EP2085606A1 - Plaque intermédiaire pour un injecteur de carburant et injecteur de carburant - Google Patents

Plaque intermédiaire pour un injecteur de carburant et injecteur de carburant Download PDF

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Publication number
EP2085606A1
EP2085606A1 EP09100003A EP09100003A EP2085606A1 EP 2085606 A1 EP2085606 A1 EP 2085606A1 EP 09100003 A EP09100003 A EP 09100003A EP 09100003 A EP09100003 A EP 09100003A EP 2085606 A1 EP2085606 A1 EP 2085606A1
Authority
EP
European Patent Office
Prior art keywords
intermediate plate
injector
recesses
pressure
face
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Withdrawn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
EP09100003A
Other languages
German (de)
English (en)
Inventor
Dietmar Uhlmann
Jens-Peter Nagel
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 EP2085606A1 publication Critical patent/EP2085606A1/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Withdrawn legal-status Critical Current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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • 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
    • F02M55/004—Joints; Sealings
    • F02M55/005—Joints; Sealings for high pressure conduits, e.g. connected to pump outlet or to injector inlet
    • 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
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/001—Control chambers formed by movable sleeves

Definitions

  • the invention relates to an intermediate plate for a fuel injector according to the preamble of claim 1 and a fuel injector with intermediate plate according to the preamble of claim 8.
  • a fuel injector which has a designed as a throttle plate intermediate plate, at the end faces in each case a high-pressure body rests directly sealingly.
  • at least one high pressure element is provided with a frontal biting edge, with which it rests directly on the intermediate plate for producing a high-pressure-tight connection.
  • a disadvantage of the known injector is that the intermediate plate bends due to the different diameters of the contact surfaces for the high-pressure body in the clamped state. This can lead to leaks.
  • the invention has for its object to provide an injector, are minimized in the deflection effects in the clamped state.
  • optimized high-pressure-tight connections to injector bodies should be able to be produced with the aid of the intermediate plate.
  • the object is to propose a fuel injector with optimized sealing conditions in the region of the intermediate plate.
  • the invention is based on the idea to provide a plurality of circumferentially spaced recesses in the edge region of at least one of the two end faces of the intermediate plate. Preference is given to an embodiment of the intermediate plate, in which a plurality of circumferentially spaced recesses are provided in the edge region of both end faces.
  • Recesses in the sense of the invention are preferably surface exposures which are open outward in the radial direction, preferably with a depth extension of approximately 0.1 mm to 3 mm, preferably of 0.1mm to 2mm, more preferably from 0.1mm to 1mm, more preferably from 0.1mm to 0.5mm, most preferably from about 0.3mm.
  • the recesses reduce the total surface area of the associated face and thereby increase the average, global surface pressure, resulting in optimized sealing conditions.
  • the recesses for producing a sealed connection are advantageously arranged radially outside the first or second abutment surface for the injector body which can be applied to the intermediate plate on the end face.
  • the bottom surfaces of the recesses are arranged in a common plane which runs parallel to the adjacent, preferably flat, end face.
  • a deflection of the intermediate plate is minimized by distortion between two Injektor stresses even for the preferred case that the contact surfaces (preferably investment lines) for the injector different Have (inner) diameter. Due to the reduction of deflection, the material stress of the intermediate plate is minimized and optimizes the sealing conditions between the intermediate plate and the applicable injector bodies.
  • the recesses (surface exposures) are arranged on the intermediate plate such that in each case a radial web (support region) is formed between each two circumferentially adjacent recesses.
  • the circumferentially spaced, preferably evenly distributed, radial webs in total prevent excessive, unwanted bending, d. H. an unwanted pre-deformation of the intermediate plate in the clamped state.
  • the edges are provided on both end faces recesses.
  • the recesses of the two end faces are located at the same circumferential positions.
  • each recess in the region of the first end face is associated with a recess in the region of the second end face.
  • the recess centers of the recesses adjacent in the axial direction are preferably located directly above one another.
  • Such an arrangement of the two-sided recesses ensures that the radial webs (support regions) formed between two circumferentially adjacent recesses are likewise arranged directly above one another, whereby the deflection tendency of the intermediate plate is further reduced.
  • the recesses provided in the region of the second end wall facing the combustion chamber have a larger surface area than the recesses provided in the region of the first end side facing an accumulator.
  • the intermediate plate preferably has at least one high-pressure bore. It is particularly advantageous that the at least one high-pressure bore obliquely, i. to be arranged at an angle to the longitudinal center axis of the intermediate plate. With regard to a symmetrical load, an embodiment in which a plurality, preferably nine, high-pressure bores distributed uniformly in the circumferential direction are provided is particularly preferred.
  • the intermediate plate in which at least one throttle bore is provided in the intermediate plate.
  • this at least one throttle bore connects two mutually separated by the intermediate plate pressure booster chambers together.
  • Such a trained intermediate plate is particularly suitable for an injector with a directly via a piezoelectric actuator controlled, on or multi-part, nozzle needle, wherein between the piezoelectric actuator and the nozzle needle, a pressure booster is arranged.
  • the throttle bore is arranged centrally, or at a radius which is smaller than the radius on which the at least one high-pressure bore is arranged.
  • the invention also leads to a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine, in particular a common rail fuel injector.
  • a fuel injector according to the invention comprises at least one intermediate plate designed according to the concept of the invention, on whose front sides in each case an injector body, preferably in each case a high-pressure body, bears.
  • the injector body against the intermediate plate in particular by means of a clamping sleeve (nozzle retaining nut), clamped to realize sufficient contact forces of the injector body on the intermediate plate and thus sufficient sealing conditions.
  • the fuel injector is preferably a fuel injector with a piezoelectric actuator (piezoelectric actuator), which preferably acts directly on a nozzle needle of the fuel injector via a pressure booster.
  • the intermediate plate preferably designed as a throttle plate, separates two pressure booster chambers of the pressure booster from one another and connects them via at least one throttle bore.
  • the first injector body and / or the second injector body abut / bear against the associated end face or the associated contact surface of the intermediate plate, in each case with a biting edge.
  • the sealing conditions can be further optimized.
  • the biting edges have an inner biting edge angle of less than 90 °.
  • the B sulfurkanten both injector bodies are not formed by the (flat) end face of a step, but by a frontal angular edge of preferably adjacent in the radial direction, conical grinding.
  • the (inner) diameter of the two B biskanten and thus the diameter of the two contact surfaces are different in size.
  • the diameter of the second biting edge, and thus of the second contact surface is smaller than the diameter of the first biting edge or first contact surface.
  • the first (upper) injector body is formed as a spacer tube, radially within which a piezoelectric actuator is arranged.
  • the piezoactuator preferably acts on a booster piston, which seals a pressure booster space adjoining the intermediate plate in the axial direction (upwards).
  • a nozzle body is arranged on the second, remote from the spacer tube, end face of the intermediate plate, in which a nozzle needle is arranged axially adjustable.
  • the nozzle needle or an operatively connected thereto, preferably integrally formed therewith, the booster piston defines a arranged on the second end face of the intermediate plate booster piston chamber in the axial direction (down).
  • the nozzle needle is preferably directly controlled by the piezoelectric actuator.
  • Fig. 1a is a detail of a designed as a common rail injector fuel injector 1 shown.
  • the fuel injector 1 comprises a first injector body 2 designed as a spacer tube (first high-pressure body) and a second injector body 3 (second high-pressure body) designed as a nozzle body, and an intermediate plate 4 arranged axially between the injector bodies 2, 3 and designed as a throttle plate.
  • the two injector bodies 2 , 3 are braced against the intermediate plate 4 by means of a nozzle lock nut 5, which is penetrated in the axial direction of the second injector body 3 and bolted to the first injector body 2.
  • the first injector 2 limits a first high-pressure chamber 6 radially outward, which is connected via a high-pressure inlet, not shown, with a high-pressure fuel storage (also not shown) (rail).
  • the high-pressure fuel storage is supplied via a high-pressure pump with fuel, wherein in the high-pressure fuel storage fuel at high pressure of more than 2000 bar is cached.
  • the first high pressure chamber 6 is over several, uniformly distributed in the circumferential direction, provided in the intermediate plate 4, obliquely running high pressure bores 7 in hydraulic communication with a second, designed as a nozzle chamber high-pressure chamber. 8
  • a piezoelectric actuator 9 Centrally within the first high pressure chamber 6 is a piezoelectric actuator 9, comprising a number of stacked piezoelectric crystals.
  • the piezoelectric actuator 9 is operatively connected to a first booster piston 10, which seals a first pressure booster chamber 11 of a hydraulic pressure booster 12 in the axial direction upwards.
  • Radially outside the first pressure booster chamber 11 is sealed by a first sleeve 13, which is supported on a first end face 14 of the intermediate plate 4.
  • a first compression spring 15 acts on the first sleeve 13 in the axial direction on the first end face 14 with a spring force.
  • a second pressure booster chamber 17 is radially disposed within the second high-pressure chamber 8, which is bounded radially outwardly by a second sleeve 18, which by means of a second compression spring 19th Federkraftbeetzschlagt against the second end face 16.
  • the inner diameter of the second pressure booster chamber 17 is smaller than the inner diameter of the first pressure booster chamber 11.
  • the two pressure booster chambers 11, 17 are connected via a parallel to the longitudinal center axis L of the injector 1, in Fig. 2 shown, throttle bore 20 hydraulically connected to each other.
  • the second pressure booster chamber 17 is bounded in the axial direction by a second booster piston 21 which is shown in FIG Embodiment is integrally formed with a nozzle needle 22 which is arranged axially adjustable within the second high-pressure chamber 8.
  • the second compression spring 19 is at the same time a closing spring, which is supported in the axial direction via a ring 23 on a shoulder of the nozzle needle 22 and this spring-loaded on a nozzle needle seat, not shown.
  • the piezocrystals arranged in the form of a stack assume their output variable, ie the piezoactuator comprising a piezocrystal stack contracts when the current is removed. Since the first booster piston 10 is subjected to a force on an annular surface 24 by the compression spring 15, the first booster piston 10 moves in the vertical direction in the plane of the drawing when the energization of the piezoelectric actuator 9 is removed. Due to the associated pressure relief in the first pressure booster chamber 11 and the pressure in the second pressure booster chamber 17, which over the in Fig. 1 Not shown throttle bore 20 is hydraulically connected to the first pressure booster chamber 11.
  • the acting on a front face 25 of the second booster piston 21 acting as a nozzle needle 22 decreases pressure and the nozzle needle 22 lifts from its nozzle needle seat, not shown, whereby fuel injected directly from the second high-pressure chamber 8 (nozzle chamber) via injection openings not shown in the combustion chamber of the internal combustion engine becomes.
  • the piezoelectric actuator 9 is energized, causing the piezocrystal stack expands and As a result, the first booster piston 10 is adjusted in the direction of the intermediate plate 4. As a result, the pressure in the first pressure booster chamber 11 and thus in the second pressure booster chamber 17 increases, with the result that the nozzle needle 22 in the drawing plane is moved downwards onto the nozzle needle seat (not shown).
  • the first injector body 2 is located with a first, end-side biting edge 26 on a first, linear, annular contoured contact surface 27 on the first end face 14 of the intermediate plate 4.
  • An inner biting edge angle ⁇ 1 (angle between the two annular surfaces forming the biting edge) is less than 90 °.
  • the first biting edge 26 is formed directly on the inner circumference of the first injector body 2. Radially outwardly, adjacent to the first biting edge 26, a conical, first biting surface 28 abuts.
  • the inner diameter of the second biting edge 29 is less than the inner diameter of the first biting edge 26.
  • the inner biting edge angle ⁇ 2 of the second biting edge 29 is less than 90 °. Radially outwardly to the second biting edge 29 bordering a concave second Anschliffs Chemistry 37.
  • the inner B thoroughlykantenwinkel ⁇ 2 is clamped between the second Anschliffs Chemistry 37 and an inside bevel 33rd
  • first biting edge 26 Radially outside the first biting edge 26 are located with radial distance to this more in the circumferential direction uniformly distributed first recesses 31 each having a depth extent of about 0.3mm in this embodiment.
  • the first recesses 31 are open in the radial direction to the outside.
  • second edge-side recesses 32 are arranged, wherein the areas of the second recesses 32 are larger than the areas of the first recesses 31.
  • the second recesses 32 protrude further in the radial direction than the first recesses 31 in each case
  • Recess 31 is associated with a second recess 32, wherein each first recess 31 each directly opposite a second recess 32.
  • the depth extension of each second recesses 32 is about 0.3 mm in the embodiment shown.
  • Fig. 2 is designed as a throttle plate intermediate plate 4 shown in two views.
  • the upper half of the drawing shows a plan view of the (upper) first end face 14 and the lower half of the drawing a plan view of the (lower) second end face 16.
  • the thickness extension (see. Fig. 1a ) of the intermediate plate 4 corresponds to a multiple of the depth extent of the first and second recesses 31, 32nd
  • the first and second recesses 31, 32 are uniformly spaced in the circumferential direction.
  • the angle ⁇ between two circumferentially adjacent recess centers 34 is 30 ° in the embodiment shown.
  • the recess centers indicated by reference numeral 34 are common recess centers 34 of the first and second ones Recesses 31, 32.
  • each first recess 31 directly opposite a second recess 32 axially, wherein the surface area of the second recesses 32 is greater than that of the first recesses 31.
  • the second recesses 32 project in the radial direction up to a radius R. 1 , which is smaller than a radius R 3 , to which the first recesses 31 point in the radial direction.
  • both the peripheral contour of the first recesses 31 and the peripheral contour of the second recesses 32 is at least approximately semicircular. Dashed lines show a possible, alternative, rectangular contouring using the example of a second cutout 32.
  • a first radial web 35 (support region) is formed between two circumferentially adjacent first recesses 31, and a second radial web 36 (support region) is formed between in each case two circumferentially adjacent second recesses 32.
  • the radial webs 35, 36 are arranged such that in each case a first radial web 35 and a second radial web 36 are opposite, so that between each two circumferentially adjacent recesses 31, 31 and 32, 32 a thicker, of a first and a second Radial web 35, 36 educated support area is formed.
  • the support areas reduce the bending tendency of the intermediate plate. 4
  • Fig. 2 corresponds to an outer radius R 2 of the second, planar end face 16 an outer radius R 4 of the first flat end side 14th
  • a radius R 5 of the first, directly cooperating with the first biting edge 26, circular first contact surface 27 is greater than the radius R 0 of the second, directly cooperating with the second biting edge 29, circular second contact surface 30th
  • the actual sealing area between the first injector body 2 and the intermediate plate 4 is arranged in the radial direction between the radius R 5 (first contact surface 27) and the radius R 4 (radial extent of the first recesses 31).
  • the sealing area on the second end face 16 is viewed in the radial direction formed between the radius R 0 (second contact surface 30) and the radius R 1 (radial extent of the second recesses 32).
  • the support region, formed in particular by the first radial webs 35 is arranged in the radial direction between the radius R 4 (outer radius of the intermediate plate 4) and the radius R 3 (radial extent of the first cutouts 31).
  • the support region formed essentially by the second radial webs 36 is located between the radius R 2 (outer radius of the intermediate plate 4) and the radius R 1 (inner radial extent of the second cutouts 32).

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Fuel-Injection Apparatus (AREA)
EP09100003A 2008-02-01 2009-01-05 Plaque intermédiaire pour un injecteur de carburant et injecteur de carburant Withdrawn EP2085606A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200810007225 DE102008007225A1 (de) 2008-02-01 2008-02-01 Zwischenplatte für einen Kraftstoffinjektor sowie Kraftstoffinjektor

Publications (1)

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EP2085606A1 true EP2085606A1 (fr) 2009-08-05

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EP09100003A Withdrawn EP2085606A1 (fr) 2008-02-01 2009-01-05 Plaque intermédiaire pour un injecteur de carburant et injecteur de carburant

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EP (1) EP2085606A1 (fr)
DE (1) DE102008007225A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011029664A1 (fr) * 2009-09-11 2011-03-17 Robert Bosch Gmbh Dispositif d'injection de carburant

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0957262A2 (fr) * 1998-05-13 1999-11-17 LUCAS INDUSTRIES public limited company Injecteur de combustible
WO2002063159A1 (fr) * 2001-02-06 2002-08-15 Siemens Aktiengesellschaft Element d'etancheite place entre des elements d'un injecteur de carburant destine a un moteur a combustion interne
DE10115214A1 (de) 2001-03-28 2002-10-10 Bosch Gmbh Robert Kraftstoffhochdrucksystem für Brennkraftmaschinen
DE202006002663U1 (de) 2006-02-20 2006-04-13 Robert Bosch Gmbh Kraftstoffinjektor für Brennkraftmaschinen

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0957262A2 (fr) * 1998-05-13 1999-11-17 LUCAS INDUSTRIES public limited company Injecteur de combustible
WO2002063159A1 (fr) * 2001-02-06 2002-08-15 Siemens Aktiengesellschaft Element d'etancheite place entre des elements d'un injecteur de carburant destine a un moteur a combustion interne
DE10115214A1 (de) 2001-03-28 2002-10-10 Bosch Gmbh Robert Kraftstoffhochdrucksystem für Brennkraftmaschinen
DE202006002663U1 (de) 2006-02-20 2006-04-13 Robert Bosch Gmbh Kraftstoffinjektor für Brennkraftmaschinen
EP1820957A2 (fr) * 2006-02-20 2007-08-22 Robert Bosch Gmbh Injecteur de carburant pour moteurs à combustion interne

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011029664A1 (fr) * 2009-09-11 2011-03-17 Robert Bosch Gmbh Dispositif d'injection de carburant

Also Published As

Publication number Publication date
DE102008007225A1 (de) 2009-08-06

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