EP1843038A1 - Injecteur de carburant avec boitier à surfaces d'étanchéité coniques haute pression - Google Patents

Injecteur de carburant avec boitier à surfaces d'étanchéité coniques haute pression Download PDF

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Publication number
EP1843038A1
EP1843038A1 EP06007432A EP06007432A EP1843038A1 EP 1843038 A1 EP1843038 A1 EP 1843038A1 EP 06007432 A EP06007432 A EP 06007432A EP 06007432 A EP06007432 A EP 06007432A EP 1843038 A1 EP1843038 A1 EP 1843038A1
Authority
EP
European Patent Office
Prior art keywords
fuel injector
pressure
sealing surfaces
housing
housing parts
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
EP06007432A
Other languages
German (de)
English (en)
Other versions
EP1843038B1 (fr
Inventor
Jürgen Dick
Hellmut Freudenberg
Walter Dr. Meindl
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.)
Aumovio Germany GmbH
Original Assignee
Siemens AG
Continental Automotive Technologies GmbH
Siemens Corp
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, Continental Automotive Technologies GmbH, Siemens Corp filed Critical Siemens AG
Priority to EP06007432A priority Critical patent/EP1843038B1/fr
Priority to DE502006003182T priority patent/DE502006003182D1/de
Publication of EP1843038A1 publication Critical patent/EP1843038A1/fr
Application granted granted Critical
Publication of EP1843038B1 publication Critical patent/EP1843038B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F02M63/0014—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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • 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
    • 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
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/701—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger mechanical
    • F02M2200/702—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger mechanical with actuator and actuated element moving in different directions, e.g. in opposite directions
    • 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
    • F02M61/167—Means for compensating clearance or thermal expansion

Definitions

  • the invention relates to a fuel injector having at least two cylindrical housing parts, which are joined together by means of a nozzle lock nut, according to the preamble of the main claim.
  • a fuel injector has a plurality of subassemblies which are assembled axially one above the other.
  • Such assemblies may be, for example, an injector housing and a nozzle housing held together by a nozzle lock nut.
  • the nozzle retaining nut is pushed over the nozzle housing as a union nut and firmly screwed to the injector housing.
  • the end faces of the two opposing housing parts are designed as sealing surfaces and are pressed together by the clamping force of the nozzle retaining nut.
  • a high pressure space e.g. Having fuel supply lines and / or pressure accumulator, formed, which is filled with fuel and in a diesel fuel injector of a common rail system may have a pressure of up to 2000 bar. Against this high pressure no leakage may occur at the end faces of the two assembled housing parts.
  • the invention has for its object to improve in a fuel injector, the high-pressure tightness of two abutting sealing surfaces of two housing parts. This object is achieved with the features independent claim.
  • the two abutting sealing surfaces of the two housing parts are conical or frustoconical.
  • the two sealing surfaces of the two housing parts are thus not manufactured at right angles to the longitudinal axis, but with a predetermined cone angle.
  • the two sealing surfaces are convex / concave flush or conical / convex contiguous.
  • the two housing parts are placed on each other with the help of the cone and pressed firmly together by the high torque of the nozzle lock nut.
  • the upper housing has a softer material or a thinner wall thickness than the lower housing part, then the upper housing part will expand somewhat more than the lower housing part when there is a pressure increase inside the fuel injector in the radial direction. Due to the high biasing force of the nozzle lock nut, however, both housing parts are fixed in this position so that their relative position to one another no longer shift after the high pressure has dropped can. This ensures that no relative displacement can occur between the two sealing surfaces of the two housing parts.
  • the high-pressure seal is therefore wear-free and reliable high-pressure-tight.
  • the sealing surfaces are formed rounded one another.
  • conical sealing surfaces can be easily formed on any housing parts.
  • a reliable high-pressure seal can also be achieved in this way between the injector housing and a further module, for example in the case of an inserted housing plate for the lever translator.
  • the high-pressure seal can be carried out in particular in a fuel injector, which has no leakage oil return.
  • a fuel injector which has no leakage oil return.
  • the high-pressure space in the interior of the fuel injector is made relatively large, so that the high-pressure seal is also exposed to particularly high loads.
  • Another aspect of the invention is that in the construction and in the design of the fuel injector it is no longer necessary to pay close attention to the fact that the wall thicknesses in the high-pressure region are the same as possible for you and for the material involved. This results in a much greater latitude for the designer in the design of the injector design.
  • the fuel injector 1 shows a detail of a longitudinal section through a fuel injector 1.
  • the fuel injector 1 is part of a common rail injection system, which is particularly suitable for diesel engines or gasoline engines.
  • the fuel injector 1 is formed without leakage oil return.
  • the fuel injector 1 is applicable to all types of fuel injectors.
  • a piezoelectric actuator 3 is arranged in the upper part of FIG.
  • the piezoelectric actuator 3 is arranged in a central bore of the fuel injector 1 such that upon electrical excitation, its bottom plate can expand downwards, while its top plate (not shown in Figure 1) is fixedly connected to an injector 2. If the excitation voltage is switched off, then the lower part of the piezoelectric actuator 3 retracts back to its original position.
  • a hydraulic longitudinal compensation 10 is arranged in the central bore of the further below the bottom plate of the piezoelectric actuator 3.
  • the hydraulic longitudinal compensation 10 causes changes in length of the actuator as a result of temperature changes, aging, wear, etc. are compensated automatically by hydraulic means, so that always the full stroke of the piezoelectric actuator 3 is available.
  • the hydraulic longitudinal compensation 10 is pressed by means of a compression spring 11, which is supported at its upper end against the injector 2, down.
  • a lever translator 15 is arranged such that the change in length of the piezoelectric actuator 3 can be transmitted to the lever translator 15.
  • the lever translator 15 has two essential tasks to fulfill.
  • the hydraulic lever translator 15 is intended to increase the stroke of the piezoelectric actuator 3, which is usually of the order of magnitude of 50 to 80 ⁇ m. As a result, the opening travel of a nozzle needle 7 can be increased.
  • a second task for the lever translator 15 is also that the lever translator 15 is simultaneously designed as a Hubumnovaer.
  • the Hubumrocker causes the downward length alignment of the piezoelectric actuator 3 is converted into a lifting movement for the nozzle needle 7, which is directed upward.
  • the lever translator 15 is essentially a pressure lever 19, to which the pressure force of the piezoelectric actuator 3 by means of the hydraulic longitudinal compensation 10 can be transmitted.
  • the pressure lever 19 is arranged transversely in the central bore of the actuator housing 2.
  • the pressure lever 19 is supported with its right part on a fixed support block 14.
  • the fixed support block 14 is formed angularly, with its free leg engages in a groove of a nozzle needle 7, which at the shaft of the nozzle needle 7 slightly below the The head is arranged in a ring shape.
  • the free leg of the support block 14 bears against the groove of the nozzle needle 7 at the top.
  • the left part of the pressure lever 19 is designed to be movable. Below the left part of the pressure lever 19, a rocker arm 16 is arranged, which is in operative connection with the movable part of the pressure lever 19. The rocker arm 16 is guided with its free leg into the groove of the nozzle needle 7 and designed such that the nozzle needle 7 is lifted from its valve seat when the piezoelectric actuator 3 is actuated while the pressure lever 19 presses on the rocker arm 16.
  • a housing part 5 is arranged below the lever translator 15, a housing part 5 is arranged.
  • the lower end of the nozzle housing 6 is formed with spray holes which are opened when the piezoelectric actuator 3 is actuated or closed when the control is switched off (not shown in FIG. 1).
  • a nozzle needle spring 13 is additionally arranged coaxially around the nozzle needle 7, which on the one hand against a lower end face of the housing part 5 and with its second end against a pressure surface of the nozzle needle. 7 supports and presses the nozzle needle 7 in the direction of its valve seat down.
  • the nozzle housing 6, the housing part 5 arranged above it and the injector housing 2 are held together with a nozzle retaining nut 4, wherein the nozzle retaining nut 4 is guided from below over the nozzle housing 6 and is firmly screwed to an external thread of the injector housing 2.
  • the housing part 5 is formed as a housing plate.
  • the housing part may be formed, for example, as a needle guide body or the like.
  • a high-pressure chamber 9 is formed, which is filled with fuel, diesel oil or gasoline.
  • the high pressure in the high pressure chamber 9 is generated by a pressure pump of the common rail injection system (not shown in Figure 1), wherein the fuel from the high pressure pump via corresponding channels of the fuel injector 1 to the high pressure chamber 9 and on to the nozzle tip of the nozzle housing 6 is performed ,
  • the high-pressure chamber is limited on the one hand to the outside through the wall of the cylinder-shaped injector 2 upwards.
  • the high-pressure chamber is bounded on the one hand by the shaft of the nozzle needle 7. Furthermore, there is a lateral boundary of the high-pressure chamber 9 through the wall of the cylinder-shaped housing part. 5
  • the lower end face of the fuel injector 2 which rests on the upper end face of the housing part 5, formed as a high-pressure seal 12. Since there is a fuel pressure inside the high-pressure chamber 9, in particular in the case of a diesel injector of up to 2000 bar, this high-pressure seal 12 must be designed to be particularly reliable and safe. In particular, it must be ensured that the high-pressure seal 12 is wear-free and durable, in particular if the wall thicknesses of the two assembled housing parts 2.5 are different degrees or if different rigid materials are used.
  • the wall thickness of the injector 2 is formed thinner than that of the housing part 5.
  • Figure 2 shows a section of the high-pressure seal 12, as in the longitudinal section of Figure 1 on the right side is shown.
  • the wall thickness d1 of the injector housing 2 is smaller than the wall thickness d2 of the housing part 5.
  • Both housing parts 2, 5 are compressed by the nozzle lock nut 4 on the upper sealing surface 8a of the injector housing 2 and the lower sealing surface 8b of the housing part 5 by the bias of the nozzle lock nut 4.
  • the two pressure surfaces 8a, 8b are formed conically with a cone angle ⁇ .
  • the conical or rounded design of the high pressure seal 12 is one aspect of the invention.
  • the cone angle ⁇ is formed so that the component with the thinner wall thickness or the weaker stiffness can not withstand pressure relief. As shown in Figures 1 and 2, the cone angle ⁇ is formed leading downward. As a result, the injector housing 2 with the smaller wall thickness d1 can expand outward when the pressure rises, thereby sliding on the sealing surfaces 8a, 8b. Due to the high clamping force P v of the nozzle retaining nut 4, the two sealing surfaces 8a, 8b of the two housing parts 2, 5 are fixed in this position.
  • the clamping force P v of the nozzle lock nut 4 continues to act in the axial direction to the fuel injector 1 on the two sealing surfaces 8 a, 8 b.
  • the cone angle ⁇ a stronger contraction of the wall of the injector 2 in the continued existing clamping force P v of the nozzle lock nut 4 prevents.
  • the result is that the high-pressure seal 12 is completely free of wear and reliably sealed high pressure-tight. Even with aging or temperature changes, a shift of the two sealing surfaces, 8a, 8b to each other can not form.
  • the cone angle ⁇ is preferably formed depending on the application and the prevailing fuel pressure between 10 and 20 °.
  • FIG 3 shows an alternative embodiment of the sealing surfaces 8a, 8b of Figure 2 with rounded sealing surfaces 8a ', 8b'.
  • the concave sealing surface 8a ' is flush with the convex sealing surface 8b'.
  • Both sealing surfaces preferably have the same radius R.
  • the sealing effect corresponds to the o.g. Version with conical sealing surfaces.
  • the radius of the convex sealing surface 8b ' is slightly smaller than the radius of the concave sealing surface 8a', so that the better tighten the sealing surfaces and a sealing ring with increased surface pressure arises.
  • FIG. 4 shows an alternative embodiment of the sealing surfaces 8a, 8b from FIG. 2 with a convex sealing surface 8d with a radius R1 and a conical sealing surface 8c resting thereon.
  • this version can also be the Tighten sealing surfaces better. The result is a sealing ring with increased surface pressure.

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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)
EP06007432A 2006-04-07 2006-04-07 Injecteur de carburant avec corps à surfaces d'étanchéité coniques haute pression Expired - Lifetime EP1843038B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP06007432A EP1843038B1 (fr) 2006-04-07 2006-04-07 Injecteur de carburant avec corps à surfaces d'étanchéité coniques haute pression
DE502006003182T DE502006003182D1 (de) 2006-04-07 2006-04-07 Kraftstoffinjektor mit einer kegeligen Gehäusehochdruckdichtung

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP06007432A EP1843038B1 (fr) 2006-04-07 2006-04-07 Injecteur de carburant avec corps à surfaces d'étanchéité coniques haute pression

Publications (2)

Publication Number Publication Date
EP1843038A1 true EP1843038A1 (fr) 2007-10-10
EP1843038B1 EP1843038B1 (fr) 2009-03-18

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EP06007432A Expired - Lifetime EP1843038B1 (fr) 2006-04-07 2006-04-07 Injecteur de carburant avec corps à surfaces d'étanchéité coniques haute pression

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EP (1) EP1843038B1 (fr)
DE (1) DE502006003182D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010081583A1 (fr) * 2009-01-13 2010-07-22 Robert Bosch Gmbh Soupape d'injection de combustible

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1692107A (en) * 1924-09-17 1928-11-20 Archaouloff Vadime Direct-injection fuel atomizer for internal-combustion engines
DE19608575A1 (de) * 1996-03-06 1997-09-11 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
WO2004046540A1 (fr) * 2002-11-20 2004-06-03 Siemens Aktiengesellschaft Injecteur dote d'un pointeau a niveaux a entrainement direct pour l'injection de carburant dans un moteur a combustion interne
EP1619383A2 (fr) * 2004-07-23 2006-01-25 Magneti Marelli Holding S.p.A. Injecteur de carburant actionné par un electro aimant

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1692107A (en) * 1924-09-17 1928-11-20 Archaouloff Vadime Direct-injection fuel atomizer for internal-combustion engines
DE19608575A1 (de) * 1996-03-06 1997-09-11 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
WO2004046540A1 (fr) * 2002-11-20 2004-06-03 Siemens Aktiengesellschaft Injecteur dote d'un pointeau a niveaux a entrainement direct pour l'injection de carburant dans un moteur a combustion interne
EP1619383A2 (fr) * 2004-07-23 2006-01-25 Magneti Marelli Holding S.p.A. Injecteur de carburant actionné par un electro aimant

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010081583A1 (fr) * 2009-01-13 2010-07-22 Robert Bosch Gmbh Soupape d'injection de combustible
US9103310B2 (en) 2009-01-13 2015-08-11 Robert Bosch Gmbh Fuel injector

Also Published As

Publication number Publication date
EP1843038B1 (fr) 2009-03-18
DE502006003182D1 (de) 2009-04-30

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