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WO2003046367A1 - Soupape d'injection de carburant pour moteurs a combustion interne - Google Patents

Soupape d'injection de carburant pour moteurs a combustion interne Download PDF

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Publication number
WO2003046367A1
WO2003046367A1 PCT/DE2002/002612 DE0202612W WO03046367A1 WO 2003046367 A1 WO2003046367 A1 WO 2003046367A1 DE 0202612 W DE0202612 W DE 0202612W WO 03046367 A1 WO03046367 A1 WO 03046367A1
Authority
WO
WIPO (PCT)
Prior art keywords
sealing element
pressure
fuel injection
injection valve
elastic sealing
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.)
Ceased
Application number
PCT/DE2002/002612
Other languages
German (de)
English (en)
Inventor
Sieghart Maier
Thomas Pauer
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 WO2003046367A1 publication Critical patent/WO2003046367A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • 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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/02—Sealings between relatively-stationary surfaces
    • F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • F16J15/08—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with exclusively metal packing
    • F16J15/0887—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with exclusively metal packing the sealing effect being obtained by elastic deformation of the packing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/02—Sealings between relatively-stationary surfaces
    • F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • F16J15/08—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with exclusively metal packing
    • F16J15/0887—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with exclusively metal packing the sealing effect being obtained by elastic deformation of the packing
    • F16J15/0893—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with exclusively metal packing the sealing effect being obtained by elastic deformation of the packing the packing having a hollow profile
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/46—Sealings with packing ring expanded or pressed into place by fluid pressure, e.g. inflatable packings
    • F16J15/48—Sealings with packing ring expanded or pressed into place by fluid pressure, e.g. inflatable packings influenced by the pressure within the member to be sealed
    • 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
    • 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
    • F02M61/166—Selection of particular materials

Definitions

  • the invention is based on a fuel injection valve for internal combustion engines, as is known, for example, from the published patent application DE 198 27 267 A1.
  • the fuel injection valve described there has a housing, the housing comprising two bodies abutting one another, in which a high-pressure channel runs, which conveys fuel from a high-pressure source to an injection opening.
  • the high-pressure channel passes through the contact surface of the two bodies.
  • the two bodies are pressed against one another by a clamping nut on their contact surface, which is intended to ensure that the high-pressure duct is sealed at the passage through the contact surface of the two bodies. Since very high pressures of up to 200 MPa can occur in the high-pressure duct, this is not always the case.
  • the fuel injection valve for internal combustion engines according to the invention has the advantage that the pressure in the inlet channel is used to reinforce the sealing of the high-pressure channel in the region of the passage through the contact surface of the two bodies.
  • a sealing element is provided in the high-pressure channel in the area of the contact surface, which is designed to be elastic. Due to the pressure of the fuel, the elastic sealing element is pressed against the wall of the high-pressure duct, so that no fuel can get between the two bodies.
  • the elastic sealing element is designed in the shape of a hollow cylinder and lies with its outer circumferential surface against the wall of the high-pressure channel, one end of the elastic sealing element being arranged in the first body and the other end in the second body.
  • the sealing element designed in this way is simple to manufacture, easy to assemble and offers a secure seal.
  • the hollow cylindrical elastic sealing element is arranged in a radial extension of the high-pressure channel, so that it cannot move in the axial direction. This arrangement also has the advantage that the cross section of the high-pressure duct can be kept at least approximately constant, in order to avoid swirling of the fuel flowing through.
  • the annular gap that exists between the wall of the high-pressure duct and the outer surface of the elastic sealing element is connected via a connection channel formed in the housing to a fuel-filled leak oil chamber which is present in the housing and in which there is always a low pressure.
  • annular space is formed between the outer circumferential surface of the elastic sealing element and the wall of the high-pressure duct, into which the connecting duct opens. This ensures that fuel that gets between the elastic sealing element and the wall of the high-pressure duct can flow into the leakage oil chamber via the connecting duct.
  • a ring shoulder is formed at the transition from the first to the second body in the high-pressure duct, on which the elastic sealing element bears with a contact surface. This ensures that the sealing element does not move in the longitudinal direction in the high-pressure duct.
  • the sealing element is rotationally symmetrical and at least approximately has an L-shaped longitudinal section. Together with the system on the ring shoulder, a contact force of the sealing element is obtained both against the contact surface and against the wall of the high-pressure duct, so that a secure seal is ensured.
  • the elastic sealing element is arranged in a recess which is delimited by a first and a second ring surface.
  • the Sealing element has a first and a second contact surface, which come to rest on the first and second ring surface and are pressed against the ring surfaces by the pressure in the high-pressure channel.
  • the first ring surface is arranged in the first body and the second ring surface in the second body, so that in addition to the sealing by the radial contact force against the wall of the high-pressure duct, an additional sealing is achieved by pressing the contact surfaces against the ring surfaces.
  • the elastic sealing element is toroidal and has a cavity which is connected to the high-pressure duct via openings.
  • fuel can flow from the high-pressure channel through the openings into the cavity of the sealing element and inflate it.
  • the toroidal sealing element is pressed against the limits of the radial expansion and thereby seals reliably.
  • the elastic sealing element consists of a plastic, preferably an elastomer. This ensures a high level of deformability and a sealing fit of the elastic sealing element against the wall of the high-pressure duct.
  • the elastic sealing element can also consist of a soft metal, preferably copper.
  • drawing shows several exemplary embodiments of the device according to the invention for supplying an internal combustion engine. It shows
  • FIG. 1 shows a longitudinal section through a fuel injection valve
  • FIG. 2 shows an enlargement of FIG. 1 in the area designated II
  • FIG. 3 shows the same detail as FIG. 2 of a further exemplary embodiment
  • FIG. 4 shows an enlargement of FIG. 3 in the area designated IV
  • FIG. 5 shows the same detail as FIG. 4 of a further exemplary embodiment
  • Figure 6 shows the same detail as Figure 5 of another embodiment.
  • the fuel injection valve has a housing 1 which comprises a first body which is designed as a valve holding body 3 and a second body which is designed as a valve body 5.
  • the valve holding body 3 and the valve body 5 lie against one another on a contact surface 20 and are pressed against one another by a tensioning device, not shown in the drawing.
  • a bore 12 is formed in the valve body 5, in which a piston-shaped valve needle 16 is arranged to be longitudinally displaceable. At its end on the combustion chamber side, the bore 12 is closed except for at least one injection opening 14, which connects the bore 12 with the combustion chamber of the internal combustion engine.
  • valve needle 16 In a section facing away from the combustion chamber, the valve needle 16 is sealingly guided its length in the bore 12 and controls the opening of the at least one injection opening 14 by its longitudinal movement in the bore 12
  • a pressure chamber 11 is formed in the bore 12 in the valve body 5, into which a high-pressure channel 10 runs in the valve body 5 and in the valve holding body 3, which connects the pressure chamber 11 to a high-pressure fuel source, not shown in the drawing.
  • the high-pressure channel 10 passes through the contact surface 20 of the valve holding body 3 and valve body 5. Through the high-pressure channel 10, the pressure chamber 11 can be filled with fuel under high pressure, which then flows from the pressure chamber 11 past the valve needle 16 to the injection openings 14.
  • a leak oil chamber 7 is formed in the valve holding body 3 and is designed as a longitudinal bore in the center of the valve holding body 3.
  • the leakage oil chamber 7 is essentially rotationally symmetrical and has a longitudinal axis 9 that is parallel to the longitudinal axis of the bore 12.
  • the leak oil chamber 7 is connected to a leak oil system via a line (not shown in the drawing), so that there is always a low pressure in the leak oil chamber 7.
  • the leakage oil chamber 7 is connected by the annular gap remaining between the valve needle 16 and the wall of the bore 12 to the bore 12 formed in the valve body 5, the annular gap only permitting a strongly throttled flow of fuel from the pressure chamber 11 into the leakage oil chamber 7. This is essential for the function, since there is at least occasionally a very high fuel pressure in the high-pressure channel 10, which can be over 100 MPa.
  • FIG. 2 shows an enlargement of the section from FIG. 1, designated II, in the region of the passage of the high-pressure duct 10 through the contact surface 20.
  • a radial extension 27 is formed in the high-pressure channel 10, which extends with a part of its length in the valve holding body 3 and with a part of its length in the valve body 5.
  • a sealing element 25 is arranged in the radial extension 27, which is linden-shaped and rests with its outer surface on the radial extension 27.
  • a chamfer in the valve holding body 3 on the radial extension 27 forms an annular space 30 which is connected to the leakage oil space 7 via a connecting channel 32.
  • the sealing element 25 here consists of an elastic material, preferably of a plastic, and of the group of plastics, preferably of an elastic. Due to the fuel pressure in the high-pressure duct 10, the sealing element 20 is pressed radially outward, since in the annular gap 29 through the annular space 30 and its connection with the leakage oil space 7 there is a significantly lower pressure than in the high-pressure duct 10.
  • FIG. 3 shows a further exemplary embodiment of the sealing element 25, the section of FIG. 1 shown here being the same as that of FIG. 2.
  • FIG. 4 shows a further enlargement of FIG. 3 in the section designated IV.
  • a radial extension 27 is again provided in the valve holding body 3 in the high-pressure channel 10, but ends at the transition to the valve body 5.
  • the diameter of the high-pressure channel 10 in the valve body 5 is significantly smaller than the diameter of the radial extension 27, so that an annular shoulder 35 is formed at the transition from the valve body 3 to the valve body 5.
  • the sealing element 25 is rotationally symmetrical and has an L-shaped longitudinal section. This is on the sealing element 25 an annular disk-shaped contact surface 37 is formed, which comes to rest on the ring shoulder 35.
  • the elastic element 25 is pressed in the radial direction against the wall of the radial extension 27 and also through the L-shaped longitudinal section with the contact surface 37 against the ring shoulder 35.
  • a chamfer and thereby an annular space 30 is also formed, which is connected to the leakage oil space 7 via a connecting channel 32.
  • Figure 5 shows the same section as Figure 4 of another embodiment.
  • a radial extension 27 is provided in the valve holding body 3, which is delimited by a first annular surface 40 and a second annular surface 42, the second annular surface 42 being formed on the valve body 5.
  • the first ring surface 40 is perpendicular to the wall of the radial extension 27, so that there is a rectangular longitudinal section of the radial extension 27.
  • the sealing element 25 has a C-shape in longitudinal section, so that a first ring-shaped sealing surface 44 and a second ring-shaped sealing surface 46 are formed on the sealing element 25, the first sealing surface 44 on the first ring surface 40 and the second sealing surface 46 on the second ring surface 42 come to the plant.
  • the elastic element 25 Due to the pressure in the high-pressure duct 10, the elastic element 25 is inflated and its outer lateral surface is pressed in the radial direction against the wall of the radial extension.
  • the sealing surfaces 44 and 46 are pressed against the corresponding ring surfaces 40 and 42, so that an all-round tight connection of the sealing element 25 with the radial extension 27 is produced.
  • a chamfer and an annular space 30 formed thereby are provided in the valve holding body 3, which is connected via a connecting channel 32 and the leak oil chamber 7.
  • FIG. 6, FIG. 6 showing the same detail as FIG. 5.
  • the radial extension 27 is here essentially the same as the one shown in FIG.
  • the sealing element 25 has a toroidal shape with a wall and a cavity 48 which is annular.
  • the cavity 48 is connected to the high-pressure duct 10 via openings 50 which are formed in the wall of the toroidal sealing element 25.
  • fuel can penetrate from the high-pressure channel 10 through the openings 50 into the cavity 48 of the sealing element 25 and inflate it.
  • an annular space is formed in the valve holding body 3 by a chamfer, which is connected to the leakage oil space 7 via a connecting channel and ensures that the annular space between the wall of the radial extension 27 and the sealing element 25 remains unpressurized.
  • such a seal of a high-pressure channel can also be formed in other devices, for example in high-pressure fuel pumps, low-pressure fuel pumps, valves or other supply devices for internal combustion engines.
  • the fuel but rather another fluid, for example water or a liquid gas, is passed through the high-pressure channel 10, that is to say any medium which can only transmit pressure forces.
  • the sealing element 25 be made of metal, for example made of copper, steel or another elastically deformable metal.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Architecture (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne une soupape d'injection de carburant destinée à des moteurs à combustion interne. Cette soupape comprend un boîtier (1) comportant un premier corps (3) et un second corps (5), ces deux corps étant en contact l'un avec l'autre au niveau d'une surface de contact (20). Dans les corps (3 ; 5) est ménagé un canal haute pression (10) qui traverse la surface de contact (20) des deux corps (3 ; 5) et qui est rempli de carburant, ce carburant se trouvant au moins temporairement sous haute pression. Un élément d'étanchéité (25) est placé dans le canal haute pression (10) au niveau de la surface de contact (20). Cet élément d'étanchéité peut être déformé élastiquement et comprimé contre la paroi du canal haute pression (10) par la pression du carburant présent dans le canal. L'étanchéité du canal haute pression (10) est ainsi assurée au niveau du passage à travers la surface de contact (20) des deux corps (3 ; 5).
PCT/DE2002/002612 2001-11-13 2002-07-17 Soupape d'injection de carburant pour moteurs a combustion interne Ceased WO2003046367A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2001155677 DE10155677A1 (de) 2001-11-13 2001-11-13 Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10155677.2 2001-11-13

Publications (1)

Publication Number Publication Date
WO2003046367A1 true WO2003046367A1 (fr) 2003-06-05

Family

ID=7705570

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2002/002612 Ceased WO2003046367A1 (fr) 2001-11-13 2002-07-17 Soupape d'injection de carburant pour moteurs a combustion interne

Country Status (2)

Country Link
DE (1) DE10155677A1 (fr)
WO (1) WO2003046367A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004022428A1 (de) * 2004-05-06 2005-12-01 Siemens Ag Einspritzventil für Brennkraftmaschinen
JP4618307B2 (ja) * 2008-03-06 2011-01-26 株式会社デンソー 燃料噴射弁
DE102012222167A1 (de) 2012-12-04 2014-06-05 Robert Bosch Gmbh Alternativer Hochdruckanschluss mit Feder-Dichtlinse
DE102022117405A1 (de) * 2022-07-13 2024-01-18 Thomas Schneider Dichtungsvorrichtung

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2460746A1 (de) * 1974-12-21 1976-07-01 Maschf Augsburg Nuernberg Ag Metallische dichtung
US4817993A (en) * 1986-04-18 1989-04-04 Walter Zoboli Dielectric joint, particularly for metallic conduits for liquids and/or gases
DE19614980C1 (de) * 1996-04-16 1997-09-18 Hatz Motoren Einspritzvorrichtung
DE19729788A1 (de) * 1997-07-11 1999-01-14 Bosch Gmbh Robert Radialkolbenpumpe zur Kraftstoffhochdruckversorgung
DE19827267A1 (de) 1998-06-18 1999-12-23 Bosch Gmbh Robert Kraftstoff-Einspritzventil für Hochdruck-Einspritzung mit verbesserter Steuerung der Kraftstoffzufuhr
DE19827628A1 (de) 1998-06-20 1999-12-23 Daimler Chrysler Ag Kraftstoffeinspritzventil für Brennkraftmaschinen
US20010020648A1 (en) * 2000-02-24 2001-09-13 Robert Bosch Gmbh Fuel injection valve for internal combustion engines

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2460746A1 (de) * 1974-12-21 1976-07-01 Maschf Augsburg Nuernberg Ag Metallische dichtung
US4817993A (en) * 1986-04-18 1989-04-04 Walter Zoboli Dielectric joint, particularly for metallic conduits for liquids and/or gases
DE19614980C1 (de) * 1996-04-16 1997-09-18 Hatz Motoren Einspritzvorrichtung
DE19729788A1 (de) * 1997-07-11 1999-01-14 Bosch Gmbh Robert Radialkolbenpumpe zur Kraftstoffhochdruckversorgung
DE19827267A1 (de) 1998-06-18 1999-12-23 Bosch Gmbh Robert Kraftstoff-Einspritzventil für Hochdruck-Einspritzung mit verbesserter Steuerung der Kraftstoffzufuhr
DE19827628A1 (de) 1998-06-20 1999-12-23 Daimler Chrysler Ag Kraftstoffeinspritzventil für Brennkraftmaschinen
US20010020648A1 (en) * 2000-02-24 2001-09-13 Robert Bosch Gmbh Fuel injection valve for internal combustion engines

Also Published As

Publication number Publication date
DE10155677A1 (de) 2003-05-22

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