EP1567763A1 - Soupape d'injection de carburant pour des moteurs a combustion interne - Google Patents

Soupape d'injection de carburant pour des moteurs a combustion interne

Info

Publication number
EP1567763A1
EP1567763A1 EP03775098A EP03775098A EP1567763A1 EP 1567763 A1 EP1567763 A1 EP 1567763A1 EP 03775098 A EP03775098 A EP 03775098A EP 03775098 A EP03775098 A EP 03775098A EP 1567763 A1 EP1567763 A1 EP 1567763A1
Authority
EP
European Patent Office
Prior art keywords
valve
needle
pressure
bore
fuel injection
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
EP03775098A
Other languages
German (de)
English (en)
Other versions
EP1567763B1 (fr
Inventor
Thomas Kuegler
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 EP1567763A1 publication Critical patent/EP1567763A1/fr
Application granted granted Critical
Publication of EP1567763B1 publication Critical patent/EP1567763B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1873—Valve seats or member ends having circumferential grooves or ridges, e.g. toroidal
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies

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 100 58 153 AI.
  • the fuel injection valve shown there has a valve body in which a bore is formed. At its end on the combustion chamber side, the bore is delimited by a valve seat in which a first row of injection openings and a second row of injection openings arranged on the combustion chamber side are formed, the injection openings of both rows of injection openings opening into the combustion chamber of the internal combustion engine.
  • An outer valve needle is arranged in the bore so as to be longitudinally displaceable and is guided in the bore in a section facing away from the combustion chamber.
  • a pressure chamber is formed between the outer valve needle and the wall of the bore, which can be filled with fuel under high pressure.
  • the valve outer needle At its end on the combustion chamber side, the valve outer needle has a valve sealing surface with which it interacts with the valve seat for controlling the first row of injection openings.
  • An inner bore in which a valve inner needle is arranged to be longitudinally displaceable, runs centrally along its longitudinal axis in the valve outer needle.
  • the valve inner needle has a sealing surface on its combustion chamber end, with which it interacts with the valve seat, and thereby the Controls opening of the second row of injection openings.
  • the opening force on the inner valve needle is generated by pressurizing a pressure surface which is acted upon by the fuel pressure of the annular space after the outer valve needle has been lifted off.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that the valve needle does not open the injection openings assigned to it uncontrolled before the intended point in time.
  • the opening force on the inner valve needle only builds up after a certain time delay after opening the outer valve needle.
  • the pressure surface of the valve inner needle can be connected to the pressure chamber via a throttle connection, which leads to the above-mentioned delay in building up the opening pressure.
  • the throttle connection is in the form of an annular gap between see the wall of the inner bore and the valve inner needle formed at the combustion chamber end of the outer valve needle.
  • a pressure chamber is formed in the outer valve needle by a radial expansion of the inner bore, in which the pressure surface of the inner valve needle is arranged and which can be connected to the pressure chamber by the throttle connection.
  • the design of the pressure chamber allows the size of the pressure area of the valve needle to be adjusted in larger areas in order to obtain the desired opening force. It is also advantageous in this embodiment to arrange a counterpressure surface in the pressure chamber on the outer valve needle, which is acted upon by the fuel pressure in the pressure chamber and which is directed opposite the valve sealing surface of the outer valve needle.
  • a return channel is formed, which opens into a leakage oil chamber formed in the fuel injection valve, in which there is a low fuel pressure.
  • the pressure chamber can be easily relieved via this return channel, so that after the injection has ended, the fuel pressure in the pressure chamber drops to the pressure of the leakage oil chamber.
  • a fuel injection valve according to the invention is shown in the drawing. It shows
  • FIG. 1 shows a fuel injection valve in longitudinal section
  • FIG. 2 shows an enlargement of the section from FIG. 1 designated II in the region of the valve seat
  • FIG. 4 shows the same detail as FIG. 2 in different opening phases of the fuel injection valve
  • FIG. 5 shows the same view as FIG. 4 of a modified exemplary embodiment.
  • a fuel injection valve according to the invention is shown in longitudinal section.
  • the fuel injection valve has a valve body 1, which is pressed by means of a clamping nut 3 against a valve holding body, not shown in the drawing.
  • a bore 5 is formed in the valve body 1 and is delimited at its combustion chamber end by a conical valve seat 18. From the valve Seat 18 extends from a first row of injection openings 20 and a second row of injection openings 22 arranged toward the combustion chamber.
  • both rows of injection openings 20, 22 open into the combustion chamber of the internal combustion engine.
  • a piston-shaped valve outer needle 8 is arranged in the bore 5 and is guided in the bore 5 in a section facing away from the combustion chamber.
  • the valve outer needle 8 tapers towards the valve seat 18 to form a pressure shoulder 12 and merges into a sealing surface 25 at its end on the combustion chamber side. Between the valve outer needle 8 and the wall of the bore 5, a pressure chamber 14 is formed, which is radially expanded at the level of the pressure shoulder 12. An inlet channel 16, which runs in the valve holding body 1 and opens into the radial expansion of the pressure chamber 14, supplies fuel under high pressure to the pressure chamber 14 from a high-pressure fuel source.
  • the valve outer needle 8 has an inner bore 11 in which a valve inner needle 10 is guided to be longitudinally displaceable.
  • the valve inner needle 10 has at its combustion chamber end a sealing surface 42 with which it, like the valve outer needle 8 with its sealing surface 35, rests on the valve seat 18.
  • valve outer needle 8 and the valve inner needle 10 are each acted upon separately at their end facing away from the combustion chamber by a closing force which presses the respective valve needle 8, 10 in the direction of the valve seat 18.
  • the closing force can be generated, for example, by springs or by hydraulic devices.
  • FIG. 2 shows an enlargement of the section from FIG. 1 designated II.
  • the valve outer needle 8 has at its combustion chamber end a conical surface 24 and an adjoining, also conical valve sealing surface 35. Due to the different opening angle of the conical surface 24 and the valve sealing surface 35, a first sealing edge 36 is formed at their transition, which is used to seal the pressure chamber 14 against the first injection Row of openings 20 serves when the valve outer needle 8 abuts the valve seat 18.
  • the conical valve sealing surface 35 has an opening angle that is slightly smaller than the opening angle of the conical valve seat 18.
  • annular groove 40 is formed on the valve sealing surface 35 between these two sealing edges 36, 38 and extends at the level of the first row of injection openings 20. The depth of the annular groove 40 is small, since a large volume in this area has an adverse effect on the hydrocarbon emissions of the internal combustion engine.
  • valve inner needle 10 is arranged with a certain clearance in the inner bore 11, so that a return channel 28 is formed between the valve inner needle 10 and the wall of the inner bore 11, which has an annular cross-section and at the end of the valve needles 8, 10 facing away from the combustion chamber into one in the Drawing not shown leakage oil chamber opens, in which there is always a low fuel pressure.
  • the valve inner needle 10 has a guide section 25, which represents a radial expansion of the valve inner needle 10 and ensures that the valve inner needle 10 is guided in the inner bore 11.
  • the guide section 25 forms a pressure shoulder 30 and merges into a conical sealing surface 42 at the end on the combustion chamber side.
  • a circumferential sealing edge 44 is formed, which comes into contact with the valve inner needle 10 in the closed position, ie when it is in contact with the conical valve seat 18.
  • the second row of injection openings 22 is closed off from the pressure chamber 14, so that no fuel can escape from the second row of injection openings 22.
  • the inner bore 11 of the valve outer needle 8 tapers towards its end on the combustion chamber side, forming an annular shoulder 34 which is arranged such that it lies opposite the pressure shoulder 30 of the valve inner needle 10.
  • a pressure chamber 27 is delimited by the pressure shoulder 30, the annular shoulder 34, the wall of the inner bore 11 and the valve needle 10 and is connected to the valve seat 18 via an annular gap 32, the annular gap 32 running between the valve inner needle 10 and the inner bore 11.
  • the pressure chamber 27 is also throttled to the return channel 28 via a residual gap 48 between the guide section 25 and the wall of the inner bore 11.
  • the fuel injector works as follows: In fuel injection systems which operate according to the so-called common rail principle, there is always a high fuel pressure in the pressure chamber 14 which corresponds to the injection pressure. A closing force which is so great that the two valve needles 8, 10 are held in contact with the valve seat 18 acts on the outer valve needle 8 and the inner valve needle 10, as a result of which the rows of injection openings 20, 22 are closed. In the fuel injection valve according to the invention, only a part of the fuel injection openings is opened first, and all the injection openings only in the further course of the injection. This will the closing force on the valve outer needle 8 is reduced, so that the hydraulic force on the pressure shoulder 12 and on the conical surface 24 of the valve outer needle 8 is greater than the closing force.
  • the outer valve needle 8 moves away from the valve seat 18, so that fuel can now flow from the pressure chamber 14 to the first row of injection openings 20, from where the fuel is injected into the combustion chamber of the internal combustion engine.
  • the valve inner needle 10 is held in its closed position by the closing force and by the lack of a corresponding opening force.
  • the fuel now also flows through the annular gap 32 into the pressure chamber 27, the annular gap 32 throttling so far that the pressure increase in the pressure chamber 27 occurs only with a certain delay. With increasing fuel pressure in the pressure chamber 27, a hydraulic force builds up on the pressure shoulder 30, which is directed against the closing force on the valve inner needle 10.
  • valve inner needle 10 As soon as the hydraulic force on the pressure shoulder 30 exceeds the closing force on the valve inner needle 10, the valve inner needle 10 also opens and its sealing edge 44 lifts off the valve seat 18, so that fuel is now also injected into the combustion chamber through the second row of injection openings 22. This open state, which is shown in FIG. 4, is maintained until the desired amount of fuel is injected into the combustion chamber.
  • the closing forces on the valve inner needle 10 and the valve outer needle 8 are increased until these closing forces are higher than the hydraulic forces due to the fuel pressure in the pressure chamber 14. Both the valve outer needle 8 and the valve inner needle 10 slide back into their closed position on the valve seat 18 and close both rows of injection openings 20, 22 again.
  • the design of the pressure chamber 27 also has a further advantage.
  • the opening speed of the outer valve needle 8 depends, in addition to the mass of the outer valve needle 8, on the acting forces, for a given closing force, that is on the surface of the outer valve needle 8 under pressure Lifted off the valve seat 18, the hydraulic force is added to the sealing surface 35.
  • the annular shoulder 34 counteracts this only very slightly, since the fuel pressure in the pressure chamber 27 is only slight at the beginning of the opening stroke movement, so that this force is negligible.
  • the outer valve needle 8 therefore opens very quickly, which is essential for rapidly successive injections. At the end of the injection, a high fuel pressure is present in the pressure chamber 27, which now also exerts a corresponding hydraulic force on the annular shoulder 34.
  • Figure 5 shows the same view as Figure 4 of another embodiment.
  • the connection of the pressure chamber 27 to the return channel 28 is not established here or not only via the remaining gap 48 formed between the guide section 25 and the wall of the inner bore 11, but via a plurality of cuts 46 which are formed laterally on the guide section 25.
  • the flow cross-section can be optimized by means of these cuts 46 in order to achieve a rapid pressure drop after the end of the injection and at the same time to ensure precise guidance of the valve inner needle 10 in the inner bore 11.
  • the cuts 46 are only very flat, preferably 5-20 ⁇ m.
  • the remaining gap 48 can be chosen to be as small as desired, as long as there is no excessive friction between the valve inner needle 10 and the wall of the inner bore 11, since the flow of fuel through the cuts 46 is ensured.
  • the flow cross-section of the grindings 46 is smaller than the flow cross-section of the annular gap 32.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne une soupape d'injection de carburant destinée à des moteurs à combustion interne et comprenant un corps de soupape (1) dans lequel est réalisé un alésage (5) délimité, à son extrémité côté chambre de combustion, par un siège de soupape (18) dans lequel sont formées une première rangée d'orifices d'injection (20) et une deuxième rangée d'orifices d'injection (22). Dans l'alésage (5) est placé un pointeau extérieur de soupape (8), déplaçable longitudinalement, qui coopère avec le siège de soupape (18) pour commander la première rangée d'orifices d'injection (20), une chambre de pression (14) étant réalisée entre le pointeau extérieur de soupape (8) et la paroi de l'alésage (5) et pouvant être remplie de carburant à haute pression. Un alésage intérieur (11) est réalisé dans le pointeau extérieur de soupape (8) ; un pointeau intérieur de soupape (10) y est logé déplaçable longitudinalement et coopère avec le siège de soupape (18) pour commander la deuxième rangée d'orifices d'injection (22). Sur le pointeau intérieur de soupape (10) est réalisé un épaulement de pression (30) par l'intermédiaire duquel une force d'ouverture hydraulique est exercée sur le pointeau intérieur de soupape (10) en cas de mise sous pression, le pointeau extérieur de soupape (8) ouvrant par son mouvement de course d'ouverture une liaison à étranglement (32) de la chambre de pression (14) vers l'épaulement de pression (30) du pointeau intérieur de soupape (10).
EP03775098A 2002-11-11 2003-10-31 Soupape d'injection de carburant pour des moteurs a combustion interne Expired - Lifetime EP1567763B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10252660 2002-11-11
DE10252660 2002-11-11
PCT/DE2003/003624 WO2004044415A1 (fr) 2002-11-11 2003-10-31 Soupape d'injection de carburant pour des moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP1567763A1 true EP1567763A1 (fr) 2005-08-31
EP1567763B1 EP1567763B1 (fr) 2006-09-27

Family

ID=32185552

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03775098A Expired - Lifetime EP1567763B1 (fr) 2002-11-11 2003-10-31 Soupape d'injection de carburant pour des moteurs a combustion interne

Country Status (6)

Country Link
US (1) US7143964B2 (fr)
EP (1) EP1567763B1 (fr)
JP (1) JP2006505742A (fr)
CN (2) CN100400850C (fr)
DE (3) DE10315821A1 (fr)
WO (1) WO2004044415A1 (fr)

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Also Published As

Publication number Publication date
CN1711415A (zh) 2005-12-21
EP1567763B1 (fr) 2006-09-27
DE10315821A1 (de) 2004-05-27
WO2004044415A1 (fr) 2004-05-27
DE50305205D1 (de) 2006-11-09
US20060118660A1 (en) 2006-06-08
JP2006505742A (ja) 2006-02-16
CN100400850C (zh) 2008-07-09
CN100378321C (zh) 2008-04-02
CN1711416A (zh) 2005-12-21
US7143964B2 (en) 2006-12-05
DE10315820A1 (de) 2004-05-27

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