EP2867517A1 - Soupape d'injection de carburant pour moteurs à combustion interne - Google Patents

Soupape d'injection de carburant pour moteurs à combustion interne

Info

Publication number
EP2867517A1
EP2867517A1 EP13723131.2A EP13723131A EP2867517A1 EP 2867517 A1 EP2867517 A1 EP 2867517A1 EP 13723131 A EP13723131 A EP 13723131A EP 2867517 A1 EP2867517 A1 EP 2867517A1
Authority
EP
European Patent Office
Prior art keywords
control
chamber
control chamber
fuel
pressure
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
EP13723131.2A
Other languages
German (de)
English (en)
Other versions
EP2867517B1 (fr
Inventor
Andreas Gruenberger
Hans-Christoph Magel
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 EP2867517A1 publication Critical patent/EP2867517A1/fr
Application granted granted Critical
Publication of EP2867517B1 publication Critical patent/EP2867517B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F02M47/025—Hydraulically 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
    • 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
    • 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
    • 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
    • F02M63/0028—Valves characterised by the valve actuating means hydraulic
    • F02M63/0029—Valves characterised by the valve actuating means hydraulic using a pilot valve controlling a hydraulic chamber
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • F02M63/0042—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing combined with valve seats of the lift valve type
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0043—Two-way valves
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0075—Stop members in valves, e.g. plates or disks limiting the movement of armature, valve or spring
    • 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
    • F02M2547/003—Valve inserts containing control chamber and valve piston
    • 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
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift

Definitions

  • the invention relates to a fuel insp scritz valve for internal combustion engines, as it is preferably used for injecting fuel into a combustion chamber of a self-igniting internal combustion engine.
  • PRIOR ART Injection systems for injecting fuel into combustion chambers under high pressure are known from the prior art.
  • fuel is compressed by a high-pressure pump and stored in a high-pressure accumulator, a so-called rail.
  • a high-pressure accumulator one or more fuels are fed insp ritz valves that inject the required fuel into the respective combustion chamber.
  • the aim is to atomize exactly the required amount of fuel as finely as possible and to introduce it into the combustion chamber evenly.
  • DE 100 24 702 Al for example, such an injection system including injection valve is known.
  • the known fuel injection valves have a nozzle needle, which is arranged longitudinally displaceable in a housing and which cooperates with a nozzle seat for opening and closing at least one injection opening.
  • the movement of the nozzle needle is controlled by the pressure in a control chamber which acts on the valve seat facing away from the end face of the nozzle needle. Via a control valve, the pressure in the control chamber is lowered or increased, which changes the closing force on the nozzle needle accordingly, so that these driven by the hydraulic force of the injection pressure and the nozzle needle surrounding fuel moves in the longitudinal direction.
  • the pressure in the control room is achieved by the inflow and outflow of pressurized fuel.
  • the control chamber is always connected to pressurized fuel via an inlet throttle, which connects the control chamber with a high pressure line within the fuel injection valve.
  • the control chamber can be connected via an outlet throttle with a low-pressure chamber, wherein the outlet throttle can be opened or closed by a control valve.
  • the outlet throttle When the outlet throttle is open, pressurized fuel thus flows out of the control chamber into the low-pressure chamber, whereby the pressure in the control chamber is reduced and thus the closing force on the nozzle needle.
  • a control piston is longitudinally displaceably arranged in the control chamber, which controls the control chamber into a first
  • Sub-control room and a second sub-control room the first part being Control space via an outlet throttle with a low-pressure chamber is connected and the first with the second part of the control room via a connecting throttle are always connected hydraulically.
  • On the control piston a sealing surface is formed, which cooperates with a sealing seat, so that when the sealing surface on the sealing seat of the second part control chamber is hydraulically separated from the inlet throttle.
  • the control piston is not moved by other actuators or other control devices, but its movement takes place exclusively on the hydraulic forces acting on it.
  • the structure is correspondingly simple and inexpensive to implement.
  • the connecting throttle is formed in a valve piece, in which the control piston is guided. This allows great variability in the arrangement of the control piston and valve piece and, compared to a guide directly in the housing of the fuel injection valve, reduces the production costs.
  • the connecting throttle can be advantageously formed in the valve piece.
  • the connection throttle can also be formed in the control piston itself.
  • annular groove is formed in the outer surface of the control piston into which the inlet throttle opens.
  • the annular groove is separated when the sealing surface on the sealing seat from the second part control room. Since the annular groove has the same hydraulically effective area in both longitudinal movement directions of the control piston, there is no hydraulic force acting on the control piston in the longitudinal direction through the fuel in the annular groove, which would have to be compensated.
  • control piston is acted upon by a spring element away from the sealing seat with an opening force.
  • Spring element serves to the control piston in a defined output to bring about a clear function.
  • the spring element can be arranged in an advantageous manner in the second part of the control room, so that the first part control room can be kept very small, which allows rapid switching of the fuel insp scritz valve.
  • FIG. 1 shows an inventive fuel insp scritz valve in longitudinal section
  • Fig. 2 shows an enlarged detail of Fig. 1 in the control room
  • Fig. 3, 4, 5 and 6 in the same representation as Fig. 2 further embodiments of the invention.
  • FIG. 1 a fuel inspector valve according to the invention is shown schematically in longitudinal section.
  • the fuel insp ritz valve has a housing 1, which comprises a holding body 3 and a nozzle body 4, which are braced against each other by means of a clamping nut 5.
  • a pressure chamber 7 is formed, which is filled via a high-pressure port 32 with fuel under high pressure.
  • a nozzle needle 8 is longitudinally displaceably arranged, which has a valve sealing surface 11 at its in installation position of an internal combustion engine facing end, with which the nozzle needle 8 cooperates with a nozzle seat 10 and thereby the connection of a plurality of injection openings 12 which are formed in the nozzle body 4, with the pressure chamber 7 controls.
  • the nozzle needle 8 is guided in the region of the nozzle body 4 in a guide section 16, wherein the fuel flow is ensured by the pressure chamber 7 on the guide portion 16 over in the direction of the injection openings 12 by one or more polished sections on the guide section 16.
  • a closing spring 9 which surrounds the nozzle needle 8 is arranged in the nozzle body 4, which is under pressure prestressing with one end against the
  • Holding body 3 and with the other end to a on the nozzle needle 8 also- formed paragraph 14 and thereby exerts a closing force in the direction of the valve seat 10 on the nozzle needle 8.
  • a valve piece 20 is arranged in the pressure chamber 7, which is supported on a throttle plate 24, which forms the valve seat facing away from the end of the pressure chamber 7 and which can also be made in one piece with the valve member 20.
  • the throttle plate 24 is clamped by a clamping screw 25 against a shoulder in the holding body 3.
  • a stepped bore 21, 22 is formed, which encloses a diameter-reduced guide bore 22 and an enlarged diameter bore portion 21.
  • the nozzle needle 8 protrudes with its nozzle seat facing away from the end, on which the end face 17 is formed, in the extended bore portion 21 and is guided there radially.
  • the control chamber 28 is formed by a valve in the piece 20
  • Inlet throttle 30 is connected to the pressure chamber 7 and via an outlet throttle 31 with a low-pressure chamber 46 which is connected to a return line, not shown in the drawing, so that there is always a low pressure in the low pressure chamber 46.
  • a control valve 40 is arranged in the housing 1 on the side facing away from the control chamber 28 side of the throttle plate 24.
  • the control valve 40 comprises a magnetic armature 42, on whose end facing the throttle plate 24, a sealing ball 43 is arranged, with which the armature 42 rests on a seat formed in the throttle plate 24 and thereby closes the outlet throttle 31.
  • the armature 42 is acted upon by a spring 45 in the direction of the throttle plate 24 with a closing force and can be pulled by an electromagnet 44 against the force of the spring 45 in an open position, so that the sealing ball 43, the outlet throttle 31 releases and fuel from the control chamber 28th can flow into the low pressure chamber 46.
  • Fig. 2 shows the area of the control chamber 28 of FIG. 1 again in an enlarged view.
  • a control piston 29 is arranged in the control chamber 28.
  • Control piston 29 is longitudinally movable in the control chamber 28 and is in the control bore 22 guided with a cylindrical portion 129.
  • the nozzle needle 8 facing the end of the control piston 29 is expanded and forms on an outer surface a sealing surface 38 which cooperates with a formed on the valve piece 20 sealing seat 39.
  • the movement of the control piston 29 is limited in the direction of the nozzle needle 8 by a stop 35.
  • the control piston 28 divides the control chamber 28 into a first partial control chamber 128 and a second partial control chamber 228, wherein the first partial control chamber 128 is formed between the first end surface 36 of the control piston 29 and the throttle plate 24 and the second partial control chamber 228 is formed between the second end surface 37 of the control piston 29 and the end face 17 of the nozzle needle 8.
  • a connecting throttle 34 is provided in the valve piece 20, via which a pressure equalization between the two sub-control chambers 128, 228 can take place.
  • a closing spring 33 is arranged, which acts on the control piston 29 in the direction of the nozzle needle 8 with an opening force and presses against the stop 35.
  • an annular groove 49 is formed on the outer side of the control piston 29, into which the inlet throttle 30 opens.
  • the control piston 29 is in its open position, that is in abutment against the stop 35, the second part control chamber 228 is hydraulically connected via the annular groove 49 with the inlet throttle 30, as shown in Fig. 2.
  • the function of the described fuel injection valve is as follows. At the beginning of the injection, the control valve 40 is de-energized, so that the armature 42 driven by the closing spring 45, the outlet throttle 31 closes. Because of the connection of the first partial control chamber 128 with the second partial control chamber 228 via the connecting throttle 34, the same high pressure prevails in the entire control chamber 28, since there is a connection to the pressure chamber 7 via the inlet throttle 30, in which fuel is present under high pressure. If the electromagnet of the control valve 40 is energized, the armature 42 lifts off from the throttle plate 24 and releases the outlet throttle 31, via which fuel from the first partial control chamber 128 flows immediately into the low-pressure chamber 46.
  • the pressure in the first sub-control chamber 128 then decreases very rapidly, which reduces the hydraulic forces on the first end face 36 of the control piston 29, while in the second sub-control chamber 228, due to the throttling action of the connecting throttle 34 and the inflowing fuel from the inlet throttle 30, the pressure is still significantly higher.
  • the resulting higher hydraulic force on the second end face 37 of the control piston 29 pushes the control piston away from the stop 35 in the direction of the throttle plate 24 until its sealing surface 38 comes to rest on the sealing seat 39 and separates the annular groove 49 from the second partial control chamber 228.
  • the inlet throttle 30 is now sealed and the high fuel pressure is only within half of the annular groove 49, while in the second part of the control chamber 228, the pressure now drops further, which also reduces the closing force on the end face 17 of the nozzle needle 8, until - driven by the hydraulic forces in the pressure chamber 7 - lifts off from the nozzle seat 10 and fuel flows from the pressure chamber 7 to the injection openings 12 and exits through this from the fuel injection valve.
  • the energization of the electromagnet 40 is stopped, so that the armature 42 moves back to its closed position and the outlet throttle 31 closes again.
  • the control piston lifts off from the sealing seat 39, which again connects the annular groove 49 with the second partial control chamber 228.
  • the pressure in both sub-control chambers 128, 228 then increases rapidly and the nozzle needle 8 is pushed back to its closed position on the nozzle seat 10, which ends the injection.
  • the control piston 29 moves as far in the direction of the nozzle needle 8, until it abuts the stop 35 again.
  • FIG. 3 another embodiment is shown, wherein like parts are provided with the same reference numerals. This differs from the embodiment of FIG. 2 only in that the connecting throttle 34 is not formed in the valve piece 20, but as a longitudinal bore in the valve piston 29, the As a rule, it is easier and cheaper to produce an angled or oblique bore in the valve piece 20.
  • FIG. 4 shows in the same representation as FIGS. 2 and 3 a further exemplary embodiment.
  • the control piston 29 is here equipped with a further paragraph at the nozzle end, between which and the valve piece 20, the closing spring 33 is arranged, which is correspondingly omitted in the first part control chamber 128.
  • This arrangement of the closing spring 33 makes it possible to make the first partial control chamber 128 very small, whereby the pressure drops very rapidly when the control valve is open and the nozzle needle 8 opens correspondingly quickly after activation of the control valve 40.
  • the control piston 29 has no annular groove 40, but is cylindrical except for the sealing surface 38.
  • the closing spring 33 is at its end facing the nozzle needle 8, while the other end of the closing spring rests against a shoulder 41 of the valve member 20.
  • an inlet chamber 47 is formed, in which the inlet throttle 30 opens and receives the closing spring 33.
  • the control piston 29 is relatively simple and the volume of the
  • Zulaufraums is further reduced by the closing spring 33, which is advantageous for a quick switching of the control piston 29.
  • FIG. 6 a further embodiment of the invention is shown, which differs from the embodiment of FIG. 3 mainly by the omission of the closing spring.
  • the opening of the fuel injection valve is identical to the above-described operation.
  • the sealing seat 39 can be radially displaced slightly outwards.

Landscapes

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

Abstract

L'invention concerne une soupape d'injection de carburant comprenant un carter (1), dans lequel une aiguille d'injecteur (8) est soumise au moins indirectement à une pression présente dans une chambre de commande (28) et exerçant une force de fermeture dans la direction d'un siège de soupape (10). La pression dans la chambre de commande (28) peut être ajustée par une soupape de commande (40), la chambre de commande (28) pouvant être reliée à une chambre basse pression (46) par un étranglement de sortie (31) et la chambre de commande (28) pouvant être remplie de carburant sous haute pression par un étranglement d'entrée (30). Dans la chambre de commande (28) est agencé un piston de commande (29) mobile longitudinalement qui divise la chambre de commande (28) en une première chambre de commande partielle (128) et une deuxième chambre de commande partielle (228), la première chambre de commande partielle (128) pouvant être reliée à la chambre basse pression (46) par l'étranglement de sortie (31). Sur le piston de commande (29) est ménagée une surface d'étanchéité (38) qui coopère avec un siège d'étanchéité (39) présent dans la chambre de commande (28) de sorte que, lorsque la surface d'étanchéité (38) se trouve sur le siège d'étanchéité (39), l'étranglement d'entrée (30) est séparé hydrauliquement de la deuxième chambre de commande partielle (228), la première chambre de commande partielle (128) et la deuxième chambre de commande partielle (228) restant reliées hydrauliquement l'une à l'autre par un raccordement à étranglement (34).
EP13723131.2A 2012-06-29 2013-05-15 Injecteur de carburant pour moteurs à combustion interne Active EP2867517B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102012211239 2012-06-29
DE102012220025.8A DE102012220025A1 (de) 2012-06-29 2012-11-02 Kraftstoffeinspritzventil für Brennkraftmaschinen
PCT/EP2013/060078 WO2014000957A1 (fr) 2012-06-29 2013-05-15 Soupape d'injection de carburant pour moteurs à combustion interne

Publications (2)

Publication Number Publication Date
EP2867517A1 true EP2867517A1 (fr) 2015-05-06
EP2867517B1 EP2867517B1 (fr) 2016-07-13

Family

ID=49754198

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13723131.2A Active EP2867517B1 (fr) 2012-06-29 2013-05-15 Injecteur de carburant pour moteurs à combustion interne

Country Status (4)

Country Link
US (1) US9777684B2 (fr)
EP (1) EP2867517B1 (fr)
DE (1) DE102012220025A1 (fr)
WO (1) WO2014000957A1 (fr)

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WO2018162747A1 (fr) * 2017-03-10 2018-09-13 Liebherr-Components Deggendorf Gmbh Soupape d'injection de carburant

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Publication number Priority date Publication date Assignee Title
WO2018162747A1 (fr) * 2017-03-10 2018-09-13 Liebherr-Components Deggendorf Gmbh Soupape d'injection de carburant
EP3800344A1 (fr) * 2017-03-10 2021-04-07 Liebherr-Components Deggendorf GmbH Soupape d'injection de carburant

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Publication number Publication date
US9777684B2 (en) 2017-10-03
WO2014000957A1 (fr) 2014-01-03
US20150159607A1 (en) 2015-06-11
DE102012220025A1 (de) 2014-01-02
EP2867517B1 (fr) 2016-07-13

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