated by inadmissibly high opening forces occurring, since this increased pressure in the hydraulic chamber 48 only on the annular surface 34 corresponding to the diameter differences of the diameter d 1 , see position 30 on the collar 28, minus the diameter of the pin 38, see position 54, acts. As a result, the occurrence of impermissibly high, in the opening direction on the needle-shaped injection valve member 26 acting hydraulic forces is prevented, whereby a low pressure compensation is given.
  • the hydraulic shield 42 designed as a spring plate shields the valve seat 32 against pressure surges, which have their cause in the operation of adjacent, in the high-pressure injection system (common rail) integrated fuel injectors from.
  • the hydraulic shield 42 assumes a check valve function, so that in the closed state of the valve seat 42 due to lack of zero crossings in the pressure curve cavitation erosion in the region of the valve seat 32 can be effectively prevented.
  • the pressure waves occurring in the pressure booster return 24 also do not lead to an unwanted reopening of the injection valve member 26, ie an opening of the valve seat 32, since the pressure waves attack only on the pin diameter 54 (d 3 ), but not on the annular surface 34 below the collar 28 of the Preferably needle-shaped injection valve member 26.
  • the force acting in the opening direction on the injection valve member 26 with the valve seat 32 closed opening force can be significantly reduced, so that accidental opening of the closed valve seat 32 is excluded.
  • the inventively proposed spring-loaded sleeve-shaped shield 42 allows on the one hand a shielding of the closed valve seat 32 against occurring in a pressure booster return area 24 pressure waves and on the other hand, the realization of a low-pressure compensation function by reopening the closed valve seat 32 causing the annular surface 34 below the collar 28 of the injection valve member 26 acting opening forces are limited. Limiting the hydraulic forces acting in the opening direction in turn allows the pressure level in the return area 24 of the fuel injector proposed according to the invention to be increased.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP08104180A 2007-06-19 2008-05-30 Injecteur de carburant doté d'une fonction de clapet anti-retour et de compensation à basse pression Withdrawn EP2006528A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007027973A DE102007027973A1 (de) 2007-06-19 2007-06-19 Kraftstoffinjektor mit Rückschlagventil- und Niederdruckausgleichsfunktion

Publications (1)

Publication Number Publication Date
EP2006528A1 true EP2006528A1 (fr) 2008-12-24

Family

ID=39817142

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08104180A Withdrawn EP2006528A1 (fr) 2007-06-19 2008-05-30 Injecteur de carburant doté d'une fonction de clapet anti-retour et de compensation à basse pression

Country Status (2)

Country Link
EP (1) EP2006528A1 (fr)
DE (1) DE102007027973A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19602288A1 (de) * 1995-02-03 1996-08-08 Zexel Corp Solenoid-Kraftstoffeinspritzventil
DE19854442A1 (de) * 1997-11-25 1999-05-27 Caterpillar Inc Leerlaufstabilisierender Einlaß mit variablem Querschnitt für ein hydraulisch betätigtes Brennstoffeinspritzsystem
US20020139863A1 (en) * 2000-10-11 2002-10-03 Jack Lorraine Compensator assembly having a flexible diaphragm and an internal filling tube for a fuel injector and method
GB2402233A (en) * 2003-05-30 2004-12-01 Ford Global Tech Llc A method for controlling pressure fluctuations in high pressure fuel injector supply lines
DE102006000023A1 (de) * 2005-01-25 2006-07-27 Denso Corp., Kariya Kraftstoffeinspritzung für eine Brennkraftmaschine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19602288A1 (de) * 1995-02-03 1996-08-08 Zexel Corp Solenoid-Kraftstoffeinspritzventil
DE19854442A1 (de) * 1997-11-25 1999-05-27 Caterpillar Inc Leerlaufstabilisierender Einlaß mit variablem Querschnitt für ein hydraulisch betätigtes Brennstoffeinspritzsystem
US20020139863A1 (en) * 2000-10-11 2002-10-03 Jack Lorraine Compensator assembly having a flexible diaphragm and an internal filling tube for a fuel injector and method
GB2402233A (en) * 2003-05-30 2004-12-01 Ford Global Tech Llc A method for controlling pressure fluctuations in high pressure fuel injector supply lines
DE102006000023A1 (de) * 2005-01-25 2006-07-27 Denso Corp., Kariya Kraftstoffeinspritzung für eine Brennkraftmaschine

Also Published As

Publication number Publication date
DE102007027973A1 (de) 2008-12-24

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